JP2008256071A - Bearing for wheel and bearing device for wheel having the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing for a wheel reduced in weight, size, and cost, and improved in durability of the bearing, and to provide a bearing device for a wheel having the same. <P>SOLUTION: An outer member 7 and an inner ring 8 are formed of pipe members by cold rolling. When a diameter of a ball 10 is Dw, heights H of groove bottom diameters of outer rolling surfaces 7a of the outer member 7 and an inner diameter of an annular projection are set to meet an equation of H/Dw=0.30-0.43. Seals 11 are fitted in cylinders 13 formed at both ends of the outer member 7, shoulders 14 which are axially extended are formed at ends on large diameter sides of the inner ring and seal lips of the seals 11 are brought into slide-contact with the shoulders 14, and both rolling surfaces, fitting surfaces of the seals 11, and seal lands are formed into predetermined dimensions and accuracy by grinding. Therefore, the generation of cracks in the shoulders 22 is prevented, and the ride-on of contact ellipses of the balls 10 on the shoulders 22 in a turning moment load is prevented. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、自動車等の車両の車輪を回転自在に支承する車輪用軸受、詳しくは、軽量・コンパクト化と低コスト化を図ると共に、軸受の耐久性の向上を図った車輪用軸受およびこれを備え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 for rotatably supporting a wheel of a vehicle such as an automobile, and more particularly, to a wheel bearing for reducing the weight, size and cost, and improving the durability of the bearing. The present invention relates to a wheel bearing device provided.

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方部材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 both an inner ring rotation method and an outer member 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.

従来から、内輪および外輪（外方部材）が鋼板からプレス加工によって形成された構造のアンギュラ玉軸受が知られている。例えば、図５に示すアンギュラ玉軸受５０は、磁気ハードディスク装置等に使用されるものであるが、外輪５１および一対の内輪５２、５３は、ステンレス鋼板からプレス加工またはローリング加工によって形成されている。   Conventionally, an angular ball bearing having a structure in which an inner ring and an outer ring (outer member) are formed by pressing from a steel plate is known. For example, the angular ball bearing 50 shown in FIG. 5 is used in a magnetic hard disk device or the like, but the outer ring 51 and the pair of inner rings 52 and 53 are formed from a stainless steel plate by pressing or rolling.

外輪５１は、内周面の略中間部に径方向内方に突出する環状凸部５１ａが形成され、この環状凸部５１ａの両側の内周面に外側転走面５１ｂ、５１ｃが形成されている。この外輪５１は、外周面がハウジング５４の穴に嵌合され、一端部に形成されたフランジ５１ｄがハウジング５４の端面に当接されて、軸方向の位置決めが行われている。また、環状凸部５１ａにより、外輪５１の外周面には環状凹部５１ｅが形成され、この環状凹部５１ｅに接着剤が充填されてハウジング５４の穴に外輪５１が固定されている。   The outer ring 51 is formed with an annular convex portion 51a protruding radially inward at a substantially middle portion of the inner peripheral surface, and outer rolling surfaces 51b and 51c are formed on inner peripheral surfaces on both sides of the annular convex portion 51a. Yes. The outer ring 51 has an outer peripheral surface fitted into a hole in the housing 54, and a flange 51 d formed at one end is brought into contact with the end surface of the housing 54 to perform axial positioning. An annular recess 51e is formed on the outer peripheral surface of the outer ring 51 by the annular protrusion 51a. The annular recess 51e is filled with an adhesive, and the outer ring 51 is fixed to the hole of the housing 54.

一方、内輪５２、５３は、外輪５１の複列の外側転走面５１ｂ、５１ｃの内側に軸方向の両側からそれぞれ嵌合される。これら内輪５２、５３の軸方向外端外周には、湾曲肩部５２ａ、５３ａが形成され、この湾曲肩部５２ａ、５３ａに内側転走面５２ｂ、５３ｂが形成されている。そして、複列のボール５６、５６がこれらの内側転走面５２ｂ、５３ｂと外輪５１の複列の外側転走面５１ｂ、５１ｃとの間に配置され、保持器５７、５７により各列毎に保持されている。   On the other hand, the inner rings 52 and 53 are respectively fitted inside the double row outer raceway surfaces 51b and 51c of the outer ring 51 from both sides in the axial direction. Curved shoulder portions 52a and 53a are formed on the outer circumferences of the outer ends in the axial direction of the inner rings 52 and 53, and inner rolling surfaces 52b and 53b are formed on the curved shoulder portions 52a and 53a. The double rows of balls 56, 56 are arranged between the inner rolling surfaces 52b, 53b and the outer rolling surfaces 51b, 51c of the outer ring 51, and are retained by the cages 57, 57 for each row. Is retained.

内輪５２、５３の内周面には、軸部材５５に隙間嵌めされる嵌合部５２ｃ、５３ｃが形成されている。内輪５２、５３が軸部材５５に軸方向から隙間嵌めされた後、一方の内輪５２の湾曲肩部５２ａに重量が一定の円筒形の重錘５９が乗せられ、この重錘５９の重量により、内輪５２、ボール５６、外輪５１、ボール５６を経由して他方の内輪５３が押圧され、湾曲肩部５３ａが軸部材５５の鍔部５５ａに当接するまで嵌合される。これにより、アンギュラ玉軸受５０に適正な予圧が設定される。   On the inner peripheral surfaces of the inner rings 52 and 53, fitting portions 52c and 53c that are fitted into the shaft member 55 with clearance are formed. After the inner rings 52, 53 are fitted into the shaft member 55 in the axial direction, a cylindrical weight 59 having a constant weight is placed on the curved shoulder 52 a of one inner ring 52, and the weight of the weight 59 The other inner ring 53 is pressed via the inner ring 52, the ball 56, the outer ring 51, and the ball 56, and the curved shoulder portion 53 a is fitted until it comes into contact with the flange portion 55 a of the shaft member 55. Thereby, an appropriate preload is set for the angular ball bearing 50.

この隙間嵌めが完了すると、一方の内輪５２の湾曲肩部５２ａと軸部材５５との間の隙間に接着剤６０が充填され、この接着剤６０で一方の内輪５２の嵌め外れが防止されると共に、軸部材５５の鍔部５５ａで他方の内輪５３の嵌め外れが防止される。
実開平６−１８３５号公報 When this gap fitting is completed, the adhesive 60 is filled in the gap between the curved shoulder portion 52a of the one inner ring 52 and the shaft member 55, and this adhesive 60 prevents the one inner ring 52 from being fitted off. The flange portion 55a of the shaft member 55 prevents the other inner ring 53 from being fitted off.
Japanese Utility Model Publication No. 6-1835

然しながら、この種のプレス製のアンギュラ玉軸受を車輪用軸受として使用した場合、車両の旋回時等に負荷されるモーメント荷重によって、ボール５６の接触楕円が乗り上げて外側転走面５１ｂから外れる、所謂肩乗り上げが発生することがある。そして、この肩乗り上げによって肩部Ａにエッジロードが発生する恐れがあった。ここで、エッジロードとは、角部等に発生する過大な応力集中のことで、早期剥離の要因の一つとなる事象を言う。   However, when this type of angular contact ball bearing made of a press is used as a wheel bearing, a so-called contact ellipse of the ball 56 rides up and disengages from the outer rolling surface 51b due to a moment load applied when the vehicle turns or the like. Shoulder climb may occur. Then, there is a fear that edge loading may occur in the shoulder A due to the riding on the shoulder. Here, the edge load is an excessive stress concentration generated at a corner or the like, and refers to an event that becomes one of the factors of early peeling.

そこで、外輪５１のローリング加工時、外輪５１の中央部を凹ませて環状凸部５１ａを形成する際、外側転走面５１ｂから環状凸部５１ａの肩高さを高くすれば旋回モーメント負荷時にボール５６が肩部Ａを乗り上げ難くなるが、肩高さを高くすると絞り率が高くなり肩部Ａに亀裂が発生し易くなる恐れがあった。したがって、工程数を増やしてこの絞り率を低く抑えて亀裂の発生を防止することも考えられるが、これでは、製造コストが高騰するだけでなく、加工精度が低下して所望の軸受精度を確保することが困難であった。   Therefore, when the outer ring 51 is rolled, the center part of the outer ring 51 is recessed to form the annular convex part 51a, and if the shoulder height of the annular convex part 51a is increased from the outer rolling surface 51b, 56 becomes difficult to ride on the shoulder A, but if the shoulder height is increased, the squeezing rate increases and there is a risk that the shoulder A is likely to crack. Therefore, it is conceivable to increase the number of processes and keep the drawing ratio low to prevent cracking. However, this will not only increase the manufacturing cost but also reduce the machining accuracy to ensure the desired bearing accuracy. It was difficult to do.

本発明は、このような事情に鑑みてなされたもので、軽量・コンパクト化と低コスト化を図ると共に、軸受の耐久性の向上を図った車輪用軸受およびこれを備えた車輪用軸受装置を提供することを目的としている。   SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and provides a wheel bearing and a wheel bearing device including the wheel bearing that are designed to be lighter, more compact and lower in cost and to improve the durability of the bearing. It is intended to provide.

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、外周に前記複列の外側転走面に対向する円弧状の内側転走面が形成された一対の内輪と、これら内輪と前記外方部材の両転走面間に収容された複列のボールと、前記外方部材と内輪との間に形成される環状空間の開口部に装着されたシールとを備え、前記内輪の小径側端面が突合せ状態で衝合して背面合せタイプの複列のアンギュラ玉軸受を構成する車輪用軸受において、前記外方部材と内輪がパイプ材からローリング加工によって形成されると共に、前記ボールの直径をＤｗとした時、前記外方部材の外側転走面の溝底径と内径の高さＨが、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲になるように設定されている。   In order to achieve such an object, the invention according to 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 the double-row on the outer periphery. A pair of inner rings formed with an arcuate inner rolling surface facing the outer rolling surface, a double row of balls accommodated between the inner ring and both rolling surfaces of the outer member, and the outer member And a seal mounted in an opening of an annular space formed between the inner ring and the inner ring, and a small diameter side end face of the inner ring abuts in a butted state to constitute a back-to-back type double row angular ball bearing In the wheel bearing, the outer member and the inner ring are formed by rolling from a pipe material, and when the diameter of the ball is Dw, the groove bottom diameter and the inner diameter of the outer rolling surface of the outer member are high. H is set to be in the range of H / Dw = 0.30-0.43

このように、背面合せタイプの複列のアンギュラ玉軸受で構成された車輪用軸受において、外方部材と内輪がパイプ材からローリング加工によって形成されると共に、ボールの直径をＤｗとした時、外方部材の外側転走面の溝底径と内径の高さＨが、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲になるように設定されているので、所望の軸受精度を確保すると共に、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るのを防止することができ、軸受の耐久性の向上を図った車輪用軸受を提供することができる。   Thus, in the wheel bearing constituted by the back-to-back type double row angular contact ball bearing, when the outer member and the inner ring are formed by rolling from the pipe material and the ball diameter is Dw, Since the groove bottom diameter and the inner diameter height H of the outer rolling surface of the side member are set to be in the range of H / Dw = 0.30-0.43, the desired bearing accuracy is ensured. Provide wheel bearings that prevent cracks in the shoulders and prevent the ball contact ellipse from climbing over the shoulders when a turning moment is applied, improving bearing durability can do.

好ましくは、請求項２に記載の発明のように、前記両転走面および前記シールのランド部となる前記内輪の肩部が研削加工により所定の寸法、精度に形成されていれば、生産性が向上して歩溜まりが良く低コスト化ができると共に、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。   Preferably, as in the invention described in claim 2, if both the rolling surfaces and the shoulder portion of the inner ring serving as the land portion of the seal are formed with a predetermined size and accuracy by grinding, productivity is improved. Thus, the yield can be improved and the cost can be reduced, and the same accuracy and sealing performance as those of the conventional bearing can be secured.

また、請求項３に記載の発明のように、前記外方部材の両端部に円筒部がローリング加工により形成され、この円筒部に前記シールが内嵌されると共に、前記内輪の大径側の端部に軸方向に延びる肩部がローリング加工により形成され、この肩部に前記シールのシールリップが摺接されていれば、所望の密封性を確保することができる。   Further, as in the invention described in claim 3, cylindrical portions are formed at both end portions of the outer member by rolling processing, and the seal is fitted into the cylindrical portions, and on the large diameter side of the inner ring. If a shoulder portion extending in the axial direction is formed at the end portion by rolling, and the seal lip of the seal is in sliding contact with the shoulder portion, a desired sealing property can be ensured.

また、請求項４に記載の発明のように、前記シールが、断面が略Ｌ字状に形成され、互いに対向配置されたスリンガと環状のシール板とからなり、このシール板がサイドリップとラジアルリップとを有すると共に、前記外方部材の両端部に円筒部がローリング加工により形成され、この円筒部に前記シール板が内嵌され、前記内輪の大径側の端部に軸方向に延びる肩部がローリング加工により形成され、この肩部に前記スリンガが圧入され、このスリンガに前記シール板のシールリップが摺接されていれば、一層強固な密封性を得ることができる。   According to a fourth aspect of the present invention, the seal is formed of a slinger and an annular seal plate having a substantially L-shaped cross section and arranged to face each other, and the seal plate is a side lip and a radial seal plate. A cylindrical portion is formed at both ends of the outer member by rolling, and the seal plate is fitted into the cylindrical portion, and a shoulder extending in the axial direction at the large-diameter end of the inner ring If the portion is formed by rolling, the slinger is press-fitted into the shoulder, and the seal lip of the seal plate is slidably contacted with the slinger, a stronger sealing performance can be obtained.

また、請求項５に記載の発明のように、前記外方部材の両端面と前記内輪の大径側端面がローリング加工後に旋削加工されると共に、前記外方部材の外径面および前記内輪の内径面と小径側端面が研削加工によって所定の寸法、精度に形成されていれば、従来の軸受と同等の軸受精度を確保することができる。   Further, as in the invention described in claim 5, the both end faces of the outer member and the large-diameter side end face of the inner ring are turned after rolling, and the outer diameter surface of the outer member and the inner ring If the inner diameter surface and the small diameter side end surface are formed with predetermined dimensions and accuracy by grinding, the bearing accuracy equivalent to that of the conventional bearing can be ensured.

また、本発明のうち請求項６に記載の発明は、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肩部を介して軸方向に延びる小径段部が形成されたハブ輪と、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た前記請求項１乃至４いずれかに車輪用軸受とを備え、前記ハブ輪に等速自在継手の外側継手部材がセレーションを介して内嵌され、前記一対の内輪が前記ハブ輪の肩部と前記外側継手部材の肩部とで挟持され、所定の軸受予圧が付与されている。   The invention according to claim 6 of the present invention is a hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in an axial direction from the wheel mounting flange via a shoulder. And a wheel bearing according to any one of claims 1 to 4, which is press-fitted into the small-diameter step portion of the hub wheel via a predetermined shimiro, and the outer joint member of the constant velocity universal joint serrated on the hub wheel. And the pair of inner rings are sandwiched between a shoulder portion of the hub wheel and a shoulder portion of the outer joint member, and a predetermined bearing preload is applied.

このように、第１世代構造の車輪用軸受装置において、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肩部を介して軸方向に延びる小径段部が形成されたハブ輪と、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た前記請求項１乃至４いずれかに車輪用軸受とを備え、前記ハブ輪に等速自在継手の外側継手部材がセレーションを介して内嵌され、前記一対の内輪が前記ハブ輪の肩部と前記外側継手部材の肩部とで挟持され、所定の軸受予圧が付与されているので、軸受剛性が高くなると共に、軸受の転がり疲労寿命が向上する。   Thus, in the wheel bearing device of the first generation structure, a hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in the axial direction from the wheel mounting flange via the shoulder is formed. And a wheel bearing according to any one of claims 1 to 4, which is press-fitted into the small-diameter step portion of the hub wheel via a predetermined shimiro, and the outer joint member of the constant velocity universal joint serrated on the hub wheel. And the pair of inner rings are sandwiched between the shoulder part of the hub wheel and the shoulder part of the outer joint member, and a predetermined bearing preload is applied. Rolling fatigue life is improved.

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、外周に前記複列の外側転走面に対向する円弧状の内側転走面が形成された一対の内輪と、これら内輪と前記外方部材の両転走面間に収容された複列のボールと、前記外方部材と内輪との間に形成される環状空間の開口部に装着されるシールとを備え、前記内輪の小径側端面が突合せ状態で衝合して背面合せタイプの複列のアンギュラ玉軸受を構成する車輪用軸受において、前記外方部材と内輪がパイプ材からローリング加工によって形成されると共に、前記ボールの直径をＤｗとした時、前記外方部材の外側転走面の溝底径と内径の高さＨが、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲になるように設定されているので、所望の軸受精度を確保すると共に、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るのを防止することができ、軸受の耐久性の向上を図った車輪用軸受を提供することができる。   The wheel bearing device according to 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 arc-shaped outer surface facing the outer-rolling surface of the double-row on the outer periphery. A pair of inner rings formed with inner rolling surfaces, a double row of balls accommodated between both inner rings and the rolling surfaces of the outer member, and an annular formed between the outer member and the inner ring In a wheel bearing comprising a back-to-back type double-row angular contact ball bearing in which a small-diameter side end face of the inner ring abuts in a butted state, and a seal attached to an opening of the space. The inner ring is formed from a pipe material by rolling, and when the diameter of the ball is Dw, the groove bottom diameter and the inner diameter height H of the outer rolling surface of the outer member are H / Dw = 0. Since it is set to be in the range of 30 to 0.43, the desired bearing accuracy is ensured. In addition, it is possible to prevent the occurrence of cracks in the shoulder, and to prevent the contact ellipse of the ball from climbing over the shoulder when a turning moment is applied, thereby improving the bearing durability. Can be provided.

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、外周に前記複列の外側転走面に対向する円弧状の内側転走面が形成された一対の内輪と、これら内輪と前記外方部材の両転走面間に収容された複列のボールと、前記外方部材と内輪との間に形成される環状空間の開口部に装着されるシールとを備え、前記内輪の小径側端面が突合せ状態で衝合して背面合せタイプの複列のアンギュラ玉軸受を構成する車輪用軸受において、前記外方部材と内輪がパイプ材からローリング加工によって形成され、前記ボールの直径をＤｗとした時、前記外方部材の外側転走面の溝底径と内径の高さＨが、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲になるように設定されると共に、前記外方部材の両端部に形成された円筒部に前記シールが内嵌され、前記内輪の大径側の端部に軸方向に延びる肩部が形成されてこの肩部に前記シールのシールリップが摺接され、前記両転走面および前記シールの嵌合面とシールランド部が研削加工により所定の寸法、精度に形成されている。   A pair of outer members in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery, and an arc-shaped inner rolling surface facing the outer-rolling surface of the double-row is formed on the outer periphery. An inner ring, a double row of balls accommodated between the rolling surfaces of the inner ring and the outer member, and a seal attached to an opening of an annular space formed between the outer member and the inner ring. And the outer ring and the inner ring are formed by rolling from a pipe material in a bearing for a wheel that forms a back-to-back type double row angular contact ball bearing by abutting the end faces on the small diameter side of the inner ring in a butted state. When the diameter of the ball is Dw, the groove bottom diameter and the inner diameter height H of the outer rolling surface of the outer member are set to be in the range of H / Dw = 0.30-0.43. In addition, the seal is fitted into cylindrical portions formed at both ends of the outer member, A shoulder portion extending in the axial direction is formed at an end portion on the large diameter side of the inner ring, and a seal lip of the seal is slidably contacted with the shoulder portion, both the rolling surfaces, the fitting surface of the seal and the seal land portion Is formed with predetermined dimensions and accuracy by grinding.

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、図１の車輪用軸受を示す拡大図、図３（ａ）は図２の外方部材単体を示す縦断面図、（ｂ）は、図２の内輪単体を示す縦断面図、図４（ａ）は、図２の変形例を示す拡大図、（ｂ）は、（ａ）のシールを示す拡大図である。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.
1 is a longitudinal sectional view showing an embodiment of a wheel bearing device according to the present invention, FIG. 2 is an enlarged view showing the wheel bearing of FIG. 1, and FIG. 3 (a) is a single outer member of FIG. FIG. 4B is a longitudinal sectional view showing the single inner ring of FIG. 2, FIG. 4A is an enlarged view showing a modification of FIG. 2, and FIG. 4B is a seal of FIG. It is an enlarged view shown. 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第１世代構造をなし、ハブ輪１と、このハブ輪１に装着される車輪用軸受２とを備えている。ハブ輪１には等速自在継手３がトルク伝達自在に内嵌され、固定ナット４を介してハブ輪１と等速自在継手３が分離可能に一体化されている。   This wheel bearing device has a first generation structure, and includes a hub wheel 1 and a wheel bearing 2 attached to the hub wheel 1. A constant velocity universal joint 3 is fitted into the hub wheel 1 so as to be able to transmit torque, and the hub wheel 1 and the constant velocity universal joint 3 are detachably integrated via a fixing nut 4.

ハブ輪１は、アウター側の一端部に車輪（図示せず）を取り付けるための車輪取付フランジ５を有し、外周にこの車輪取付フランジ５から肩部１ａを介して軸方向に延びる円筒状の小径段部１ｂが形成され、内周にトルク伝達用のセレーション（またはスプライン）１ｃが形成されている。このハブ輪１はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、鍛造の生のままである。また、曲げ強度に対する疲労強度増加のために鍛造後に調質処理を行う方法や、肩部１ａから小径段部１ｂに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理をしても良い。   The hub wheel 1 has a wheel mounting flange 5 for mounting a wheel (not shown) at one end portion on the outer side, and a cylindrical shape extending from the wheel mounting flange 5 to the outer periphery in the axial direction via a shoulder portion 1a. A small-diameter step portion 1b is formed, and a serration (or spline) 1c for torque transmission is formed on the inner periphery. The hub wheel 1 is made of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and remains as forged. In addition, a method of performing a tempering treatment after forging in order to increase the fatigue strength with respect to the bending strength, or by subjecting the surface hardness to a range of 58 to 64 HRC by induction hardening from the shoulder portion 1a to the small diameter step portion 1b. May be.

車輪用軸受２はナックル６に内嵌され、図２に拡大して示すように、内周に複列の円弧状の外側転走面７ａ、７ａが形成された外方部材（外輪）７と、外周にこれら複列の外側転走面７ａ、７ａに対向する円弧状の内側転走面８ａ、８ａが形成された一対の内輪８、８と、両転走面間に保持器９、９を介して転動自在に収容された複列のボール１０、１０と、外方部材７の両端部に装着されたシール１１とを備えている。そして、内輪８、８の小径（正面）側端面８ｂ、８ｂを突合せ状態で衝合し、所謂背面合せタイプの複列のアンギュラ玉軸受を構成している。   The wheel bearing 2 is fitted into a knuckle 6, and as shown in an enlarged view in FIG. 2, an outer member (outer ring) 7 in which double-row arc-shaped outer rolling surfaces 7a and 7a are formed on the inner periphery. A pair of inner rings 8 and 8 having arcuate inner rolling surfaces 8a and 8a formed on the outer periphery and facing these double-row outer rolling surfaces 7a and 7a, and cages 9 and 9 between both rolling surfaces. And the double-row balls 10 and 10 accommodated so as to be freely rollable via each other, and the seals 11 attached to both ends of the outer member 7. The small diameter (front) side end faces 8b, 8b of the inner rings 8, 8 are abutted in a butted state to constitute a so-called back-to-back type double row angular ball bearing.

シール１１は、外方部材７の円筒部１３に嵌合される芯金１１ａと、この芯金１１ａに加硫接着等により一体に接合され、ニトリルゴム等のエラストマーからなるシール部材１１ｂからなり、一対のラジアルリップを備えている。そして、軸受内部に封入されたグリースの漏洩と、外部から雨水やダスト等の異物が軸受内部に侵入するのを防止している。   The seal 11 is composed of a core metal 11a fitted to the cylindrical portion 13 of the outer member 7, and a seal member 11b integrally joined to the core metal 11a by vulcanization adhesion or the like, and made of an elastomer such as nitrile rubber, It has a pair of radial lips. In addition, leakage of grease sealed in the bearing and foreign matter such as rainwater and dust from the outside are prevented from entering the bearing.

等速自在継手３は、図１に示すように、外側継手部材１５と、継手内輪１６とケージ１７およびトルク伝達ボール１８とを備えている。外側継手部材１５は、カップ状のマウス部１９と、このマウス部１９の底部となる肩部２０と、この肩部２０から軸方向に延びる軸部２１を一体に有している。軸部２１の外周にはハブ輪１のセレーション１ｃに係合するセレーション２１ａと、このセレーション２１ａの端部に雄ねじ２１ｂが形成されている。そして、肩部２０が内輪８の大端面と衝合するまでハブ輪１に外側継手部材１５がセレーション１ｃ、２１ａを介して内嵌され、一対の内輪８、８がハブ輪１の肩部１ａと外側継手部材１５の肩部２０に挟持された状態でハブ輪１の小径段部１ｂに所定のシメシロを介して圧入されている。さらに、雄ねじ２１ｂに固定ナット４を所定の締付トルクで緊締することにより所定の軸受予圧が付与されている。これにより、軸受剛性が高くなると共に、軸受の転がり疲労寿命が向上する。   As shown in FIG. 1, the constant velocity universal joint 3 includes an outer joint member 15, a joint inner ring 16, a cage 17, and a torque transmission ball 18. The outer joint member 15 integrally includes a cup-shaped mouth portion 19, a shoulder portion 20 that is a bottom portion of the mouth portion 19, and a shaft portion 21 that extends from the shoulder portion 20 in the axial direction. A serration 21a that engages with the serration 1c of the hub wheel 1 is formed on the outer periphery of the shaft portion 21, and a male screw 21b is formed at the end of the serration 21a. The outer joint member 15 is fitted into the hub wheel 1 via the serrations 1c and 21a until the shoulder 20 abuts the large end surface of the inner ring 8, and the pair of inner rings 8 and 8 is the shoulder 1a of the hub ring 1. The outer joint member 15 is press-fitted into the small-diameter step portion 1b of the hub wheel 1 through a predetermined squeeze while being sandwiched between the shoulder portions 20 of the outer joint member 15. Further, a predetermined bearing preload is applied to the male screw 21b by tightening the fixing nut 4 with a predetermined tightening torque. As a result, the bearing rigidity is increased and the rolling fatigue life of the bearing is improved.

ここで、外方部材７および内輪８は、ＳＵＪ２等の軸受鋼やＳＣｒ４２０やＳＣＭ４１５等の浸炭鋼からなるパイプ材を冷間のローリング加工によって形成されている。そして、ＳＵＪ２はズブ焼や高周波焼入れ、浸炭鋼は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７および内輪８の材質としてこれ以外にも、ＳＣＭ４４０や冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）やＳ５３Ｃ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７においては複列の外側転走面７ａ、７ａが、また、内輪８においては内側転走面８ａ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、転がり疲労寿命を向上させている。そして、これらの転走面７ａ、８ａは、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。   Here, the outer member 7 and the inner ring 8 are formed by cold rolling a pipe material made of bearing steel such as SUJ2 or carburized steel such as SCr420 or SCM415. Then, SUJ2 is hardened to a surface hardness of 50 to 64 HRC by submerged or induction hardening, and carburized steel is carburized and quenched. Other examples of the material of the outer member 7 and the inner ring 8 include carbon steel such as SCM440, cold rolled steel plate (JIS standard SPCC system, etc.), S53C, and the like. In the case of cold rolled steel or carbon steel, at least the outer member 7 has double-row outer rolling surfaces 7a and 7a, and in the inner ring 8, the inner rolling surface 8a has a surface hardness of 50 by induction hardening. A hardening treatment is applied in a range of ˜64 HRC to improve the rolling fatigue life. These rolling surfaces 7a and 8a are formed with predetermined dimensions and accuracy by grinding. After that, superfinishing is performed as necessary.

次に、図３を用いて、外方部材７および内輪８の構成について詳細に説明する。
外方部材７は、（ａ）に示すように、素材となるパイプ材から内周に冷間のローリング加工により、径方向内方に突出する環状凸部１２と、この環状凸部１２の両側に複列の円弧状の外側転走面７ａ、７ａが形成されると共に、両端部にシール１１の嵌合部となる円筒部１３、１３が形成される。ここで、この円筒部１３は、冷間のローリング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。なお、ローリング加工でバリが発生する両端面はローリング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。 Next, the configuration of the outer member 7 and the inner ring 8 will be described in detail with reference to FIG.
The outer member 7 includes, as shown in (a), an annular protrusion 12 that protrudes radially inward from the pipe material, which is a raw material, by cold rolling, and both sides of the annular protrusion 12. In addition, double-row arc-shaped outer rolling surfaces 7a and 7a are formed, and cylindrical portions 13 and 13 serving as fitting portions of the seal 11 are formed at both ends. Here, the cylindrical portion 13 is formed with a predetermined size and accuracy by grinding after cold rolling. Note that both end surfaces where burrs are generated in the rolling process are turned after the rolling process. Moreover, a grinding process is given as needed.

一方、内輪８は、（ｂ）に示すように、素材となるパイプ材から冷間のローリング加工により、円弧状の内側転走面８ａと、この内側転走面８ａから軸方向に延びる肩部１４が形成される。ここで、この肩部１４はシール１１のシールランド部となり、冷間のローリング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。なお、外方部材７と同様、ローリング加工でバリが発生する両端面はローリング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。   On the other hand, as shown in (b), the inner ring 8 includes an arc-shaped inner rolling surface 8a and a shoulder portion extending in the axial direction from the inner rolling surface 8a by cold rolling from a pipe material as a material. 14 is formed. Here, the shoulder portion 14 becomes a seal land portion of the seal 11 and is formed with a predetermined size and accuracy by grinding after cold rolling. As with the outer member 7, both end surfaces where burrs are generated in the rolling process are turned after the rolling process. Moreover, a grinding process is given as needed.

本実施形態では、外方部材７および内輪８がパイプ材から冷間のローリング加工で形成されると共に、両転走面７ａ、８ａとシール１１の嵌合面となる外方部材７の円筒部１３、およびシール１１のランド部となる内輪８の肩部１４が研削加工によって形成されているので、生産性が向上して歩溜まりが良く、また、低コスト化ができると共に、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。   In this embodiment, the outer member 7 and the inner ring 8 are formed by cold rolling from a pipe material, and the cylindrical portion of the outer member 7 that serves as a fitting surface between the rolling surfaces 7 a and 8 a and the seal 11. 13 and the shoulder portion 14 of the inner ring 8 that becomes the land portion of the seal 11 are formed by grinding, so that the productivity is improved, the yield is good, the cost can be reduced, and the conventional bearing Equivalent accuracy and sealing performance can be ensured.

ここで、ローリング加工によって環状凸部１２を形成する場合、外側転走面７ａから環状凸部１２に繋がる肩部２２のＲ（曲率半径）は、素材の充足度や亀裂の発生を抑制するという観点から単に小さくすれば良いという訳ではないので、外側転走面７ａを研削加工する際、研削される範囲がどうしても限定される。したがって、本実施形態では、肩高さ、すなわち、ローリング加工において、外側転走面７ａの溝底径と環状凸部１２の内径の高さＨ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１０の直径をＤｗとした時、この肩高さＨをボール１０の直径Ｄｗで割った値が、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲、好ましくは、Ｈ／Ｄｗ＝０．３５〜０．４０の範囲になるように設定されている。これにより、所望の軸受精度を確保すると共に、肩部２２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１０の接触楕円が肩部２２を乗り上げるのを防止することができる。   Here, when the annular convex portion 12 is formed by rolling, the R (curvature radius) of the shoulder portion 22 connected to the annular convex portion 12 from the outer rolling surface 7a suppresses the material satisfaction and the generation of cracks. Since it is not necessary to simply reduce the size from the viewpoint, the grinding range is inevitably limited when the outer rolling surface 7a is ground. Therefore, in the present embodiment, the shoulder height, that is, the rolling process, the groove bottom diameter of the outer rolling surface 7a and the height H of the inner diameter of the annular convex portion 12 are set within a predetermined range. . Specifically, when the diameter of the ball 10 is Dw, a value obtained by dividing the shoulder height H by the diameter Dw of the ball 10 is in a range of H / Dw = 0.30 to 0.43, preferably H /Dw=0.35 to 0.40. As a result, it is possible to ensure the desired bearing accuracy, to prevent the shoulder portion 22 from cracking, and to prevent the contact ellipse of the ball 10 from riding on the shoulder portion 22 when a turning moment is applied.

このＨ／Ｄｗが０．３０未満では、通常の接触角２５〜３５°で、旋回モーメント負荷時にボール１０の接触楕円が肩部２２を乗り上げる恐れがあり、また、Ｈ／Ｄｗが０．４３を超えると、絞り率が高くなって肩部２２に亀裂が発生し易くなるからである。   If this H / Dw is less than 0.30, the contact ellipse of the ball 10 may ride on the shoulder 22 when a turning moment is applied at a normal contact angle of 25 to 35 °, and H / Dw is 0.43. This is because if it exceeds, the squeezing ratio becomes high and cracks are likely to occur in the shoulder portion 22.

なお、ここでは、外方部材７と内輪８を冷間のローリング加工によって形成したが、これに限らず、温間のローリング加工によって形成しても良く、また、ナックル６やハブ輪１の嵌合面となる外方部材７の外径面および内輪８の内径面、さらには突合せ面となる内輪８の小径側端面８ｂを研削加工によって形成しても良い。   Here, the outer member 7 and the inner ring 8 are formed by cold rolling. However, the outer member 7 and the inner ring 8 may be formed by warm rolling, and the fitting of the knuckle 6 or the hub wheel 1 may be performed. The outer diameter surface of the outer member 7 serving as the mating surface, the inner diameter surface of the inner ring 8, and the small-diameter side end surface 8b of the inner ring 8 serving as the butting surface may be formed by grinding.

図４（ａ）は、前述した実施形態（図２）の変形例であるが、シールの構成のみが異なっている。なお、前述した実施形態と同一部品同一部位あるいは同一機能を有する部品、部位には同じ符号を付して詳細な説明を省略する。   FIG. 4A is a modification of the above-described embodiment (FIG. 2), but only the configuration of the seal is different. The same parts and parts as those in the above-described embodiment or parts and parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

この車輪用軸受２３は、外方部材７と一対の内輪８、８と、両転走面間に保持器９、９を介して転動自在に収容された複列のボール１０、１０と、外方部材７と内輪８との間に形成される環状空間の開口部に装着されたシール２４とを備えている。   The wheel bearing 23 includes an outer member 7, a pair of inner rings 8, 8, and double-row balls 10, 10 accommodated so as to be able to roll between the rolling surfaces via the cages 9, 9, And a seal 24 attached to an opening of an annular space formed between the outer member 7 and the inner ring 8.

シール２４は、（ｂ）に拡大して示すように、互いに対向配置されたスリンガ２５と環状のシール板２６とからなる、所謂パックシールで構成されている。スリンガ２５は、オーステナイト系ステンレス鋼鈑（ＪＩＳ規格のＳＵＳ３０４系等）、あるいは、防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）等からプレス加工にて断面が略Ｌ字状に形成され、内輪８の肩部１４に圧入される円筒部２５ａと、この円筒部２５ａから径方向外方に延びる立板部２５ｂとからなる。   The seal 24 is constituted by a so-called pack seal composed of a slinger 25 and an annular seal plate 26 arranged to face each other as shown in an enlarged view in FIG. The slinger 25 has a substantially L-shaped cross section when it is pressed from an austenitic stainless steel plate (JIS standard SUS304, etc.) or a rust-proof cold rolled steel plate (JIS standard SPCC, etc.). A cylindrical portion 25a that is press-fitted into the shoulder portion 14 of the inner ring 8, and a standing plate portion 25b that extends radially outward from the cylindrical portion 25a.

シール板２６は断面略Ｌ字状に形成され、外方部材７の円筒部１３に圧入される芯金２７と、この芯金２７に加硫接着等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）、あるいは、防錆処理された冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）等からプレス加工にて形成されている。   The seal plate 26 is formed in a substantially L-shaped cross section, and includes a core metal 27 press-fitted into the cylindrical portion 13 of the outer member 7, and a seal member 28 integrally joined to the core metal 27 by vulcanization adhesion or the like. Become. The core metal 27 is formed by press working from 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).

一方、シール部材２８はニトリルゴム等の弾性部材からなり、スリンガ２５の立板部２５ｂに摺接するサイドリップ２８ａと、円筒部２５ａに摺接し、二股状に形成されたラジアルリップ２８ｂ、２８ｃとを有している。そして、スリンガ２５における立板部２５ｂの外縁と芯金２７とを僅かな径方向すきまを介して対峙させてラビリンスシールが構成され、外部から雨水やダスト等が直接サイドリップ２８ａに降りかかるのを防止して密封性を向上させている。   On the other hand, the sealing member 28 is made of an elastic member such as nitrile rubber, and includes a side lip 28a that is in sliding contact with the standing plate portion 25b of the slinger 25, and a radial lip 28b and 28c that are in sliding contact with the cylindrical portion 25a and formed in a bifurcated shape. Have. A labyrinth seal is formed by allowing the outer edge of the standing plate portion 25b of the slinger 25 and the cored bar 27 to face each other through a slight radial clearance, thereby preventing rainwater, dust, etc. from directly falling on the side lip 28a from the outside. And improve the sealing performance.

本実施形態においても、生産性が向上して歩溜まりが良く、低コスト化ができると共に、両転走面７ａ、８ａとシール２３の嵌合面となる外方部材７の円筒部１３および内輪８の肩部１４が研削加工によって形成されているので、従来の軸受と同等の精度を確保し、一層強固な密封性を得ることができる。   Also in the present embodiment, the productivity is improved, the yield is good, the cost can be reduced, and the cylindrical portion 13 and the inner ring of the outer member 7 serving as a fitting surface between the rolling surfaces 7a and 8a and the seal 23 are also provided. Since the eight shoulder portions 14 are formed by grinding, it is possible to ensure the same accuracy as that of a conventional bearing and obtain a stronger sealing performance.

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、一端部に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た一対の内輪とを備えた第１世代構造の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 having a first generation structure including a hub wheel integrally having a wheel mounting flange at one end and a pair of inner rings press-fitted into the hub wheel. .

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の車輪用軸受を示す拡大図である。It is an enlarged view which shows the wheel bearing of FIG. （ａ）は、図２の外方部材輪単体を示す縦断面図である。 （ｂ）は、同上、内輪単体を示す縦断面図である。(A) is a longitudinal cross-sectional view which shows the outer member ring single-piece | unit of FIG. (B) is the longitudinal cross-sectional view which shows an inner ring single-piece | unit as above. （ａ）は、図２の車輪用軸受の変形例を示す拡大図である。 （ｂ）は、（ａ）のシールを示す拡大図である。(A) is an enlarged view which shows the modification of the wheel bearing of FIG. (B) is an enlarged view showing the seal of (a). 従来の内・外輪がプレス加工によって形成された構造のアンギュラ玉軸受を示す縦断面図である。It is a longitudinal cross-sectional view which shows the angular contact ball bearing of the structure where the conventional inner and outer ring | wheel was formed by press work.

符号の説明Explanation of symbols

１・・・・・・・・・・・・・・・・ハブ輪
１ａ、１４、２０、２２・・・・・・肩部
１ｂ・・・・・・・・・・・・・・・小径段部
１ｃ、２１ａ・・・・・・・・・・・セレーション
２、２３・・・・・・・・・・・・・車輪用軸受
３・・・・・・・・・・・・・・・・等速自在継手
４・・・・・・・・・・・・・・・・固定ナット
５・・・・・・・・・・・・・・・・車輪取付フランジ
６・・・・・・・・・・・・・・・・ナックル
７・・・・・・・・・・・・・・・・外方部材
７ａ・・・・・・・・・・・・・・・外側転走面
８・・・・・・・・・・・・・・・・内輪
８ａ・・・・・・・・・・・・・・・内側転走面
８ｂ・・・・・・・・・・・・・・・小径側端面
９・・・・・・・・・・・・・・・・保持器
１０・・・・・・・・・・・・・・・ボール
１１、２４・・・・・・・・・・・・シール
１１ａ、２７・・・・・・・・・・・芯金
１１ｂ、２８・・・・・・・・・・・シール部材
１２・・・・・・・・・・・・・・・環状凸部
１３、２５ａ・・・・・・・・・・・円筒部
１５・・・・・・・・・・・・・・・外側継手部材
１６・・・・・・・・・・・・・・・継手内輪
１７・・・・・・・・・・・・・・・ケージ
１８・・・・・・・・・・・・・・・トルク伝達ボール
１９・・・・・・・・・・・・・・・マウス部
２１・・・・・・・・・・・・・・・軸部
２１ｂ・・・・・・・・・・・・・・雄ねじ
２５・・・・・・・・・・・・・・・スリンガ
２５ｂ・・・・・・・・・・・・・・立板部
２６・・・・・・・・・・・・・・・シール板
２８ａ・・・・・・・・・・・・・・サイドリップ
２８ｂ、２８ｃ・・・・・・・・・・ラジアルリップ
５０・・・・・・・・・・・・・・・アンギュラ玉軸受
５１・・・・・・・・・・・・・・・外輪
５１ａ・・・・・・・・・・・・・・環状凸部
５１ｂ、５１ｃ・・・・・・・・・・外側転走面
５１ｄ・・・・・・・・・・・・・・フランジ
５１ｅ・・・・・・・・・・・・・・環状凹部
５２、５３・・・・・・・・・・・・内輪
５２ａ、５３ａ・・・・・・・・・・湾曲肩部
５２ｂ、５３ｂ・・・・・・・・・・内側転走面
５２ｃ、５３ｃ・・・・・・・・・・嵌合部
５４・・・・・・・・・・・・・・・ハウジング
５５・・・・・・・・・・・・・・・軸部材
５５ａ・・・・・・・・・・・・・・鍔部
５６・・・・・・・・・・・・・・・ボール
５７・・・・・・・・・・・・・・・保持器
５９・・・・・・・・・・・・・・・重錘
６０・・・・・・・・・・・・・・・接着剤
Ａ・・・・・・・・・・・・・・・・肩部 1 ················ Hub wheel 1a, 14, 20, 22 ··· shoulder 1b ········ Small diameter step 1c, 21a ... Serration 2, 23 ... Wheel bearing 3 ...・ ・ ・ ・ Constant velocity universal joint 4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Fixing nut 5 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 6 ・ ・.... Knuckle 7 ... Outer member 7a ...・ Outer rolling surface 8 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner ring 8a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 8b ・ ・ ・ ・ ・ ・······· Small diameter side end face 9 ·········································· ... Balls 11, 24 ... Seals 11a, 27 ... Core metal 11b, 28 ... ··· Seal member 12 ······················································································· ... outer joint member 16 ... joint inner ring 17 ... cage 18 ... ·········· Torque transmission ball 19 ···························· ··························································· Slinger 25b ······················ ..... seal plate 28a ...・ ・ ・ ・ ・ Side lip 28b, 28c ・ ・ ・ ・ ・ Radial lip 50 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Angular ball bearing 51 ・ ・ ・ ・ ・ ・ ・ ・········ Outer ring 51a ············································· ... Flange 51e ... Ring recesses 52, 53 ... Inner rings 52a, 53a ... ... curved shoulders 52b, 53b ... inner rolling surfaces 52c, 53c ... fitting part 54 ...・ ・ ・ ・ ・ ・ ・ Housing 55 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shaft member 55a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hut 56 ・ ・ ・ ・ ・ ・... ball 57 ... ····································································· Adhesive A・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shoulder

Claims (6)

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、
外周に前記複列の外側転走面に対向する円弧状の内側転走面が形成された一対の内輪と、
これら内輪と前記外方部材の両転走面間に収容された複列のボールと、
前記外方部材と内輪との間に形成される環状空間の開口部に装着されたシールとを備え、前記内輪の小径側端面が突合せ状態で衝合して背面合せタイプの複列のアンギュラ玉軸受を構成する車輪用軸受において、
前記外方部材と内輪がパイプ材からローリング加工によって形成されると共に、前記ボールの直径をＤｗとした時、前記外方部材の外側転走面の溝底径と内径の高さＨが、Ｈ／Ｄｗ＝０．３０〜０．４３の範囲になるように設定されていることを特徴とする車輪用軸受。 An outer member in which a double-row arc-shaped outer rolling surface is integrally formed on the inner periphery;
A pair of inner rings each having an arcuate inner rolling surface facing the double row outer rolling surface on the outer periphery;
A double row of balls accommodated between both rolling surfaces of the inner ring and the outer member;
A double-sided angular contact ball of a back-to-back type in which a small-diameter side end face of the inner ring abuts in a butted state, and a seal attached to an opening of an annular space formed between the outer member and the inner ring In the wheel bearing constituting the bearing,
When the outer member and the inner ring are formed from a pipe material by rolling, and the diameter of the ball is Dw, the groove bottom diameter and the inner diameter height H of the outer rolling surface of the outer member are H /Dw=0.30-0.43 It is set so that it may become the range, The wheel bearing characterized by the above-mentioned. 前記両転走面および前記シールのランド部または嵌合部となる前記内輪の肩部が研削加工により所定の寸法、精度に形成されている請求項１に記載の車輪用軸受。   The wheel bearing according to claim 1, wherein both the rolling surfaces and a shoulder portion of the inner ring that becomes a land portion or a fitting portion of the seal are formed with a predetermined size and accuracy by grinding. 前記外方部材の両端部に円筒部がローリング加工により形成され、この円筒部に前記シールが内嵌されると共に、前記内輪の大径側の端部に軸方向に延びる肩部がローリング加工により形成され、この肩部に前記シールのシールリップが摺接されている請求項１または２に記載の車輪用軸受。   Cylindrical portions are formed at both ends of the outer member by rolling processing, and the seal is fitted into the cylindrical portion, and a shoulder portion extending in the axial direction at the end portion on the large diameter side of the inner ring is formed by rolling processing. The wheel bearing according to claim 1, wherein a seal lip of the seal is formed in sliding contact with the shoulder portion. 前記シールが、断面が略Ｌ字状に形成され、互いに対向配置されたスリンガと環状のシール板とからなり、このシール板がサイドリップとラジアルリップとを有すると共に、前記外方部材の両端部に円筒部がローリング加工により形成され、この円筒部に前記シール板が内嵌され、前記内輪の大径側の端部に軸方向に延びる肩部がローリング加工により形成され、この肩部に前記スリンガが圧入され、このスリンガに前記シール板のシールリップが摺接されている請求項１または２に記載の車輪用軸受。   The seal is formed of a slinger and an annular seal plate having a substantially L-shaped cross section and arranged to face each other. The seal plate has a side lip and a radial lip, and both end portions of the outer member. A cylindrical portion is formed by rolling processing, and the sealing plate is fitted into the cylindrical portion, and a shoulder portion extending in the axial direction is formed by rolling processing on the end portion on the large diameter side of the inner ring. The wheel bearing according to claim 1 or 2, wherein a slinger is press-fitted, and a seal lip of the seal plate is slidably contacted with the slinger. 前記外方部材の両端面と前記内輪の大径側端面がローリング加工後に旋削加工されると共に、前記外方部材の外径面および前記内輪の内径面と小径側端面が研削加工によって所定の寸法、精度に形成されている請求項１乃至４いずれかに記載の車輪用軸受。   Both end surfaces of the outer member and the large-diameter side end surface of the inner ring are turned after rolling, and the outer-diameter surface of the outer member and the inner-diameter surface and the small-diameter side end surface of the inner ring have predetermined dimensions by grinding. The wheel bearing according to claim 1, wherein the wheel bearing is formed with high accuracy. 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肩部を介して軸方向に延びる小径段部が形成されたハブ輪と、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た前記請求項１乃至５いずれかに記載の車輪用軸受とを備え、前記ハブ輪に等速自在継手の外側継手部材がセレーションを介して内嵌され、前記一対の内輪が前記ハブ輪の肩部と前記外側継手部材の肩部とで挟持され、所定の軸受予圧が付与されていることを特徴とする車輪用軸受装置。   A hub wheel integrally having a wheel mounting flange at one end and having a small-diameter step portion extending in the axial direction from the wheel mounting flange via a shoulder portion, and a predetermined squeeze through a small-diameter step portion of the hub wheel And a wheel bearing according to any one of claims 1 to 5, wherein an outer joint member of a constant velocity universal joint is fitted into the hub wheel via a serration, and the pair of inner rings are connected to the hub. A wheel bearing device characterized by being sandwiched between a shoulder portion of a ring and a shoulder portion of the outer joint member and given a predetermined bearing preload.

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