JP4780707B2 - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

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JP4780707B2
JP4780707B2 JP2006037824A JP2006037824A JP4780707B2 JP 4780707 B2 JP4780707 B2 JP 4780707B2 JP 2006037824 A JP2006037824 A JP 2006037824A JP 2006037824 A JP2006037824 A JP 2006037824A JP 4780707 B2 JP4780707 B2 JP 4780707B2
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inner ring
wheel
bearing device
wheel bearing
curvature
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JP2007218305A (en
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和雄 小森
貴之 小和田
恭大 有竹
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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
    • F16C33/60—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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors

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

Description

本発明は、自動車等の車輪を懸架装置に対して回転自在に支承する車輪用軸受装置、特に、ハブ輪に加締固定される内輪の耐久性向上を図った車輪用軸受装置に関するものである。   The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like with respect to a suspension device, and more particularly to a wheel bearing device that improves durability of an inner ring that is crimped and fixed to a hub wheel. .

自動車等の車両の車輪用軸受装置には、駆動輪用のものと従動輪用のものとがある。特に、自動車の懸架装置に対して車輪を回転自在に支承する車輪用軸受装置は、低コスト化は言うまでもなく、燃費向上のための軽量・コンパクト化が進んでいる。その従来構造の代表的な一例として、図３に示すような従動輪用の車輪用軸受装置が知られている。   2. Description of the Related Art Wheel bearing devices for vehicles such as automobiles include those for driving wheels and those for driven wheels. In particular, a wheel bearing device that rotatably supports a wheel with respect to a suspension device of an automobile has been made lighter and more compact for improving fuel efficiency, not to mention cost reduction. As a typical example of the conventional structure, a wheel bearing device for a driven wheel as shown in FIG. 3 is known.

この車輪用軸受装置は第３世代と称され、内方部材５１と外方部材６０、および両部材５１、６０間に転動自在に収容された複列のボール５５、５５を備えている。内方部材５１は、ハブ輪５２と、このハブ輪５２に所定のシメシロを介して圧入された内輪５３とからなる。   This wheel bearing device is referred to as a third generation, and includes an inner member 51 and an outer member 60, and double-row balls 55 and 55 accommodated between the members 51 and 60 so as to roll freely. The inner member 51 includes a hub ring 52 and an inner ring 53 press-fitted into the hub ring 52 through a predetermined shimoshiro.

ハブ輪５２は、一端部に車輪（図示せず）を取り付けるための車輪取付フランジ５４を一体に有し、外周に内側転走面５２ａと、この内側転走面５２ａから軸方向に延びる小径段部５２ｂが形成されている。そして、外周に内側転走面５３ａが形成された内輪５３が小径段部５２ｂに圧入され、さらに、小径段部５２ｂの端部を径方向外方に塑性変形させて形成した加締部５２ｃにより、ハブ輪５２に対して内輪５３が軸方向に固定されている。   The hub wheel 52 integrally has a wheel mounting flange 54 for mounting a wheel (not shown) at one end, an inner rolling surface 52a on the outer periphery, and a small diameter step extending in the axial direction from the inner rolling surface 52a. A portion 52b is formed. An inner ring 53 having an inner raceway surface 53a formed on the outer periphery is press-fitted into the small-diameter stepped portion 52b, and further, an end portion of the small-diameter stepped portion 52b is plastically deformed outward in the radial direction. The inner ring 53 is fixed to the hub ring 52 in the axial direction.

外方部材６０は、外周に車体（図示せず）に取り付けるための車体取付フランジ６０ｂを一体に有し、内周に複列の外側転走面６０ａ、６０ａが形成されている。そして、それぞれの転走面６０ａ、５２ａと６０ａ、５３ａ間に複列のボール５５、５５が収容され、保持器５６、５６によりこれら複列のボール５５、５５が転動自在に保持されている。また、外方部材６０の端部にはシール５７、５８が装着され、軸受内部に封入された潤滑グリースの漏洩と、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。   The outer member 60 integrally has a vehicle body mounting flange 60b for mounting to the vehicle body (not shown) on the outer periphery, and double row outer rolling surfaces 60a, 60a are formed on the inner periphery. The double rows of balls 55 and 55 are accommodated between the respective rolling surfaces 60a and 52a and 60a and 53a, and the double rows of balls 55 and 55 are held by the cages 56 and 56 so as to freely roll. . Further, seals 57 and 58 are attached to the end portion of the outer member 60 to prevent leakage of lubricating grease sealed inside the bearing and intrusion of rainwater, dust and the like from the outside into the bearing.

ここで、加締前におけるハブ輪５２の小径段部５２ｂは、図４に示すように、中空状の円筒部７０として形成されている。この円筒部７０は所定の軸方向深さｄ１を有し、円筒部７０の先端部肉厚Ｄ２が、根元部の肉厚Ｄ１よりも大きくなるよう先端に向って漸増する形状に形成されている。これにより、加締加工の初期にポンチ等の加締治具によって押し広げられる肉量が多くなるため、ハブ輪５２の円筒部７０を塑性変形させる軸方向寸法が短くて済むと共に、加締治具形状に早期に充足し易く、内輪５３を強固に固定することができる。   Here, the small-diameter step portion 52b of the hub wheel 52 before caulking is formed as a hollow cylindrical portion 70 as shown in FIG. The cylindrical portion 70 has a predetermined axial depth d1, and is formed in a shape that gradually increases toward the distal end so that the distal end thickness D2 of the cylindrical portion 70 is larger than the thickness D1 of the root portion. . As a result, the amount of the wall that is pushed and expanded by a clamping jig such as a punch increases in the initial stage of the crimping process, so that the axial dimension for plastic deformation of the cylindrical portion 70 of the hub wheel 52 can be shortened, and the crimping process can be performed. It is easy to satisfy the tool shape at an early stage, and the inner ring 53 can be firmly fixed.

また、内輪５３の内径端部に、曲率半径ｒ１が１〜２．５ｍｍの円弧形状からなる面取り部５３ｂが形成されると共に、円筒部７０の外周面に深さｎが０．５ｍｍ程度、曲率半径ｒ２が５〜１０ｍｍ程度の環状溝７１が、内輪５３の面取り部５３ｂにかかるように形成されている。これにより、ハブ輪５２の円筒部７０を加締めても、内輪５３の変形を最小限に抑えることができると共に、加締加工時の亀裂等の損傷を防止することができる。
特開２００２−１３９０６０号公報 A chamfered portion 53b having an arc shape with a radius of curvature r1 of 1 to 2.5 mm is formed at the inner diameter end of the inner ring 53, and a depth n is about 0.5 mm on the outer peripheral surface of the cylindrical portion 70. An annular groove 71 having a radius r2 of about 5 to 10 mm is formed so as to cover the chamfered portion 53b of the inner ring 53. As a result, even when the cylindrical portion 70 of the hub wheel 52 is crimped, the deformation of the inner ring 53 can be minimized, and damage such as cracks during the crimping process can be prevented.
JP 2002-139060 A

このような従来の車輪用軸受装置では、ハブ輪５２において、加締前の小径段部５２ｂの円筒部７０が先端に向って漸増する形状に形成されると共に、円筒部７０の外周面に環状溝７１、所謂アンダーカットが、内輪５３の面取り部５３ｂにかかるように形成されているので、加締加工による内輪５３の変形を最小限に抑えることができ、その外径に発生するフープ応力を抑制することができる特徴を備えている。然しながら、このフープ応力は内輪押込み量（加締量）と相関関係があり、この内輪押込み量が大きくなるとフープ応力が増加する傾向にある。したがって、内輪割れ等に繋がる過大フープ応力、例えば、２５０ＭＰａ以上のフープ応力の発生を防止するためには、内輪押込み量を小さくする必要があるが、単にこの内輪押込み量を小さくするだけでは内輪５３の固定力を確保することができないため、フープ応力を抑えると共に、適切な内輪押込み量が得られる手法等が求められていた。   In such a conventional wheel bearing device, in the hub wheel 52, the cylindrical portion 70 of the small-diameter stepped portion 52b before caulking is formed in a shape that gradually increases toward the tip, and the outer peripheral surface of the cylindrical portion 70 is annular. Since the groove 71, so-called undercut, is formed so as to be applied to the chamfered portion 53b of the inner ring 53, deformation of the inner ring 53 due to crimping can be minimized, and hoop stress generated at the outer diameter can be reduced. It has features that can be suppressed. However, the hoop stress has a correlation with the inner ring pushing amount (clamping amount), and the hoop stress tends to increase as the inner ring pushing amount increases. Therefore, in order to prevent the occurrence of an excessive hoop stress that leads to cracking of the inner ring, for example, a hoop stress of 250 MPa or more, it is necessary to reduce the inner ring pushing amount, but simply reducing the inner ring pushing amount reduces the inner ring 53. Therefore, there has been a demand for a technique for suppressing the hoop stress and obtaining an appropriate inner ring pushing amount.

本発明は、このような従来の問題に鑑みてなされたもので、ハブ輪に加締固定される内輪の変形を抑制し、かつクリープを防止すると共に、ハブ輪の強度・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する。   The present invention has been made in view of such conventional problems, and suppresses deformation of the inner ring that is crimped and fixed to the hub ring, prevents creep, and improves the strength and durability of the hub ring. It is an object of the present invention to provide a wheel bearing device.

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、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる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圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、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転動体とを備え、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り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、前記小径段部の加締前の端部が中空状の円筒部として形成され、この円筒部の外周面に０．５〜１．０ｍｍの深さで、両側に所定の曲率半径Ｒｉ、Ｒｏからなる円弧面を有する環状溝が形成され、これら円弧面のうちインナー側の円弧面の曲率半径Ｒｉがアウター側の円弧面の曲率半径Ｒｏよりも小さく設定されると共に、当該環状溝が、前記転動体と内側転走面との接触線の延長上と前記小径段部の外周面と交叉する点から所定の間隔をおいてインナー側に、かつ前記内輪の加締部側の面取り部にかかって大端面を越えて形成されている。
In order to achieve such an object, the invention according to claim 1 of the present invention integrally has an outer member having a double row outer rolling surface formed on the inner periphery and a wheel mounting flange at one end. A hub wheel formed with a small-diameter step portion extending in the axial direction from the wheel mounting flange, and at least one inner ring press-fitted into the small-diameter step portion of the hub wheel, and the outer circumferential surface of the double row on the outer periphery. An inward member formed with opposing double-row inner rolling surfaces, and a double-row rolling member accommodated between the rolling surfaces of the inner member and the outer member via a cage. In a wheel bearing device in which the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming an end portion of the small diameter step portion radially outwardly, the caulking of the small diameter step portion is provided. The front end is formed as a hollow cylindrical portion, and a depth of 0.5 to 1.0 mm is formed on the outer peripheral surface of the cylindrical portion. An annular groove having an arc surface having predetermined curvature radii Ri and Ro is formed on both sides, and the curvature radius Ri of the inner arc surface is smaller than the curvature radius Ro of the outer arc surface of these arc surfaces. The annular groove is on the inner side at a predetermined interval from the point of intersection of the contact line between the rolling element and the inner rolling surface and the outer peripheral surface of the small diameter step portion, and the depends on the chamfered portion of the caulking portion side of the inner ring is a large end face Yue forte formation.

このように、ハブ輪の小径段部に内輪が圧入され、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り、ハブ輪に対して内輪を軸方向に固定した第１世代乃至第３世代のセルフリテイン構造の車輪用軸受装置において、小径段部の加締前の端部が中空状の円筒部として形成され、この円筒部の外周面に０．５〜１．０ｍｍの深さで、両側に所定の曲率半径Ｒｉ、Ｒｏからなる円弧面を有する環状溝が形成され、これら円弧面のうちインナー側の円弧面の曲率半径Ｒｉがアウター側の円弧面の曲率半径Ｒｏよりも小さく設定されると共に、当該環状溝が、転動体と内側転走面との接触線の延長上と小径段部の外周面と交叉する点から所定の間隔をおいてインナー側に、かつ内輪の加締部側の面取り部にかかって大端面を越えて形成されているので、加締加工時に円筒部が変形し易くなり、加締加工による内輪の変形を抑制し、かつ内輪のクリープを防止することができると共に、ハブ輪の強度・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。
In this way, the inner ring is fixed to the hub ring in the axial direction by the caulking portion formed by press-fitting the inner ring into the small-diameter step portion of the hub wheel and plastically deforming the end of the small-diameter step portion radially outward. In the first-generation to third-generation self-retained wheel bearing device, the end portion of the small-diameter step portion before caulking is formed as a hollow cylindrical portion, and the outer peripheral surface of this cylindrical portion is 0.5- An annular groove having an arc surface having predetermined curvature radii Ri and Ro is formed on both sides at a depth of 1.0 mm, and the curvature radius Ri of the inner arc surface of these arc surfaces is the same as that of the outer arc surface. It is set smaller than the radius of curvature Ro, and the annular groove is formed on the inner side at a predetermined interval from the point of intersection of the contact line between the rolling element and the inner rolling surface and the outer peripheral surface of the small diameter step portion. to, and Yue the large end face rests on the chamfered portion of the caulking portion side of the inner ring forte As a result, the cylindrical part is easily deformed during caulking, which suppresses deformation of the inner ring due to caulking, prevents creep of the inner ring, and improves the strength and durability of the hub ring. It is possible to provide a wheel bearing device that achieves the above.

好ましくは、請求項２に記載の発明のように、前記内輪における加締部側の内径端部の面取り部が所定の曲率半径ｒ１からなる円弧面を有し、この曲率半径ｒ１よりも、前記環状溝におけるインナー側の円弧面の曲率半径Ｒｉが大きく、ｒ１≦Ｒｉとなるように設定されていれば、加締加工による亀裂等の損傷を防止すると共に、内輪の変形を抑制することができる。   Preferably, as in the invention described in claim 2, the chamfered portion at the inner diameter end portion on the side of the caulking portion in the inner ring has an arc surface having a predetermined curvature radius r1, and the curvature radius r1 is greater than the curvature radius r1. If the radius of curvature Ri of the circular arc surface on the inner side in the annular groove is large and is set so as to satisfy r1 ≦ Ri, damage such as cracks due to caulking can be prevented and deformation of the inner ring can be suppressed. .

また、請求項３に記載の発明のように、前記小径段部に高周波焼入れによって所定の硬化層が形成され、この硬化層が前記環状溝におけるアウター側の円弧面の起点で止められていれば、ハブ輪の耐フレッティング性を高めて強度・耐久性の向上を図ることができる。   Further, as in the third aspect of the present invention, if a predetermined hardened layer is formed by induction hardening in the small-diameter step portion, and this hardened layer is stopped at the starting point of the outer arc surface in the annular groove It is possible to improve the strength and durability by increasing the fretting resistance of the hub wheel.

また、請求項４に記載の発明のように、前記円筒部における前記内輪の加締部側の大端面からの深さが前記環状溝の幅よりも小さく設定されていれば、円筒部の塑性変形がし易くなると共に、所定の内輪固定力を得ることができる。   If the depth from the large end surface of the inner ring on the side of the caulking portion of the inner ring is set to be smaller than the width of the annular groove as in the invention described in claim 4, the plasticity of the cylindrical portion It becomes easy to deform, and a predetermined inner ring fixing force can be obtained.

好ましくは、請求項５に記載の発明のように、前記円筒部における前記内輪の加締部側の大端面からの深さが０〜５ｍｍの範囲に設定されていれば、ハブ輪の強度・剛性を確保しつつ、所定の内輪固定力を得ることができると共に、加締加工によって生じる内輪のフープ応力を２５０ＭＰａ以下に抑えることができ、内輪の割れ等の損傷を防止することができる。   Preferably, as in the invention described in claim 5, if the depth from the large end surface of the inner ring on the side of the caulking portion in the cylindrical portion is set in a range of 0 to 5 mm, the strength of the hub wheel While ensuring rigidity, a predetermined inner ring fixing force can be obtained, and the hoop stress of the inner ring caused by caulking can be suppressed to 250 MPa or less, and damage such as cracking of the inner ring can be prevented.

本発明に係る車輪用軸受装置は、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる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圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、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転動体とを備え、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り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、前記小径段部の加締前の端部が中空状の円筒部として形成され、この円筒部の外周面に０．５〜１．０ｍｍの深さで、両側に所定の曲率半径Ｒｉ、Ｒｏからなる円弧面を有する環状溝が形成され、これら円弧面のうちインナー側の円弧面の曲率半径Ｒｉがアウター側の円弧面の曲率半径Ｒｏよりも小さく設定されると共に、当該環状溝が、前記転動体と内側転走面との接触線の延長上と前記小径段部の外周面と交叉する点から所定の間隔をおいてインナー側に、かつ前記内輪の加締部側の面取り部にかかって大端面を越えて形成されているので、加締加工時に円筒部が変形し易くなり、加締加工による内輪の変形を抑制し、かつ内輪のクリープを防止することができると共に、ハブ輪の強度・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 integrally has an outer member having a double row outer raceway formed on the inner periphery and a wheel mounting flange at one end, and extends in an axial direction from the wheel mounting flange. A hub ring formed with a small diameter step portion and at least one inner ring press-fitted into the small diameter step portion of the hub ring, and a double row inner rolling surface facing the double row outer rolling surface on the outer periphery. An inner member formed, and a double row rolling element that is rotatably accommodated between the rolling surfaces of the inner member and the outer member via a cage, In the wheel bearing device in which the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming an end portion radially outward, the end portion of the small diameter step portion before caulking is a hollow cylindrical portion And a predetermined radius of curvature R on both sides at a depth of 0.5 to 1.0 mm on the outer peripheral surface of the cylindrical portion. An annular groove having an arc surface made of Ro is formed, and the radius of curvature Ri of the inner arc surface of these arc surfaces is set smaller than the radius of curvature Ro of the outer arc surface, and the annular groove The chamfered portion on the inner side at a predetermined interval from the point of intersection of the contact line between the rolling element and the inner rolling surface and the outer peripheral surface of the small-diameter stepped portion, and on the caulking portion side of the inner ring the suffering and because it is formed large end face Yue forte, easily deformed cylindrical portion during caulking, and suppress deformation of the inner ring by caulking, and it is possible to prevent the inner ring of the creep, the hub It is possible to provide a wheel bearing device that improves the strength and durability of the wheel.

外周に車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面の一方に対向する内側転走面と、この内側転走面から軸方向に延びる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転動体とを備え、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り前記内輪が軸方向に固定された第１世代乃至第３世代のセルフリテイン構造の車輪用軸受装置において、前記小径段部の加締前の端部が中空状の円筒部として形成され、この円筒部の外周面に０．５〜１．０ｍｍの深さで、両側に所定の曲率半径Ｒｉ、Ｒｏからなる円弧面を有する環状溝が形成され、これら円弧面のうちインナー側の円弧面の曲率半径Ｒｉが、前記内輪における面取り部の曲率半径ｒ１よりも大きく、アウター側の円弧面の曲率半径Ｒｏよりも小さく、ｒ１≦Ｒｉ≦Ｒｏに設定されると共に、当該環状溝が、前記転動体と内側転走面との接触線の延長上と前記小径段部の外周面と交叉する点から所定の間隔をおいてインナー側に、かつ前記内輪の加締部側の面取り部にかかって大端面を越えて形成されている。

A vehicle body mounting flange is integrally formed on the outer periphery, an outer member having a double row outer rolling surface formed on the inner periphery, a wheel mounting flange is integrally formed on one end, and the double row outer rolling is formed on the outer periphery. An inner rolling surface facing one of the running surfaces, a hub wheel formed with a small-diameter step portion extending in the axial direction from the inner rolling surface, and a small diameter step portion of the hub wheel are press-fitted into the outer periphery of the double row. An inner member made of an inner ring formed with an inner rolling surface facing the other of the outer rolling surfaces of the inner rolling surface, and can be rolled via a cage between both rolling surfaces of the inner member and the outer member. The inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming an end of the small diameter step portion radially outward. In the third-generation self-retained wheel bearing device, the end portion of the small-diameter step portion before caulking is formed as a hollow cylindrical portion. An annular groove having a circular arc surface having a predetermined curvature radius Ri and Ro is formed on both sides at a depth of 0.5 to 1.0 mm on the outer peripheral surface of the cylindrical portion. The radius of curvature Ri of the circular arc surface is set to be larger than the radius of curvature r1 of the chamfered portion of the inner ring and smaller than the radius of curvature Ro of the arcuate surface on the outer side, and r1 ≦ Ri ≦ Ro. The chamfered portion on the inner side at a predetermined interval from the point of intersection of the contact line between the rolling element and the inner rolling surface and the outer peripheral surface of the small-diameter stepped portion, and on the caulking portion side of the inner ring It depends on it being a large end face Yue forte formation.

以下、本発明の実施の形態を図面に基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一実施形態を示す縦断面図、図２は、加締前のハブ輪および内輪を示す要部拡大図である。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（図面左側）、中央寄り側をインナー側（図面右側）という。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, and FIG. 2 is an enlarged view of a main part showing a hub wheel and an inner ring before caulking. In the following description, the side closer to the outer side of the vehicle in a state assembled to the vehicle is referred to as the outer side (left side in the drawing), and the side closer to the center is referred to as the inner side (right side in the drawing).

この車輪用軸受装置は従動輪側の第３世代と称され、内方部材１と外方部材１０、および両部材１、１０間に転動自在に収容された複列の転動体（ボール）６、６を備えている。内方部材１は、ハブ輪２と、このハブ輪２に所定のシメシロを介して圧入された内輪３とからなる。   This wheel bearing device is referred to as the third generation on the driven wheel side, and is a double row rolling element (ball) accommodated between the inner member 1 and the outer member 10 and between both members 1 and 10 so as to roll freely. 6 and 6 are provided. The inner member 1 includes a hub ring 2 and an inner ring 3 that is press-fitted into the hub ring 2 through a predetermined scissors.

ハブ輪２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４を一体に有し、この車輪取付フランジ４の円周等配位置に車輪を固定するためのハブボルト５が植設されている。また、ハブ輪２の外周には一方（アウター側）の内側転走面２ａが直接形成され、この内側転走面２ａから軸方向に延びる小径段部２ｂが形成されている。そして、外周に他方（インナー側）の内側転走面３ａが形成された内輪３がこの小径段部２ｂに圧入され、さらに、小径段部２ｂの端部を径方向外方に塑性変形させて形成した加締部２ｃにより、ハブ輪２に対して内輪３が軸方向へ抜けるのを防止している。   The hub wheel 2 integrally has a wheel mounting flange 4 for mounting a wheel (not shown) at an end on the outer side, and a hub bolt for fixing the wheel at a circumferentially equidistant position of the wheel mounting flange 4. 5 is planted. Further, one (outer side) inner rolling surface 2a is directly formed on the outer periphery of the hub wheel 2, and a small-diameter step portion 2b extending in the axial direction from the inner rolling surface 2a is formed. And the inner ring | wheel 3 in which the inner side rolling surface 3a of the other (inner side) was formed in the outer periphery is press-fit in this small diameter step part 2b, and also the edge part of the small diameter step part 2b is plastically deformed to radial direction outward. The formed caulking portion 2 c prevents the inner ring 3 from coming off in the axial direction with respect to the hub wheel 2.

ハブ輪２は、Ｓ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、アウター側の内側転走面２ａをはじめ、シール８が摺接するシールランド部、および小径段部２ｂに亙り高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化層１１が形成されている。なお、加締部２ｃは、鍛造後の素材表面硬さ２５ＨＲＣ以下の未焼入れ部としている。一方、内輪３は、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。これにより、シールランド部の耐摩耗性が向上するだけでなくハブ輪２の強度も向上すると共に、内輪３の嵌合面におけるフレッティング摩耗が抑制されて耐久性が向上する。また、加締部２ｃの加工性を向上させ、塑性変形によるクラック等の発生を防止することができる。   The hub wheel 2 is made of medium carbon steel containing 0.40 to 0.80% by weight of carbon such as S53C, and includes an inner side rolling surface 2a on the outer side, a seal land portion in which the seal 8 is in sliding contact, and a small diameter step. The hardened layer 11 is formed in the range of 58 to 64 HRC by induction hardening over the portion 2b. The caulking portion 2c is an unquenched portion having a material surface hardness of 25 HRC or less after forging. On the other hand, the inner ring 3 is made of high carbon chrome bearing steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching. Thereby, not only the wear resistance of the seal land portion is improved, but also the strength of the hub wheel 2 is improved, and the fretting wear on the fitting surface of the inner ring 3 is suppressed, thereby improving the durability. Moreover, the workability of the caulking portion 2c can be improved, and the occurrence of cracks and the like due to plastic deformation can be prevented.

外方部材１０は、外周に車体（図示せず）に取り付けるための車体取付フランジ１０ｂを一体に有し、内周には複列の外側転走面１０ａ、１０ａが形成されている。この外方部材１０は、ハブ輪２と同様、Ｓ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、少なくとも複列の外側転走面１０ａ、１０ａが高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。そして、それぞれの転走面１０ａ、２ａと１０ａ、３ａ間に複列の転動体６、６が収容され、保持器７、７によりこれら複列の転動体６、６が転動自在に保持されている。また、外方部材１０の端部にはシール８、９が装着され、軸受内部に封入された潤滑グリースの漏洩と、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。   The outer member 10 integrally has a vehicle body mounting flange 10b for mounting to a vehicle body (not shown) on the outer periphery, and double row outer rolling surfaces 10a, 10a are formed on the inner periphery. The outer member 10 is formed of medium carbon steel containing 0.40 to 0.80% by weight of carbon such as S53C, as in the case of the hub wheel 2, and at least the double row outer raceway surfaces 10a and 10a are formed by induction hardening. The surface hardness is set in the range of 58 to 64 HRC. And the double row rolling elements 6 and 6 are accommodated between each rolling surface 10a, 2a and 10a, 3a, and these double row rolling elements 6 and 6 are rollably hold | maintained by the holder | retainers 7 and 7. ing. Further, seals 8 and 9 are attached to the end portion of the outer member 10 to prevent leakage of the lubricating grease sealed inside the bearing and intrusion of rainwater, dust and the like from the outside into the bearing.

ここでは、ハブ輪２の外周に直接内側転走面２ａが形成された第３世代と呼称される車輪用軸受装置を例示したが、本発明に係る車輪用軸受装置はこうした構造に限定されず、例えば、図示はしないが、ハブ輪の小径段部に一対の内輪を圧入した、第１世代あるいは第２世代構造であっても良い。なお、転動体６、６をボールとした複列アンギュラ玉軸受を例示したが、これに限らず転動体６に円すいころを使用した複列円すいころ軸受であっても良い。   Here, the wheel bearing device referred to as the third generation in which the inner raceway surface 2a is directly formed on the outer periphery of the hub wheel 2 is illustrated, but the wheel bearing device according to the present invention is not limited to such a structure. For example, although not shown, a first generation or second generation structure in which a pair of inner rings are press-fitted into a small diameter step portion of the hub ring may be used. In addition, although the double row angular contact ball bearing which used the rolling elements 6 and 6 as the ball was illustrated, it is not restricted to this, The double row tapered roller bearing which uses the tapered roller for the rolling element 6 may be sufficient.

ここで、図２に示すように、内輪３における加締部２ｃ側の大端面３ｂの内径端部に曲率半径ｒ１がＲ１．０〜２．５からなる面取り部３ｃが形成されている。この面取り部３ｃの曲率半径ｒ１を１．０ｍｍよりも小さく設定すると、車両の運転中に曲げモーメント荷重が装置に負荷された時、加締部２ｃの根元部分に応力集中が起こり、微小クラック等の損傷が発生する恐れがある。逆に、曲率半径ｒ１が２．５ｍｍを超えると、円筒部１２を塑性変形する際、内輪３を径方向外方に押し広げることになり、内輪３の外径に過大なフープ応力が発生して好ましくない。なお、加締部２は図中二点鎖線にて示す。   Here, as shown in FIG. 2, a chamfered portion 3c having a radius of curvature r1 of R1.0 to 2.5 is formed at the inner diameter end portion of the large end surface 3b on the caulking portion 2c side in the inner ring 3. If the radius of curvature r1 of the chamfered portion 3c is set to be smaller than 1.0 mm, when a bending moment load is applied to the device during operation of the vehicle, stress concentration occurs at the root portion of the crimped portion 2c, and microcracks, etc. May cause damage. On the contrary, if the radius of curvature r1 exceeds 2.5 mm, when the cylindrical portion 12 is plastically deformed, the inner ring 3 is pushed outward in the radial direction, and an excessive hoop stress is generated in the outer diameter of the inner ring 3. It is not preferable. The caulking portion 2 is indicated by a two-dot chain line in the figure.

一方、ハブ輪２における加締前の小径段部２ｂの端部は中空状の円筒部１２として形成され、この円筒部１２の底面１２ａは、内輪３の大端面３ｂから所定の寸法（深さ）ａになるように形成されている。また、円筒部１２の外周面には深さｂからなる環状溝１３が形成されている。そして、この環状溝１３の両側にそれぞれ曲率半径Ｒｉ、Ｒｏからなる円弧面１３ａ、１３ｂが形成されている。   On the other hand, the end of the small diameter step 2b before caulking in the hub wheel 2 is formed as a hollow cylindrical portion 12, and the bottom surface 12a of the cylindrical portion 12 has a predetermined dimension (depth) from the large end surface 3b of the inner ring 3. ) It is formed to be a. An annular groove 13 having a depth b is formed on the outer peripheral surface of the cylindrical portion 12. Then, arc surfaces 13a and 13b having curvature radii Ri and Ro are formed on both sides of the annular groove 13, respectively.

環状溝１３は、内輪３における内側転走面３ａの大径端に対応する位置よりもインナー側から内輪３の面取り部３ｃにかかり、大端面３ｂを僅かに越える範囲に形成されている。具体的には、アウター側の円弧面１３ｂの起点は、転動体６と内側転走面３ａとの接触線の延長上と小径段部２ｂの外周面と交叉する支持点Ｐからインナー側に所定の間隔ｃをおいて設定されている。これにより、内輪３のクリープを防止することができる。クリープとは、嵌合シメシロ不足や嵌合面の加工精度不良等により軸受が周方向に微動して嵌合面が鏡面化し、場合によってはかじりを伴い焼付きや溶着する現象をいう。   The annular groove 13 extends from the inner side to the chamfered portion 3c of the inner ring 3 from the position corresponding to the large diameter end of the inner rolling surface 3a in the inner ring 3, and is formed in a range slightly beyond the large end surface 3b. Specifically, the starting point of the arcuate surface 13b on the outer side is predetermined on the inner side from the support point P that intersects the extension of the contact line between the rolling element 6 and the inner rolling surface 3a and the outer peripheral surface of the small-diameter step portion 2b. Is set at an interval c. Thereby, creep of the inner ring 3 can be prevented. Creep refers to a phenomenon in which the bearing surface slightly moves in the circumferential direction due to lack of mating shimoshiro or poor mating surface processing accuracy, the mating surface becomes mirrored, and in some cases, seizure or welding occurs with galling.

本実施形態では、環状溝１３の深さｂは０．５〜１．０ｍｍ、インナー側の円弧面１３ａの曲率半径Ｒｉは、内輪３の面取り部３ｃの曲率半径ｒ１よりも大きく、アウター側の円弧面１３ｂの曲率半径Ｒｏよりも小さく設定され（ｒ１≦Ｒｉ≦Ｒｏ）、ＲｉがＲ１〜１０の範囲に設定されている。円筒部１２の外周面に環状溝１３を形成することにより、加締加工時に円筒部１２が変形し易くなり、内輪３の変形を抑えることができる。ただし、環状溝１３の深さｂが０．５ｍｍよりも小さいとその効果が薄れ、また、深さｂが１．０ｍｍを超えると、加締部２ｃの強度不足が懸念される。   In the present embodiment, the depth b of the annular groove 13 is 0.5 to 1.0 mm, the radius of curvature Ri of the arcuate surface 13a on the inner side is larger than the radius of curvature r1 of the chamfered portion 3c of the inner ring 3, and It is set smaller than the radius of curvature Ro of the arc surface 13b (r1 ≦ Ri ≦ Ro), and Ri is set in the range of R1-10. By forming the annular groove 13 on the outer peripheral surface of the cylindrical portion 12, the cylindrical portion 12 is easily deformed during caulking, and deformation of the inner ring 3 can be suppressed. However, if the depth b of the annular groove 13 is smaller than 0.5 mm, the effect is reduced, and if the depth b exceeds 1.0 mm, the strength of the crimped portion 2c may be insufficient.

本出願人が実施した加締試験では、ａが０〜５ｍｍの範囲では、寸法ａが大きくなるほど内輪３の外径に発生するフープ応力が低下する。ところが、ａ＜５ｍｍでは、その効果が小さく、顕著な応力低下が見られないことが判った。一方、寸法ａが大きくなると内輪押込み量が不足して所定の内輪固定力が得られないだけでなく、ハブ輪２の強度・剛性の低下に繋がり好ましくない。   In the caulking test conducted by the present applicant, the hoop stress generated at the outer diameter of the inner ring 3 decreases as the dimension a increases in a range of 0 to 5 mm. However, it was found that when a <5 mm, the effect is small and no significant stress reduction is observed. On the other hand, when the dimension “a” is large, not only the inner ring pushing amount is insufficient and a predetermined inner ring fixing force cannot be obtained, but also the strength and rigidity of the hub ring 2 are lowered, which is not preferable.

さらに、本実施形態では、ハブ輪２の外周に形成される硬化層１１は、この環状溝１３におけるアウター側の円弧面１３ｂの起点で止められている。これにより、小径段部２ｂにおける円筒部１２の加工性を向上させ、塑性変形によるクラック等の発生を防止することができる。   Furthermore, in this embodiment, the hardened layer 11 formed on the outer periphery of the hub wheel 2 is stopped at the starting point of the outer arcuate surface 13b in the annular groove 13. Thereby, the workability of the cylindrical part 12 in the small diameter step part 2b can be improved, and the occurrence of cracks and the like due to plastic deformation can be prevented.

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、ハブ輪の小径段部に内輪を圧入し、小径段部の端部を塑性変形させて形成した加締部によって内輪を固定した第１世代乃至第３世代のセルフリテイン構造の車輪用軸受装置に適用できる。   In the wheel bearing device according to the present invention, the inner ring is fixed by a caulking portion formed by press-fitting an inner ring into a small-diameter step portion of a hub wheel and plastically deforming an end portion of the small-diameter step portion. It can be applied to a self-retained wheel bearing device.

本発明に係る車輪用軸受装置の一実施形態を示す縦断面図である。It is a longitudinal section showing one embodiment of a wheel bearing device concerning the present invention. 図１の加締前のハブ輪および内輪を示す要部拡大図である。It is a principal part enlarged view which shows the hub ring and inner ring | wheel before caulking of FIG. 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. 図３の加締前のハブ輪と内輪を示す要部拡大図である。It is a principal part enlarged view which shows the hub ring and inner ring | wheel before caulking of FIG.

符号の説明Explanation of symbols

１・・・・・・・・・内方部材
２・・・・・・・・・ハブ輪
２ａ、３ａ・・・・・内側転走面
２ｂ・・・・・・・・小径段部
２ｃ・・・・・・・・加締部
３・・・・・・・・・内輪
３ｂ・・・・・・・・大端面
３ｃ・・・・・・・・面取り部
４・・・・・・・・・車輪取付フランジ
５・・・・・・・・・ハブボルト
６・・・・・・・・・転動体
７・・・・・・・・・保持器
８、９・・・・・・・シール
１０・・・・・・・・外方部材
１０ａ・・・・・・・外側転走面
１０ｂ・・・・・・・車体取付フランジ
１１・・・・・・・・硬化層
１２・・・・・・・・円筒部
１２ａ・・・・・・・底面
１３・・・・・・・・環状溝
１３ａ、１３ｂ・・・円弧面
５１・・・・・・・・内方部材
５２・・・・・・・・ハブ輪
５２ａ、５３ａ・・・内側転走面
５２ｂ・・・・・・・小径段部
５２ｃ・・・・・・・加締部
５３・・・・・・・・内輪
５４・・・・・・・・車輪取付フランジ
５５・・・・・・・・ボール
５６・・・・・・・・保持器
５７、５８・・・・・シール
６０・・・・・・・・外方部材
６０ａ・・・・・・・外側転走面
６０ｂ・・・・・・・車体取付フランジ
７０・・・・・・・・円筒部
７１・・・・・・・・環状溝
ａ・・・・・・・・・円筒部の底面と内輪の端面の寸法
ｂ、ｎ・・・・・・・環状溝の深さ
ｃ・・・・・・・・・支持点と円弧面の起点との間隔
ｄ１・・・・・・・・円筒部の軸方向深さ
Ｄ１・・・・・・・・円筒部の根元部の肉厚
Ｄ２・・・・・・・・円筒部の先端部の肉厚
Ｐ・・・・・・・・・支持点
ｒ１・・・・・・・・内輪の面取り部の曲率半径
ｒ２・・・・・・・・環状溝の円弧面の曲率半径
Ｒｉ・・・・・・・・環状溝におけるインナー側の円弧面の曲率半径
Ｒｏ・・・・・・・・環状溝におけるアウター側の円弧面の曲率半径 1 ... inner member 2 ... hub wheels 2a, 3a ... inner rolling surface 2b ... small diameter step 2c ································································································· Chamfered portion 4 ··· Wheel mounting flange 5 ······································································· ··· Seal 10 ··· Outer member 10a ··· Outer rolling surface 10b ····· Body mounting flange 11 ··· Hardened layer 12 ... Cylindrical part 12a ......... Bottom surface 13 ......... Round groove 13a, 13b ... Arc surface 51 ......... Inner member 52 ... Hub wheels 52a, 53a ... Inner rolling surface 2b ····· Small diameter step 52c ··························································· ... Ball 56 ... Cage 57, 58 ... Seal 60 ... Outer member 60a ... Outer rolling surface 60b ... ····· Body mounting flange 70 ········································································ Dimensions b, n ... Depth of annular groove c ... ... Distance d1 between support point and starting point of arc surface ... ... Axial direction of cylindrical part Depth D1 ·························································································· .... Curvature radius of inner ring chamfer r2 ... .... Radius of curvature Ri of circular groove of annular groove ... Radius of curvature of inner circular face of annular groove Ro ... of outer circular face of annular groove curvature radius

Claims (5)

内周に複列の外側転走面が形成された外方部材と、
一端部に車輪取付フランジを一体に有し、この車輪取付フランジから軸方向に延びる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圧入された少なくとも一つの内輪からなり、外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、
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転動体とを備え、
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り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、
前記小径段部の加締前の端部が中空状の円筒部として形成され、この円筒部の外周面に０．５〜１．０ｍｍの深さで、両側に所定の曲率半径Ｒｉ、Ｒｏからなる円弧面を有する環状溝が形成され、これら円弧面のうちインナー側の円弧面の曲率半径Ｒｉがアウター側の円弧面の曲率半径Ｒｏよりも小さく設定されると共に、当該環状溝が、前記転動体と内側転走面との接触線の延長上と前記小径段部の外周面と交叉する点から所定の間隔をおいてインナー側に、かつ前記内輪の加締部側の面取り部にかかって大端面を越えて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 having a double row outer raceway formed on the inner periphery;
It has a wheel mounting flange integrally at one end, a hub wheel formed with a small diameter step portion extending in the axial direction from the wheel mounting flange, and at least one inner ring press-fitted into the small diameter step portion of the hub wheel, An inner member in which a double row inner rolling surface facing the outer row rolling surface of the double row is formed on the outer periphery;
A double-row rolling element accommodated between the rolling surfaces of the inner member and the outer member via a cage so as to freely roll,
In the wheel bearing device in which the inner ring is fixed in the axial direction by a caulking portion formed by plastically deforming an end portion of the small diameter step portion radially outward,
The end portion of the small-diameter step portion before caulking is formed as a hollow cylindrical portion, and has a depth of 0.5 to 1.0 mm on the outer peripheral surface of the cylindrical portion, with predetermined curvature radii Ri and Ro on both sides. An annular groove having an arc surface is formed, and the curvature radius Ri of the inner arc surface of these arc surfaces is set to be smaller than the curvature radius Ro of the outer arc surface. From the point of intersection of the contact line between the moving body and the inner rolling surface and the outer peripheral surface of the small-diameter stepped portion to the inner side at a predetermined interval and to the chamfered portion on the caulking portion side of the inner ring wheel bearing apparatus characterized in that it is a large end face Yue forte formation. 前記内輪における加締部側の内径端部の面取り部が所定の曲率半径ｒ１からなる円弧面を有し、この曲率半径ｒ１よりも、前記環状溝におけるインナー側の円弧面の曲率半径Ｒｉが大きく、ｒ１≦Ｒｉとなるように設定されている請求項１に記載の車輪用軸受装置。   The inner ring end chamfered portion of the inner ring has a circular arc surface having a predetermined radius of curvature r1, and the radius of curvature Ri of the inner circular surface of the annular groove is larger than the radius of curvature r1. The wheel bearing device according to claim 1, wherein the wheel bearing device is set to satisfy r1 ≦ Ri. 前記小径段部に高周波焼入れによって所定の硬化層が形成され、この硬化層が前記環状溝におけるアウター側の円弧面の起点で止められている請求項１または２に記載の車輪用軸受装置。   3. The wheel bearing device according to claim 1, wherein a predetermined hardened layer is formed on the small-diameter step portion by induction hardening, and the hardened layer is stopped at a starting point of an outer arc surface of the annular groove. 4. 前記円筒部における前記内輪の加締部側の大端面からの深さが前記環状溝の幅よりも小さく設定されている請求項１乃至３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 to 3, wherein a depth from a large end surface of the inner ring on the caulking portion side of the cylindrical portion is set smaller than a width of the annular groove. 前記円筒部における前記内輪の加締部側の大端面からの深さが０〜５ｍｍの範囲に設定されている請求項４に記載の車輪用軸受装置。
The wheel bearing device according to claim 4, wherein a depth of the inner ring from the large end surface of the inner ring on the caulking part side is set in a range of 0 to 5 mm.
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