JP2009002369A - Bearing device for wheel - Google Patents

Bearing device for wheel Download PDF

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Publication number
JP2009002369A
JP2009002369A JP2007161216A JP2007161216A JP2009002369A JP 2009002369 A JP2009002369 A JP 2009002369A JP 2007161216 A JP2007161216 A JP 2007161216A JP 2007161216 A JP2007161216 A JP 2007161216A JP 2009002369 A JP2009002369 A JP 2009002369A
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Prior art keywords
wheel
bearing
wheel bearing
bearing device
knuckle
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JP2007161216A
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JP4940027B2 (en
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Keizo Kobayashi
圭三 小林
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/588—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
    • 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
    • F16C35/067—Fixing them in a 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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device for a wheel reduced in weight, size and cost, in which preload degradation and bearing creep caused by temperature rise are prevented. <P>SOLUTION: A bearing 3 for a wheel is constituted of a double row angular contact ball bearing of a back-to-back duplex type comprising: an external member 12 having an annular recess part 18 at a center part of an outer periphery and having a double rows of outer rolling surfaces 12a formed at an inner periphery; a pair of inner rings 13 having an inner rolling surface 13a formed to its outer periphery and a shoulder part 20 extended from the inner rolling surface in an axial direction; and a double rows of balls 15 housed between the inner rings 13 and the external member 12, wherein the inner rings 13 are caught between a shoulder part 1a of a hub wheel 1 and a shoulder part 9 of an outer joint member 8 and a bearing preload is applied thereto. The external member 12 and the inner rings 13 are made of pipe materials by cold rolling processing, and the annular recess part 18 of the external member 12, and an annular recess part 22 extended from the inner periphery of the shoulder part 20 of the inner ring 13 to a chamfered part 13c, are filled with resin bands 21, 23 made from heat-resistant synthetic resin by injection molding. <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装置、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 wheel of a vehicle such as an automobile, and more particularly, to a wheel bearing device that achieves weight reduction, compactness, and cost reduction and also improves bearing durability. Is.

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（外方部材）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 are formed from a steel plate by pressing 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 (outer member) 51 and the pair of inner rings 52 and 53 are made of stainless steel by pressing or rolling. Is formed.

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

この種のプレス製のアンギュラ玉軸受５０を車輪用軸受として使用した場合、予圧抜けを防止するためにアンギュラ玉軸受５０の初期予圧量を高く設定すると、当然のことながらアンギュラ玉軸受５０に余分な荷重を常時負荷することになって軸受寿命が短くなる。また、温度変化によって予圧量が大きく変化するに伴い軸受剛性が変動し、車両の走行安定性に悪影響を及ぼす。さらには、クリープを防止するために初期のシメシロを大きく設定すると、アンギュラ玉軸受５０を圧入する時にハウジング（ナックル）５４をかじる恐れがあるため、ハウジング５４を予め加熱した状態でアンギュラ玉軸受５０を圧入する必要がある。これでは組立工数がアップしてコスト高騰を招来することになる。ここで、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。   When this type of angular contact ball bearing 50 made of a press is used as a wheel bearing, if the initial preload amount of the angular ball bearing 50 is set high in order to prevent preload loss, it is a matter of course that extra angular ball bearing 50 is added. The bearing life is shortened because the load is always applied. Further, the bearing rigidity varies as the preload amount greatly changes due to temperature change, which adversely affects the running stability of the vehicle. Furthermore, if the initial squeeze is set large in order to prevent creep, the angular contact ball bearing 50 may be gnawed when the angular ball bearing 50 is press-fitted. It is necessary to press fit. This increases the number of assembly steps and causes a cost increase. Here, creep refers to a phenomenon in which the bearing surface slightly moves in the circumferential direction due to a lack of mating squealing or poor mating surface processing accuracy, and the mating surface becomes a mirror surface, and in some cases, seizure or welding occurs with galling. .

本発明は、このような事情に鑑みてなされたもので、軽量化を図った軽合金製ナックルに装着され、軽量・コンパクト化と低コスト化を図ると共に、温度上昇による予圧低下と軸受クリープを防止し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 is mounted on a light alloy knuckle that is reduced in weight to reduce weight, reduce size, reduce costs, reduce preload due to temperature rise, and reduce bearing creep. It aims at providing the bearing device for wheels which prevented.

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、一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、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、このハブ輪にセレーションを介して内嵌された等速自在継手の外側継手部材と、懸架装置を構成するナックルと、このナックルと前記ハブ輪の小径段部との間に所定のシメシロで嵌合された車輪用軸受とを備え、この車輪用軸受を介して前記ハブ輪が前記ナックルに対して回転自在に支承されている車輪用軸受装置において、前記車輪用軸受が、外周の中央部に環状凹部を有し、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を備え、前記一対の内輪が、その小径側端面が突合せ状態で衝合して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た背面合せタイプの複列のアンギュラ玉軸受からなると共に、前記外方部材と内輪がパイプ材から塑性加工によって形成され、前記外方部材の環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されている。   In order to achieve such an object, the invention according to claim 1 of the present invention has a wheel mounting flange for mounting a wheel at one end portion, and axially extends from the wheel mounting flange via a shoulder portion. A hub wheel formed with an extending small-diameter stepped portion, an outer joint member of a constant velocity universal joint fitted into the hub wheel via serrations, a knuckle constituting a suspension device, and a small diameter of the knuckle and the hub wheel A wheel bearing device fitted with a predetermined squeeze between the stepped portion and a wheel bearing device in which the hub wheel is rotatably supported with respect to the knuckle via the wheel bearing; The wheel bearing includes an outer member having an annular recess in the central portion of the outer periphery, a double-row arc-shaped outer rolling surface formed integrally on the inner periphery, and the double-row outer rolling on the outer periphery. An arc-shaped inner rolling surface that faces the surface is formed The inner ring and a double row of balls accommodated between the inner ring and the rolling surfaces of the outer member, and the pair of inner rings abut each other with the small-diameter side end faces butting the hub ring. A back-to-back type double row angular contact ball bearing which is sandwiched between the shoulder portion of the outer joint member and the shoulder portion of the outer joint member and applied with a predetermined bearing preload, and the outer member and the inner ring are formed from a pipe material by plastic working. A resin band made of heat-resistant synthetic resin is filled in the annular recess of the outer member by injection molding.

このように、一端部に車輪取付フランジを有し、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、このハブ輪にセレーションを介して内嵌された外側継手部材と、懸架装置を構成するナックルと、このナックルと小径段部との間に嵌合された車輪用軸受とを備えた第１世代構造の車輪用軸受装置において、車輪用軸受が、外周の中央部に環状凹部を有し、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を備え、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と共に、外方部材と内輪がパイプ材から塑性加工によって形成され、外方部材の環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されているので、温度上昇時、ナックルと車輪用軸受の線膨張係数の違いにより、ナックルが車輪用軸受以上に熱膨張したとしても、嵌合シメシロの低下を抑制し、軸受クリープの発生を防止することができると共に、初期に設定した軸受予圧が低下するのを防止することができ、軸受剛性の変動を抑えて車両の走行安定性を確実に保つことができる。   As described above, a hub wheel having a wheel mounting flange 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 the hub wheel is internally fitted via serrations. In the wheel bearing device of the first generation structure provided with the outer joint member, the knuckle constituting the suspension device, and the wheel bearing fitted between the knuckle and the small diameter step portion, An outer member having an annular recess in the central portion of the outer periphery, and a double row arc-shaped outer rolling surface formed integrally on the inner periphery, and a circle facing the outer rolling surface of the double row on the outer periphery A pair of inner rings formed with arc-shaped inner rolling surfaces, and a double row of balls accommodated between the inner rings and both rolling surfaces of the outer member, and the end surfaces on the small diameter side of the inner rings collide with each other. Combined to form a back-to-back double-row angular contact ball bearing and an outer member The inner ring is formed from pipe material by plastic working, and the resin recess made of heat-resistant synthetic resin is filled in the annular recess of the outer member by injection molding, so when the temperature rises, the linear expansion coefficient of the knuckle and wheel bearing Because of this difference, even if the knuckle expands more than the wheel bearing, it is possible to suppress the lowering of the fitting squeeze and prevent the occurrence of bearing creep, and also prevent the initially set bearing preload from decreasing. Therefore, the running stability of the vehicle can be reliably maintained by suppressing the fluctuation of the bearing rigidity.

好ましくは、請求項２に記載の発明のように、前記ナックルが軽合金からなり、このナックルの線膨張係数より前記樹脂バンドの線膨張係数が大きく設定されていれば、温度上昇によるシメシロ低下を防止することができる。   Preferably, as in the invention described in claim 2, if the knuckle is made of a light alloy and the linear expansion coefficient of the resin band is set larger than the linear expansion coefficient of the knuckle, the squeezing drop due to temperature rise is reduced. Can be prevented.

また、請求項３に記載の発明のように、前記樹脂バンドの外径が、前記外輪の外径よりも０〜５０μｍ突出して形成されていれば、温度上昇によるシメシロの低下を確実に防止できると共に、樹脂バンドの剛性の低下を抑制することができる。   Further, as in the invention described in claim 3, if the outer diameter of the resin band is formed so as to protrude from 0 to 50 μm from the outer diameter of the outer ring, it is possible to reliably prevent the lowering of the shimeshiro due to the temperature rise. At the same time, a decrease in the rigidity of the resin band can be suppressed.

また、請求項４に記載の発明のように、前記内輪の内側転走面の大径側から軸方向に延びる肩部が形成され、この肩部の内周面から面取り部に亙る環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形により充填されていれば、予圧抜けを効果的に防止することができる。   Further, as in the invention described in claim 4, a shoulder portion extending in the axial direction from the large diameter side of the inner raceway surface of the inner ring is formed, and an annular recess extending from the inner peripheral surface of the shoulder portion to the chamfered portion is formed. If a resin band made of a heat-resistant synthetic resin is filled by injection molding, preload loss can be effectively prevented.

好ましくは、請求項５に記載の発明のように、前記樹脂バンドが前記内輪の大径側端面より０〜５０μｍ突出して形成されていれば、予圧抜けを確実に防止して初期に設定された軸受予圧を長期間に亙って保持することができる。   Preferably, as in the invention described in claim 5, if the resin band is formed so as to protrude from the large-diameter side end surface of the inner ring by 0 to 50 μm, the preload is surely prevented and set to the initial stage. Bearing preload can be maintained over a long period of time.

また、請求項６に記載の発明のように、前記外方部材と内輪がパイプ材から冷間のローリング加工によって形成されていれば、肉厚を略均等にすることができると共に、形状、寸法を所定の精度に確保することができる。   If the outer member and the inner ring are formed by cold rolling from the pipe material as in the invention described in claim 6, the thickness can be made substantially uniform and the shape and dimensions can be made. Can be ensured with a predetermined accuracy.

また、請求項７に記載の発明のように、前記樹脂バンドがポリアミド系の合成樹脂からなり、その線膨張係数が８〜１６×１０−５／℃に設定されていれば、少なくとも嵌合される部材の線膨張係数よりも大きく、この部材が車輪用軸受以上に熱膨張したとしても、この樹脂バンドがそれ以上に膨張してその変化に追従することができる。 Further, as in the invention described in claim 7, when the resin band is made of a polyamide-based synthetic resin and the linear expansion coefficient is set to 8 to 16 × 10 −5 / ° C., at least the fitting is performed. Even if this member is larger than the linear expansion coefficient of the member, and the member is thermally expanded more than the wheel bearing, the resin band can be further expanded to follow the change.

本発明に係る車輪用軸受装置は、一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、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、このハブ輪にセレーションを介して内嵌された等速自在継手の外側継手部材と、懸架装置を構成するナックルと、このナックルと前記ハブ輪の小径段部との間に所定のシメシロで嵌合された車輪用軸受とを備え、この車輪用軸受を介して前記ハブ輪が前記ナックルに対して回転自在に支承されている車輪用軸受装置において、前記車輪用軸受が、外周の中央部に環状凹部を有し、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を備え、前記一対の内輪が、その小径側端面が突合せ状態で衝合して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た背面合せタイプの複列のアンギュラ玉軸受からなると共に、前記外方部材と内輪がパイプ材から塑性加工によって形成され、前記外方部材の環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填されているので、ナックルと外方部材の線膨張係数の違いにより、走行時の温度上昇によってナックルと外方部材との嵌合シメシロが減少したり、あるいは解放されることはなくなり、予圧抜けを防止して組立時の軸受予圧を長期間に亘って維持することができる。さらに、外方部材がクリープを起こして焼付いたり、短寿命を誘発するのを確実に防止することができる。   A wheel bearing device according to the present invention has a wheel mounting flange for mounting a wheel at one end, and a hub wheel formed with a small-diameter step portion extending axially from the wheel mounting flange via a shoulder. An outer joint member of a constant velocity universal joint fitted into the hub ring via serrations, a knuckle constituting a suspension device, and a predetermined squeezing between the knuckle and the small-diameter step portion of the hub ring. A wheel bearing device, wherein the hub wheel is rotatably supported with respect to the knuckle through the wheel bearing. An outer member having an annular recess in the inner periphery and a double row arc-shaped outer rolling surface formed integrally on the inner periphery, and an arc-shaped inner rolling facing the outer surface of the double row on the outer periphery. A pair of inner rings formed with surfaces, the inner rings and the A plurality of balls accommodated between both rolling surfaces of the side member, and the pair of inner rings are brought into contact with each other with their small diameter side end faces butting the shoulders of the hub wheel and the outer joint member. It consists of a back-to-back double row angular contact ball bearing that is sandwiched between shoulders and applied with a predetermined bearing preload, and the outer member and inner ring are formed by plastic processing from a pipe material, and the outer member annular Since the resin band made of heat-resistant synthetic resin is filled in the recess by injection molding, due to the difference in the linear expansion coefficient between the knuckle and the outer member, the knuckles and the outer member are fitted due to the temperature rise during running Is not reduced or released, and preload loss can be prevented and the bearing preload during assembly can be maintained over a long period of time. Furthermore, it is possible to reliably prevent the outer member from creeping and seizing or inducing a short life.

一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、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、このハブ輪にセレーションを介して内嵌された等速自在継手の外側継手部材と、懸架装置を構成する軽合金からなるナックルと、このナックルと前記ハブ輪の小径段部との間に所定のシメシロで嵌合された車輪用軸受とを備え、この車輪用軸受を介して前記ハブ輪が前記ナックルに対して回転自在に支承されている車輪用軸受装置において、前記車輪用軸受が、外周の中央部に環状凹部を有し、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と、この内側転走面の大径側から軸方向に延びる肩部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を備え、前記一対の内輪が、その小径側端面が突合せ状態で衝合して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た背面合せタイプの複列のアンギュラ玉軸受からなると共に、前記外方部材と内輪がパイプ材から冷間のローリング加工によって形成され、前記外方部材の環状凹部と、前記内輪の肩部の内周面から面取り部に亙る環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形により充填されている。   A hub wheel that integrally has a wheel mounting flange for mounting a wheel at one end, and has a small-diameter step portion extending in an axial direction from the wheel mounting flange through a shoulder portion, and a serration on the hub wheel via a serration For a wheel fitted with a predetermined squeeze between the outer joint member of a constant velocity universal joint fitted inside, a knuckle made of a light alloy constituting a suspension device, and the small-diameter step portion of the hub wheel. A wheel bearing device in which the hub wheel is rotatably supported with respect to the knuckle via the wheel bearing. The wheel bearing has an annular recess at the center of the outer periphery. An outer member in which a double row arc-shaped outer rolling surface is integrally formed on the inner periphery, an arc-shaped inner rolling surface facing the outer surface of the double row on the outer periphery, and the inner rolling surface. A shoulder extending in the axial direction from the large diameter side of the running surface is formed. A pair of inner rings and a double row of balls accommodated between both inner rings and the rolling surfaces of the outer member, and the pair of inner rings abut each other with their small diameter side end faces butting the hub. It consists of a back-to-back type double row angular contact ball bearing that is sandwiched between the shoulder of the ring and the shoulder of the outer joint member and applied with a predetermined bearing preload, and the outer member and the inner ring are A resin band made of heat-resistant synthetic resin is filled in the annular recess of the outer member and the annular recess extending from the inner peripheral surface of the shoulder portion of the inner ring to the chamfered portion by injection molding. .

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は、従来の車輪用軸受と本実施形態に係る車輪用軸受の温度変化と軸受予圧の変化の関係を比較測定した結果を示すグラフである。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 a single inner ring of FIG. 2, and FIG. 4 is a relationship between a temperature change of a conventional wheel bearing and the wheel bearing according to the present embodiment and a change in bearing preload. It is a graph which shows the result of having carried out comparative measurement. 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).

図１に示す車輪用軸受装置は、ハブ輪１と、このハブ輪１に圧入され、ナックル２に対してハブ輪１を回転自在に支承する車輪用軸受３とを主たる構成としている。ハブ輪１は、アウター側の端部に車輪ＷおよびブレーキロータＢを取り付けるための車輪取付フランジ４と、この車輪取付フランジ４から肩部１ａを介して軸方向に延びる円筒状の小径段部５が形成されている。車輪取付フランジ４には車輪ＷおよびブレーキロータＢを締結するハブボルト４ａが周方向等配に植設されている。また、ハブ輪１の内周面にはセレーション（またはスプライン）６が形成され、小径段部５の外周面には後述する車輪用軸受３が圧入されている。   The wheel bearing device shown in FIG. 1 mainly includes a hub wheel 1 and a wheel bearing 3 that is press-fitted into the hub wheel 1 and rotatably supports the hub wheel 1 with respect to the knuckle 2. The hub wheel 1 includes a wheel mounting flange 4 for mounting the wheel W and the brake rotor B to an end portion on the outer side, and a cylindrical small-diameter step portion 5 extending in an axial direction from the wheel mounting flange 4 via a shoulder portion 1a. Is formed. Hub bolts 4 a that fasten the wheels W and the brake rotor B are planted on the wheel mounting flange 4 at equal intervals in the circumferential direction. A serration (or spline) 6 is formed on the inner peripheral surface of the hub wheel 1, and a wheel bearing 3 described later is press-fitted on the outer peripheral surface of the small diameter step portion 5.

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、鍛造加工後の生のままである。なお、曲げ強度に対する疲労強度増加のために鍛造加工後に調質処理を行う方法や、肩部１ａから小径段部５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 is formed of medium and high carbon steel containing carbon of 0.40 to 0.80 wt% such as S53C, and remains raw after forging. In addition, in order to increase the fatigue strength with respect to the bending strength, a method of performing a tempering treatment after forging, or a hardening treatment in the range of 58 to 64 HRC by induction hardening from the shoulder portion 1a to the small diameter step portion 5 is performed. You may do it.

車輪用軸受３は、等速自在継手７を構成する外側継手部材８の肩部９とハブ輪１の肩部１ａとで挟持された状態で固定されている。外側継手部材８は、肩部９から軸方向に延びるステム部１０が一体に形成されている。このステム部１０の外周には、ハブ輪１のセレーション６に係合するセレーション（またはスプライン）１０ａと、このセレーション１０ａの端部に雄ねじ１０ｂが形成され、エンジンからのトルクを図示しないドライブシャフトおよび等速自在継手７、そしてこのセレーション６、１０ａを介してハブ輪１に伝達している。   The wheel bearing 3 is fixed in a state of being sandwiched between the shoulder 9 of the outer joint member 8 constituting the constant velocity universal joint 7 and the shoulder 1 a of the hub wheel 1. The outer joint member 8 is integrally formed with a stem portion 10 extending in the axial direction from the shoulder portion 9. A serration (or spline) 10a that engages with the serration 6 of the hub wheel 1 and a male screw 10b at the end of the serration 10a are formed on the outer periphery of the stem portion 10 to drive torque from the engine (not shown) It is transmitted to the hub wheel 1 through the constant velocity universal joint 7 and the serrations 6 and 10a.

ここで、セレーション１０ａには軸線に対して所定の角度傾斜した捩れ角が設けられ、外側継手部材８の肩部９が車輪用軸受３に当接するまでステム部１０がハブ輪１に内嵌され、ハブ輪１のセレーション６に圧入嵌合されている。これにより、セレーション６、１０ａの嵌合部に予圧を付与し周方向のガタを殺している。また、ステム部１０の端部に形成された雄ねじ１０ｂに固定ナット１１が所定の締付トルクで締結され、所望の軸受予圧が付与された状態で、ハブ輪１と等速自在継手３が分離可能に結合されている。   Here, the serration 10 a is provided with a torsion angle inclined at a predetermined angle with respect to the axis, and the stem portion 10 is fitted into the hub wheel 1 until the shoulder portion 9 of the outer joint member 8 abuts against the wheel bearing 3. The hub ring 1 is press-fitted into the serration 6. Thereby, the preload is given to the fitting part of the serrations 6 and 10a, and the play of the circumferential direction is killed. Further, the hub wheel 1 and the constant velocity universal joint 3 are separated in a state where the fixing nut 11 is fastened to the male screw 10b formed at the end portion of the stem portion 10 with a predetermined tightening torque and a desired bearing preload is applied. It is combined as possible.

一方、ナックル２は、アルミ合金等の軽合金で形成されている。これにより、従来の鋳鉄等に比べ、剛性不足を補うために各部を肉厚に設計したとしてもその重量は半減する。そして、このナックル２に車輪用軸受３が所定のシメシロで圧入されている。   On the other hand, the knuckle 2 is formed of a light alloy such as an aluminum alloy. As a result, compared with conventional cast iron or the like, even if each part is designed to be thick in order to compensate for the lack of rigidity, its weight is halved. A wheel bearing 3 is press-fitted into the knuckle 2 with a predetermined scissors.

車輪用軸受３は、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１２ａ、１２ａが一体に形成された外方部材１２と、外周にこれら複列の外側転走面１２ａ、１２ａに対向する円弧状の内側転走面１３ａ、１３ａが形成された一対の内輪１３、１３と、両転走面間に保持器１４、１４を介して転動自在に収容された複列のボール１５、１５と、外方部材１２の両端部に装着されたシール１６、１６とを備えている。そして、内輪１３の小径（正面）側端面１３ｂ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。   As shown in an enlarged view in FIG. 2, the wheel bearing 3 includes an outer member 12 in which double-row arc-shaped outer rolling surfaces 12 a and 12 a are integrally formed on the inner periphery, and these double-rows on the outer periphery. A pair of inner rings 13, 13 formed with arc-shaped inner rolling surfaces 13 a, 13 a facing the outer rolling surfaces 12 a, 12 a, and freely rollable via the cages 14, 14 between both rolling surfaces. The double row balls 15 and 15 accommodated therein and the seals 16 and 16 attached to both ends of the outer member 12 are provided. The small-diameter (front) side end surface 13b of the inner ring 13 is abutted in a butted state to constitute a so-called back-to-back type double row angular ball bearing.

シール１６は、外方部材１２の円筒部１２ｂに嵌合される芯金１６ａと、この芯金１６ａ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１６ｂからなり、内輪１３の外径面に摺接する一対のラジアルリップを備えている。これにより、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。また、図示していないが、こうしたシール１６以外に他の構造のシールを用いても良い。すなわち、内輪１３の外径にスリンガを圧入すると共に、このスリンガに対向して環状のシール板を外方部材１２の円筒部１２ａに装着し、このシール板のシールリップをスリンガに摺接させる、所謂パックシールを用いても良い。   The seal 16 includes a metal core 16a that is fitted to the cylindrical portion 12b of the outer member 12, and a seal member 16b that is integrally joined to the metal core 16a by vulcanization adhesion or the like and is made of an elastomer such as nitrile rubber. A pair of radial lips are provided in sliding contact with the outer diameter surface of the inner ring 13. This prevents leakage of grease sealed inside the bearing and prevents foreign matter such as rainwater and dust from entering the bearing from the outside. Although not shown, a seal having a structure other than the seal 16 may be used. That is, a slinger is press-fitted into the outer diameter of the inner ring 13, and an annular seal plate is mounted on the cylindrical portion 12a of the outer member 12 so as to face the slinger, and the seal lip of the seal plate is slidably contacted with the slinger. A so-called pack seal may be used.

ここで、外方部材１２および内輪１３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焼鈍した後、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。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１２および内輪１３の材質としてこれ以外にも、Ｓ５０Ｃ〜Ｓ５５Ｃや冷間圧延鋼鈑（ＪＩＳ規格のＳＰＣＣ系等）等の炭素鋼あるいはＳＣＭ４４０等の浸炭鋼を例示することができる。   Here, the outer member 12 and the inner ring 13 are obtained by annealing a pipe material made of bearing steel such as SUJ2 or carburized steel such as SCr420 or SCM415, and then pressing or cold rolling (hereinafter referred to as plastic working). Is formed. 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 12 and the inner ring 13 include carbon steels such as S50C to S55C and cold rolled steel plates (such as JIS standard SPCC), and carburized steels such as SCM440.

一方、冷間圧延鋼鈑や炭素鋼の場合、外方部材１２においては、少なくとも複列の外側転走面１２ａ、１２ａが、また、内輪１３においては、少なくとも内側転走面１３ａ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１２ａ、１３ａ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。   On the other hand, in the case of cold rolled steel or carbon steel, at least the double row outer rolling surfaces 12a, 12a are formed by induction hardening in the outer member 12, and at least the inner rolling surface 13a is formed by induction hardening in the inner ring 13. The surface hardness is set in the range of 50 to 64 HRC, and the rolling fatigue life is improved. These rolling surfaces 12a and 13a 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１２および内輪１３の構成について詳細に説明する。
外方部材１２は、（ａ）に示すように、素材となるパイプ材から塑性加工により、内周に径方向内方に突出する環状凸部１７と、この環状凸部１７の両側に複列の円弧状の外側転走面１２ａ、１２ａが形成されると共に、両端部にシール１６の嵌合部となる円筒部１２ｂ、１２ｂが形成される。 Next, the configuration of the outer member 12 and the inner ring 13 will be described in detail with reference to FIG.
As shown in (a), the outer member 12 is formed by forming a circular projection 17 projecting radially inward from the pipe material, which is a raw material, and a double row on both sides of the annular projection 17. Arc-shaped outer rolling surfaces 12a and 12a are formed, and cylindrical portions 12b and 12b serving as fitting portions of the seal 16 are formed at both ends.

ここで、外側転走面１２ａから環状凸部１７の肩高さを適切に確保するために、外方部材１２の塑性加工時、環状凸部１７の内径がフラット形状に形成されると共に、外方部材１２の中央部を凹ませて環状凹部１８が形成され、肩部１９に素材が充足するようにされている。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。   Here, in order to appropriately secure the shoulder height of the annular convex portion 17 from the outer rolling surface 12a, the inner diameter of the annular convex portion 17 is formed into a flat shape during plastic processing of the outer member 12, and the outer An annular recess 18 is formed by denting the central portion of the side member 12 so that the shoulder portion 19 is filled with the material. Note that both end surfaces where burrs are generated by plastic working are turned after machining. Moreover, a grinding process is given as needed.

一方、内輪１３は、（ｂ）に示すように、素材となるパイプ材から塑性加工により、外周に円弧状の内側転走面１３ａと、この内側転走面１３ａの大径側から軸方向に延びる肩部２０が形成されている。ここで、この肩部２０はシール１６のシールランド部となり、塑性加工後に内側転走面１３ａと同時に研削加工され、所定の寸法、精度に形成される。なお、外方部材１２と同様、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。   On the other hand, as shown in (b), the inner ring 13 is formed by plastic processing from a pipe material as a raw material, and an arcuate inner rolling surface 13a on the outer periphery, and from the large diameter side of the inner rolling surface 13a in the axial direction An extending shoulder 20 is formed. Here, the shoulder portion 20 becomes a seal land portion of the seal 16, and is ground at the same time as the inner rolling surface 13a after plastic working, and is formed with a predetermined size and accuracy. As with the outer member 12, both end faces where burrs are generated by plastic working are turned after machining. Moreover, a grinding process is given as needed.

本実施形態では、外方部材１２および内輪１３がパイプ材から塑性加工で形成されると共に、両転走面１２ａ、１３ａとシール１６の嵌合面となる外方部材１２の円筒部１２ｂ、およびシール１６のシールランド部となる内輪１３の肩部２０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。なお、ナックル２やハブ輪１の嵌合面となる外方部材１２の外径面および内輪１３の内径、さらには突合せ面となる内輪１３の小径側端面１３ｂを研削加工によって形成しても良い。これにより、従来の鍛造、削り出しの軸受と同等の軸受精度を確保することができる。   In the present embodiment, the outer member 12 and the inner ring 13 are formed from a pipe material by plastic working, and the cylindrical portion 12b of the outer member 12 serving as a fitting surface between the rolling surfaces 12a and 13a and the seal 16, and Since the shoulder portion 20 of the inner ring 13 serving as the seal land portion of the seal 16 is formed by grinding, the productivity is improved, the yield is good, the cost can be reduced, and it is equivalent to the conventional bearing. Accuracy and sealability can be secured. The outer diameter surface of the outer member 12 that becomes the fitting surface of the knuckle 2 and the hub wheel 1, the inner diameter of the inner ring 13, and the small-diameter side end surface 13b of the inner ring 13 that becomes the butting surface may be formed by grinding. . Thereby, the bearing accuracy equivalent to the conventional forged and machined bearing can be ensured.

ここで、本実施形態では、図２に示すように、外方部材１２の環状凹部１８にＰＡ（ポリアミド）１１をベースとした耐熱性の熱可塑性合成樹脂が射出成形により充填され、樹脂バンド２１が形成されている。この樹脂バンド２１の外径は、外方部材１２の外径より０〜５０μｍ突出して形成されている。突出量が０以下では、温度上昇によるシメシロ低下を確実に防止することが難しく、また、突出量が５０μｍを超えると、ナックル２の圧入時に樹脂バンド２１のむしれ等が発生し易い。なお、突出量は軸受のサイズ等によって若干異なるも、製造バラツキを考慮して１０〜４０μｍの範囲に設定するのが好ましい。   Here, in this embodiment, as shown in FIG. 2, the annular recess 18 of the outer member 12 is filled with a heat-resistant thermoplastic synthetic resin based on PA (polyamide) 11 by injection molding, and the resin band 21 Is formed. The outer diameter of the resin band 21 is formed so as to protrude from the outer diameter of the outer member 12 by 0 to 50 μm. If the amount of protrusion is 0 or less, it is difficult to reliably prevent a decrease in squeeze due to temperature rise, and if the amount of protrusion exceeds 50 μm, the resin band 21 is likely to be peeled when the knuckle 2 is press-fitted. Although the amount of protrusion differs slightly depending on the size of the bearing, etc., it is preferable to set it within a range of 10 to 40 μm in consideration of manufacturing variations.

これにより、予圧抜けと軸受クリープを効果的に防止することができる。すなわち、ナックル２と外方部材１２の線膨張係数の違いにより、例えば、走行時の温度上昇によってナックル２と外方部材１２との嵌合シメシロが減少したり、あるいは解放されることはなくなり、予圧抜けを防止して組立時の軸受予圧を長期間に亘って維持することができる。さらに、外方部材１２がクリープを起こして焼付いたり、短寿命を誘発するのを確実に防止することができる。   Thereby, preload loss and bearing creep can be effectively prevented. That is, due to the difference in linear expansion coefficient between the knuckle 2 and the outer member 12, for example, the fitting shimiro between the knuckle 2 and the outer member 12 will not be reduced or released due to the temperature rise during traveling, Preload loss can be prevented and the bearing preload during assembly can be maintained over a long period of time. Furthermore, it is possible to reliably prevent the outer member 12 from creeping and seizing or inducing a short life.

さらに、本実施形態では、外方部材１２と同様、内輪１３の肩部２０の内周面から面取り部１３ｃに亙る環状凹部２２にＰＡ１１からなる耐熱性の熱可塑性合成樹脂が射出成形により充填され、樹脂バンド２３が形成されている。この樹脂バンド２３は、内輪１３の大径（背面）側端面１３ｄより０〜５０μｍ、好ましくは、製造バラツキを考慮して１０〜４０μｍの範囲に突出して形成されている。   Further, in the present embodiment, similarly to the outer member 12, the annular recess 22 extending from the inner peripheral surface of the shoulder portion 20 of the inner ring 13 to the chamfered portion 13c is filled with a heat-resistant thermoplastic synthetic resin made of PA11 by injection molding. A resin band 23 is formed. The resin band 23 is formed so as to protrude from the large-diameter (rear) side end surface 13d of the inner ring 13 in a range of 0 to 50 μm, preferably 10 to 40 μm in consideration of manufacturing variations.

軸受予圧は、一対の内輪１３、１３の大径側端面１３ｄ、１３ｄをハブ輪１の肩部１ａと外側継手部材８の肩部９で挟持することにより付与されるが、こうした樹脂バンド２３により、外方部材１２の樹脂バンド２１と相俟って予圧抜けを確実に防止して初期に設定された軸受予圧を長期間に亙って保持することができる。   The bearing preload is applied by sandwiching the large-diameter side end surfaces 13d and 13d of the pair of inner rings 13 and 13 between the shoulder 1a of the hub wheel 1 and the shoulder 9 of the outer joint member 8. In combination with the resin band 21 of the outer member 12, it is possible to reliably prevent the preload from being lost and to retain the initially set bearing preload for a long period of time.

また、樹脂バンド２１、２３の材質は、前述したＰＡ１１に限らず、アルミ合金等の軽合金からなるナックル２の線膨張係数（２〜２．３×１０−５／℃）よりも大きく、線膨張係数が８〜１６×１０−５／℃の範囲の合成樹脂なら良い。例えば、ＰＡ６６、さらにこれらの熱可塑性合成樹脂にＧＦ（グラスファイバー）等の強化繊維を１０〜３０ｗｔ％の範囲で含有させたものを例示することができる。 The material of the resin bands 21 and 23 is not limited to the PA 11 described above, and is larger than the linear expansion coefficient (2 to 2.3 × 10 −5 / ° C.) of the knuckle 2 made of a light alloy such as an aluminum alloy. A synthetic resin having an expansion coefficient of 8 to 16 × 10 −5 / ° C. may be used. For example, PA66 and those obtained by adding reinforcing fibers such as GF (glass fiber) in the range of 10 to 30 wt% to these thermoplastic synthetic resins can be exemplified.

図４は、従来の車輪用軸受と本実施形態に係る車輪用軸受のそれぞれ外方部材のみをアルミ合金からなるナックルに圧入した状態で、温度変化と軸受予圧の変化、すなわち、外方部材の外側転走面の寸法変化との関係を比較測定した結果を示している。この図でも明確なように、従来のものでは、温度上昇に比例してリニアに軸受予圧が低下しているが、本実施形態に係る車輪用軸受においては、軸受予圧は８０℃近傍までは漸次低下するも、それ以降は所定の予圧量を維持することが判る。   FIG. 4 shows a change in temperature and a change in bearing preload, that is, a change in the outer member, in a state where only the outer members of the conventional wheel bearing and the wheel bearing according to the present embodiment are press-fitted into an aluminum alloy knuckle. The result of the comparative measurement of the relationship with the dimensional change of the outer rolling surface is shown. As is clear from this figure, in the conventional one, the bearing preload decreases linearly in proportion to the temperature rise. However, in the wheel bearing according to this embodiment, the bearing preload gradually increases up to about 80 ° C. Although it decreases, it can be seen that the predetermined preload amount is maintained thereafter.

以上、詳述したように、本実施形態では、ナックル２がアルミ合金等の軽合金で形成され、このナックル２に圧入される車輪用軸受３の外方部材１２の外周にナックル２の線膨張係数よりも大きな線膨張係数を有する樹脂バンド２１が形成されると共に、内輪１３の端部にも、少なくともハブ輪１および外側継手部材８の線膨張係数よりも大きな線膨張係数を有する樹脂バンド２３が形成されているので、温度上昇時、ナックル２と車輪用軸受３の線膨張係数の違いにより、ナックル２が車輪用軸受３以上に熱膨張したとしても嵌合シメシロの低下を抑制して軸受クリープの発生を防止することができると共に、ハブ輪１や外側継手部材８が熱膨張したとしても初期に設定した軸受予圧が低下するのを防止することができ、軸受剛性の変動を抑えて車両の走行安定性を確実に保つことができる。   As described above in detail, in this embodiment, the knuckle 2 is formed of a light alloy such as an aluminum alloy, and the linear expansion of the knuckle 2 is performed on the outer periphery of the outer member 12 of the wheel bearing 3 that is press-fitted into the knuckle 2. The resin band 21 having a linear expansion coefficient larger than the coefficient is formed, and the resin band 23 having a linear expansion coefficient larger than at least the linear expansion coefficient of the hub wheel 1 and the outer joint member 8 is also formed at the end of the inner ring 13. Because of the difference in linear expansion coefficient between the knuckle 2 and the wheel bearing 3 when the temperature rises, even if the knuckle 2 thermally expands more than the wheel bearing 3, it is possible to suppress the lowering of the fitting shimiro. Creeping can be prevented, and even if the hub wheel 1 or the outer joint member 8 is thermally expanded, the initially set bearing preload can be prevented from being lowered, and the bearing rigidity can be changed. Ete can be maintained reliably running stability of the vehicle.

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. 従来の車輪用軸受と本実施形態に係る車輪用軸受の温度変化と軸受予圧の変化の関係を比較測定した結果を示すグラフである。It is a graph which shows the result of having comparatively measured the relationship between the temperature change of the conventional wheel bearing and the wheel bearing which concerns on this embodiment, and the change of a bearing preload. 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、９、１９、２０・・・・・・・肩部
２・・・・・・・・・・・・・・・・ナックル
３・・・・・・・・・・・・・・・・車輪用軸受
４・・・・・・・・・・・・・・・・車輪取付フランジ
４ａ・・・・・・・・・・・・・・・ハブボルト
５・・・・・・・・・・・・・・・・小径段部
６、１０ａ・・・・・・・・・・・・セレーション
７・・・・・・・・・・・・・・・・等速自在継手
８・・・・・・・・・・・・・・・・外側継手部材
１０・・・・・・・・・・・・・・・ステム部
１０ｂ・・・・・・・・・・・・・・雄ねじ
１１・・・・・・・・・・・・・・・固定ナット
１２・・・・・・・・・・・・・・・外方部材
１２ａ・・・・・・・・・・・・・・外側転走面
１２ｂ・・・・・・・・・・・・・・円筒部
１３・・・・・・・・・・・・・・・内輪
１３ａ・・・・・・・・・・・・・・内側転走面
１３ｂ・・・・・・・・・・・・・・小径側端面
１３ｃ・・・・・・・・・・・・・・面取り部
１３ｄ・・・・・・・・・・・・・・大径側端面
１４・・・・・・・・・・・・・・・保持器
１５・・・・・・・・・・・・・・・ボール
１６・・・・・・・・・・・・・・・シール
１６ａ・・・・・・・・・・・・・・芯金
１６ｂ・・・・・・・・・・・・・・シール部材
１７・・・・・・・・・・・・・・・環状凸部
１８、２２・・・・・・・・・・・・環状凹部
２１、２３・・・・・・・・・・・・樹脂バンド
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
Ｂ・・・・・・・・・・・・・・・・ブレーキロータ
Ｗ・・・・・・・・・・・・・・・・車輪 1 ················· Hub wheel 1a, 9, 19, 20 · · · Knuckle 3 · · · · · · Wheel bearing 4 · · · · · · Wheel mounting flange 4a · · · ························································································ Serration 7・ ・ ・ ・ ・ ・ ・ ・ Constant velocity universal joint 8 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer joint member 10 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・... Stem part 10b ... Male thread 11 ... Fixing nut 12 ... ... External member 12a ... External rolling surface 12b ... ... Cylindrical part 13 ... Inner ring 13a ... Inner rolling surface 13b ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Small-diameter side end face 13c ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Chamfer 13d ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Large-diameter side end face 14 ... Cage 15 ... Ball 16 ...・ Seal 16a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Core 16b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal member 17 ・ ・ ・ ・ ・ ・ ・ ・················································································ Resin band 50 ... Angular ball bearings 51 ... Outer rings 51a ... ··························································· Outside rolling surface 51d ····························· 52 ... Inner rolling surfaces 52c, 53c ... Fitting part 54 ... Housing 55 ... ············ Shaft member 55a ························································· ················································································· Adhesion Agent B ... Brake rotor W ... ········Wheel

Claims (7)

一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、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、
このハブ輪にセレーションを介して内嵌された等速自在継手の外側継手部材と、
懸架装置を構成するナックルと、
このナックルと前記ハブ輪の小径段部との間に所定のシメシロで嵌合された車輪用軸受とを備え、
この車輪用軸受を介して前記ハブ輪が前記ナックルに対して回転自在に支承されている車輪用軸受装置において、
前記車輪用軸受が、外周の中央部に環状凹部を有し、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を備え、
前記一対の内輪が、その小径側端面が突合せ状態で衝合して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た背面合せタイプの複列のアンギュラ玉軸受からなると共に、
前記外方部材と内輪がパイプ材から塑性加工によって形成され、前記外方部材の環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形によって充填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 for mounting a wheel on one end, and a small-diameter step portion extending in the axial direction from the wheel mounting flange via a shoulder; and
An outer joint member of a constant velocity universal joint fitted into the hub wheel via a serration;
A knuckle constituting a suspension device;
A wheel bearing fitted with a predetermined scissors between the knuckle and the small-diameter step portion of the hub wheel,
In the wheel bearing device in which the hub wheel is rotatably supported with respect to the knuckle through the wheel bearing,
The wheel bearing has an annular recess in the central portion of the outer periphery, and 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;
These inner rings and double row balls accommodated between both rolling surfaces of the outer member,
A pair of back-to-back types in which the pair of inner rings are abutted with their small-diameter side end faces abutting and are sandwiched between the shoulder part of the hub wheel and the shoulder part of the outer joint member and given a predetermined bearing preload. Of angular contact ball bearings,
The wheel bearing device, wherein the outer member and the inner ring are formed from a pipe material by plastic working, and a resin band made of a heat-resistant synthetic resin is filled in the annular recess of the outer member by injection molding. . 前記ナックルが軽合金からなり、このナックルの線膨張係数よりも前記樹脂バンドの線膨張係数が大きく設定されている請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein the knuckle is made of a light alloy, and the linear expansion coefficient of the resin band is set larger than the linear expansion coefficient of the knuckle. 前記樹脂バンドの外径が、前記外輪の外径よりも０〜５０μｍ突出して形成されている請求項１または２に記載の車輪用軸受装置。   The wheel bearing device according to claim 1 or 2, wherein an outer diameter of the resin band is formed so as to protrude 0 to 50 µm from an outer diameter of the outer ring. 前記内輪の内側転走面の大径側から軸方向に延びる肩部が形成され、この肩部の内周面から面取り部に亙る環状凹部に耐熱性の合成樹脂からなる樹脂バンドが射出成形により充填されている請求項１乃至３いずれかに記載の車輪用軸受装置。   A shoulder portion extending in the axial direction from the large diameter side of the inner raceway surface of the inner ring is formed, and a resin band made of a heat-resistant synthetic resin is formed by injection molding in an annular recess extending from the inner peripheral surface of the shoulder portion to the chamfered portion. The wheel bearing device according to any one of claims 1 to 3, wherein the wheel bearing device is filled. 前記樹脂バンドが前記内輪の大径側端面より０〜５０μｍ突出して形成されている請求項４に記載の車輪用軸受装置。   The wheel bearing device according to claim 4, wherein the resin band is formed to protrude from 0 to 50 μm from the large-diameter side end surface of the inner ring. 前記外方部材と内輪がパイプ材から冷間のローリング加工によって形成されている請求項１乃至５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 5, wherein the outer member and the inner ring are formed by cold rolling from a pipe material. 前記樹脂バンドがポリアミド系の合成樹脂からなり、その線膨張係数が８〜１６×１０−５／℃に設定されている請求項１乃至６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 6, wherein the resin band is made of a polyamide-based synthetic resin, and a linear expansion coefficient thereof is set to 8 to 16 × 10 -5 / ° C.
JP2007161216A 2007-06-19 2007-06-19 Wheel bearing device Expired - Fee Related JP4940027B2 (en)

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JP2010281417A (en) * 2009-06-05 2010-12-16 Toyota Motor Corp Motion converting device and vehicle steering device
CN102619872A (en) * 2012-04-09 2012-08-01 湖州铧星轴承有限公司 Bearing rotating method and composite double-row ball bearing
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WO2017033653A1 (en) * 2015-08-26 2017-03-02 日本精工株式会社 Rolling bearing unit for wheel support
JP2017044332A (en) * 2014-12-04 2017-03-02 日本精工株式会社 Wheel support rolling bearing unit
CN107379892A (en) * 2017-07-21 2017-11-24 上汽通用五菱汽车股份有限公司 Drive axle hub and automobile
DE102018107875A1 (en) * 2018-04-04 2019-10-10 Schaeffler Technologies AG & Co. KG Tandem angular contact ball bearings
US11685187B2 (en) * 2020-05-15 2023-06-27 Aktiebolaget Skf Light-weight wheel hub for a wheel hub assembly

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JPH01210612A (en) * 1988-02-11 1989-08-24 Skf Nova Ab Double-row angular contact ball bearing and manufacture thereof
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010281417A (en) * 2009-06-05 2010-12-16 Toyota Motor Corp Motion converting device and vehicle steering device
DE102011085922A1 (en) * 2011-11-08 2013-05-08 Schaeffler Technologies AG & Co. KG Bearing i.e. double-row groove ball bearing, for driving pulley of compressor of air-conditioning system in motor vehicle, has inner bearing ring formed by tube whose outer contour has form of W extending in direction of symmetrical axis
DE102012202900A1 (en) * 2012-02-27 2013-08-29 Aktiebolaget Skf Bearing arrangement of electric motor, has rolling bearing including ring element arranged in annular groove of outer bearing ring such that outer diameter of ring element is set based on outer diameter of outer bearing ring
CN102619872A (en) * 2012-04-09 2012-08-01 湖州铧星轴承有限公司 Bearing rotating method and composite double-row ball bearing
JP2017044332A (en) * 2014-12-04 2017-03-02 日本精工株式会社 Wheel support rolling bearing unit
WO2017033653A1 (en) * 2015-08-26 2017-03-02 日本精工株式会社 Rolling bearing unit for wheel support
CN107379892A (en) * 2017-07-21 2017-11-24 上汽通用五菱汽车股份有限公司 Drive axle hub and automobile
DE102018107875A1 (en) * 2018-04-04 2019-10-10 Schaeffler Technologies AG & Co. KG Tandem angular contact ball bearings
US11685187B2 (en) * 2020-05-15 2023-06-27 Aktiebolaget Skf Light-weight wheel hub for a wheel hub assembly

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