JP5252834B2 - Manufacturing method of wheel bearing device - Google Patents

Manufacturing method of wheel bearing device Download PDF

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Publication number
JP5252834B2
JP5252834B2 JP2007130614A JP2007130614A JP5252834B2 JP 5252834 B2 JP5252834 B2 JP 5252834B2 JP 2007130614 A JP2007130614 A JP 2007130614A JP 2007130614 A JP2007130614 A JP 2007130614A JP 5252834 B2 JP5252834 B2 JP 5252834B2
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wheel
rolling
hub wheel
hub
mounting flange
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JP2008284960A (en
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真 友上
茂明 福島
清茂 山内
光 梅木田
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NTN Corp
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NTN Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/187—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2204/00—Metallic materials; Alloys
    • F16C2204/60—Ferrous alloys, e.g. steel alloys
    • F16C2204/64—Medium carbon steel, i.e. carbon content from 0.4 to 0,8 wt%
    • 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
    • F16C2223/00—Surface treatments; Hardening; Coating
    • F16C2223/10—Hardening, e.g. carburizing, carbo-nitriding
    • F16C2223/18—Hardening, e.g. carburizing, carbo-nitriding with induction hardening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • 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
    • F16C33/62—Selection of substances
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2250/00—Manufacturing; Assembly
    • F16D2250/0038—Surface treatment
    • F16D2250/0053—Hardening

Description

本発明は、自動車等の車両の車輪を車体に対して回転自在に支承した車輪用軸受装置の製造方法に関し、特に回転曲げ条件下でのハブ輪の強度、耐久性を向上させた車輪用軸受装置の製造方法に関するものである。
The present invention relates to a method of manufacturing a wheel bearing device in which a wheel of a vehicle such as an automobile is rotatably supported with respect to the vehicle body, and more particularly, a wheel bearing with improved strength and durability of a hub wheel under rotational bending conditions. The present invention relates to a device manufacturing method .

自動車の車輪用軸受装置には、従動輪用と駆動輪用とがあり、それぞれの用途に応じて種々の形式のものがあるが、例えば、図４に示す従来の駆動輪用の車輪用軸受装置では、ハブ輪５１と内輪５２とを備えた内方部材５０と、複列の転動体５３、５４と、外方部材５５と、そして、エンジン動力をハブ輪５１に伝達する等速自在継手５６を主要な構成要素としている。こうした車輪用軸受装置において、車輪（図示せず）およびブレーキロータ５７を支持するハブ輪５１には、鍛造の容易性、切削性、熱処理性、あるいは経済性の面からＳ５３Ｃ等の機械構造用の中炭素鋼が採用されている。このハブ輪５１をはじめこの種の車輪用軸受装置の小型・軽量化を図ることは、自動車の燃費向上と走行安定性の向上に大きく寄与するため、ハブ輪５１の車輪取付フランジ５８のリブ化や薄肉化が進んでいる。しかし、このハブ輪５１自体の機械的強度が、素材である中炭素鋼の疲労限に近付きつつあり、これ以上の小型・軽量化を図ることは難しくなってきている。   There are two types of wheel bearing devices for automobiles, one for a driven wheel and one for a drive wheel, and there are various types depending on the application. For example, the conventional wheel bearing for a drive wheel shown in FIG. In the apparatus, an inner member 50 having a hub wheel 51 and an inner ring 52, double-row rolling elements 53 and 54, an outer member 55, and a constant velocity universal joint that transmits engine power to the hub wheel 51. 56 is a main component. In such a wheel bearing device, the hub wheel 51 that supports the wheel (not shown) and the brake rotor 57 is used for a machine structure such as S53C in terms of easiness of forging, machinability, heat treatment, or economy. Medium carbon steel is used. The reduction of the size and weight of this type of wheel bearing device including this hub wheel 51 greatly contributes to the improvement of the fuel consumption and the running stability of the automobile, so that the wheel mounting flange 58 of the hub wheel 51 is ribbed. Thinning is progressing. However, the mechanical strength of the hub wheel 51 itself is approaching the fatigue limit of medium carbon steel, which is a material, and it is becoming difficult to achieve further reduction in size and weight.

特に、この種の構造のハブ輪５１においては、軽量化のために車輪取付フランジ５８を薄肉化する場合、そのアウトボード側の付け根部、すなわち、ブレーキロータ取付面５９から円筒状のパイロット部６０に延びる隅部６１に回転曲げの応力が集中し、対策が必要である。したがって、この隅部６１の寸法、つまり曲率半径を大きくすることによって発生応力を緩和することも考えられるが、これでは車輪取付フランジ５８に取り付けられるブレーキロータ５７との干渉が問題となるため、隅部６１の曲率半径を大きくするのにも限界がある。   In particular, in the hub wheel 51 of this type of structure, when the wheel mounting flange 58 is thinned for weight reduction, the base portion on the outboard side, that is, the cylindrical pilot portion 60 from the brake rotor mounting surface 59 is used. Rotational bending stress concentrates on the corner 61 that extends to, and countermeasures are required. Therefore, it is conceivable to reduce the generated stress by increasing the size of the corner 61, that is, the radius of curvature, but this causes a problem of interference with the brake rotor 57 attached to the wheel mounting flange 58. There is a limit to increasing the radius of curvature of the portion 61.

このような背景において、本出願人は、車輪取付フランジ５８の形状・寸法を変更することなく軽量化を図り、かつハブ輪５１の強度アップを図ることができる車輪用軸受装置を既に提案している。この車輪用軸受装置は、図５に示すように、ハブ輪５１の車輪取付フランジ５８の隅部６１に表面硬化層６２を高周波焼入れ等によって形成している。これにより、回転曲げ疲労の最弱部となる車輪取付フランジ５８の隅部６１を高強度化することができ、ハブ輪５１の耐久性を図ることができる。   Against such a background, the present applicant has already proposed a wheel bearing device capable of reducing the weight without changing the shape and dimensions of the wheel mounting flange 58 and increasing the strength of the hub wheel 51. Yes. In this wheel bearing device, as shown in FIG. 5, a hardened surface layer 62 is formed at the corner 61 of the wheel mounting flange 58 of the hub wheel 51 by induction hardening or the like. Thereby, the corner | angular part 61 of the wheel mounting flange 58 used as the weakest part of rotation bending fatigue can be strengthened, and durability of the hub wheel 51 can be aimed at.

また、これ以外の部位、すなわち、図示しない外方部材５５のアウトボード側端部に装着されたシールのシールリップが摺接するシールランド部をはじめ、軌道面から小径段部の各部位ａ〜ｄに亙って、高周波焼入れ等によって表面硬化層６３を形成している。さらには、ハブ輪５１の内周面に形成されたセレーション部６４にも表面硬化層６５を形成している。こうした表面硬化層６３、６５により、各部位ａ〜ｄ等において要求される回転曲げ疲労強度、耐摩耗性、転がり疲労寿命等を向上させることができる。
特開２００２−８７００８号公報 In addition to the seal land portion where the seal lip of the seal mounted on the outboard side end portion of the outer member 55 (not shown) is slidably contacted, the portions a to d of the small-diameter step portion from the raceway surface. Accordingly, the surface hardened layer 63 is formed by induction hardening or the like. Furthermore, a hardened surface layer 65 is also formed on the serration portion 64 formed on the inner peripheral surface of the hub wheel 51. Such hardened surface layers 63 and 65 can improve the rotational bending fatigue strength, wear resistance, rolling fatigue life, and the like required in the respective parts a to d.
JP 2002-87008 A

こうした従来の車輪用軸受装置では、ハブ輪５１の車輪取付フランジ５８の隅部６１に表面硬化層６２を形成することにより、車輪取付フランジ５８の形状・寸法を変更することなく、軽量化を図りつつハブ輪５１の強度アップを図ることができる。然しながら、隅部６１に表面硬化層６２を形成する高周波焼入れ工程で、車輪取付フランジ５８に熱処理変形が生じ、ブレーキロータ取付面５９の面振れが大きくなるという新たな問題が発生した。この傾向は車輪取付フランジ５８の薄肉化にも起因している。この面振れは、ブレーキロータ５７の振れに影響してブレーキジャダーを誘発することになり、自動車の操縦安定性やドライブフィーリングが低下する恐れがある。ここで、ハブ輪５１の熱処理後にこのブレーキロータ取付面５９をさらに旋削加工し、変形分を修正して面振れを改善する方法も考えられるが、隅部６１と未焼入れ部であるブレーキロータ取付面５９とに硬度差があるため、隅部６１の表面硬化層６２との境界部に僅かな段差が発生するという一種ジレンマ的な問題が内在していた。   In such a conventional wheel bearing device, the surface hardening layer 62 is formed at the corner 61 of the wheel mounting flange 58 of the hub wheel 51, thereby reducing the weight without changing the shape and dimensions of the wheel mounting flange 58. However, the strength of the hub wheel 51 can be increased. However, in the induction hardening process for forming the surface hardened layer 62 at the corner 61, a heat treatment deformation occurs in the wheel mounting flange 58, resulting in a new problem that the runout of the brake rotor mounting surface 59 increases. This tendency is also attributed to the thinning of the wheel mounting flange 58. This surface runout affects the runout of the brake rotor 57 and induces brake judder, which may reduce the driving stability and drive feeling of the automobile. Here, a method of further turning the brake rotor mounting surface 59 after the heat treatment of the hub wheel 51 and correcting the deformation to improve the surface runout can be considered. However, the corner rotor 61 and the brake rotor mounting which is an unquenched portion can be considered. Since the surface 59 has a hardness difference, there is a kind of dilemma problem that a slight step is generated at the boundary between the corner 61 and the surface hardened layer 62.

本発明は、このような事情に鑑みてなされたもので、車輪取付フランジの形状・寸法を変更することなく、また、その面振れを劣化させることなく、軽量化を図りつつ、回転曲げ条件下でのハブ輪の強度、耐久性を向上させた車輪用軸受装置の製造方法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 without changing the shape and dimensions of the wheel mounting flange, and without deteriorating the surface runout, while reducing the weight while rotating and bending conditions An object of the present invention is to provide a method of manufacturing a wheel bearing device in which the strength and durability of the hub wheel are improved.

係る目的を達成すべく、本発明のうち請求項１記載の発明は、ハブ輪と複列の転がり軸受および等速自在継手がユニット化された車輪用軸受装置の製造方法であって、外周に懸架装置に取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内側転走面が形成されたハブ輪、およびこのハブ輪に嵌合され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された前記等速自在継手の外側継手部材からなる内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体と、前記外方部材と内方部材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、前記ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装置の製造方法において、前記複列の転動体列のうちインナー側の転動体列のピッチ円直径がアウター側の転動体列のピッチ円直径よりも大径に設定され、このインナー側の転動体の個数が前記アウター側の転動体の個数よりも多く設定されると共に、前記ハブ輪が炭素０．４０〜０．８０重量％を含む中炭素鋼から旋削加工によって所望の形状・寸法に形成され、その後、所定の表面硬さに調質処理され、前記内側転走面と前記シールのシールランド部となる前記車輪取付フランジのインナー側の基部および内周に形成された凹凸部が高周波焼入れによって表面に所定の硬化層が形成され、その後、前記外側継手部材を前記凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材とが塑性結合される。
In order to achieve the object, the invention according to claim 1 of the present invention is a method of manufacturing a wheel bearing device in which a hub wheel, a double row rolling bearing and a constant velocity universal joint are unitized, and is provided on the outer periphery. A vehicle body mounting flange for mounting on a suspension device is integrally formed, an outer member having a double row outer rolling surface formed on the inner periphery, a wheel mounting flange on one end, and a wheel mounting flange on the outer periphery. A hub wheel formed with one inner rolling surface facing the double row outer rolling surface, and the other inner rolling member fitted to the hub wheel and facing the outer surface of the double row on the outer periphery. An inner member formed of an outer joint member of the constant velocity universal joint having a surface formed thereon, and a double row rolling element housed movably between both rolling surfaces of the inner member and the outer member; A seal mounted in an opening of an annular space formed between the outer member and the inner member; Wherein the hub wheel and the manufacturing method of the outer joint member is plastically bonded wheel support bearing assembly together, rolling pitch diameter of the rolling element row on the inner side of the outer side of the rolling element row of the double row The diameter is set to be larger than the pitch circle diameter of the moving body row, the number of rolling elements on the inner side is set to be larger than the number of rolling elements on the outer side, and the hub wheel is carbon 0.40-0. The wheel that is formed from a medium carbon steel containing 80% by weight into a desired shape and size by turning, and then tempered to a predetermined surface hardness and serves as a seal land portion of the inner rolling surface and the seal irregular portion formed on the base and the inner periphery of the inner side of the mounting flange a predetermined hardened layer on the surface by induction hardening is formed, then, crimping by bite into the outer joint member into the irregular portion, the hub wheel And the outer joint member is plastically bonded.

このように、ハブ輪と外側継手部材とが一体に塑性結合された第４世代構造の車輪用軸受装置の製造方法において、複列の転動体列のうちインナー側の転動体列のピッチ円直径がアウター側の転動体列のピッチ円直径よりも大径に設定され、このインナー側の転動体の個数がアウター側の転動体の個数よりも多く設定されると共に、ハブ輪が炭素０．４０〜０．８０重量％を含む中炭素鋼から旋削加工によって所望の形状・寸法に形成され、その後、所定の表面硬さに調質処理され、内側転走面とシールのシールランド部となる車輪取付フランジのインナー側の基部および内周に形成された凹凸部が高周波焼入れによって表面に所定の硬化層が形成され、その後、外側継手部材を凹凸部に食い込ませて加締め、ハブ輪と外側継手部材とが塑性結合されるので、軸受スペースを有効に活用して装置の軽量・コンパクト化を図り、軸受剛性の増大と軸受の長寿命化を図ると共に、車輪取付フランジの形状・寸法を変更することなく、また、現行の加工方法や既存設備のままでハブ輪の強度・耐久性を高めることができる。さらに、調質処理により、熱処理変形を抑制することができ、凹凸部の形成が正確にできる。
Thus, in the manufacturing method of the wheel bearing device of the fourth generation structure in which the hub wheel and the outer joint member are integrally plastically coupled, the pitch circle diameter of the inner rolling element row of the double row rolling element rows Is set to be larger than the pitch circle diameter of the outer side rolling element row, the number of inner side rolling elements is set to be larger than the number of outer side rolling elements, and the hub wheel is carbon 0.40. A wheel that is formed into a desired shape and dimensions by turning from medium carbon steel containing ˜0.80% by weight, and then tempered to a predetermined surface hardness to become the inner rolling surface and the seal land part of the seal The base portion on the inner side of the mounting flange and the concave and convex portions formed on the inner periphery are subjected to induction hardening to form a predetermined hardened layer on the surface, and then the outer joint member is bitten into the concave and convex portions and caulked, and the hub wheel and the outer joint The material is plastic Since the engagement, by effectively utilizing the bearing space reducing the weight and size of the apparatus, together with the prolong the life of the increase and the bearing of the bearing stiffness, without changing the shape and dimensions of the wheel mounting flange, also The strength and durability of the hub wheel can be improved with the current processing method and existing equipment. Furthermore, heat treatment deformation can be suppressed by the tempering treatment, and the uneven portion can be formed accurately.

好ましくは、請求項２に記載の発明のように、前記ハブ輪の調質処理後の表面硬さが３５ＨＲＣ以下に設定されていれば、切削等の加工性が向上すると共に、熱処理変形を抑制することができる。また、車輪取付フランジに圧入されるハブボルトのボルト孔の表面硬さがハブボルトの表面硬さに近付き、ハブボルトを圧入する時に、ナールが潰れて固着力が低下するのを防止できると共に、圧入後のブレーキロータ取付面の変形を防止して、ブレーキジャダーの原因となる面振れを抑えることができる。   Preferably, when the surface hardness of the hub wheel after the tempering treatment is set to 35 HRC or less as in the invention described in claim 2, the workability of cutting and the like is improved and the heat treatment deformation is suppressed. can do. Moreover, the surface hardness of the bolt hole of the hub bolt that is press-fitted into the wheel mounting flange approaches the surface hardness of the hub bolt. The deformation of the brake rotor mounting surface can be prevented, and the surface runout causing the brake judder can be suppressed.

また、請求項３に記載の発明のように、前記ハブ輪の内周に硬化した凹凸部が形成されると共に、前記外側継手部材が、カップ状のマウス部と、このマウス部の底部となる肩部と、この肩部から軸方向に延び、前記ハブ輪に所定のシメシロを介して内嵌されるインロウ部、およびこのインロウ部の端部に形成された嵌合部とからなるステム部とを備え、前記嵌合部を拡径することにより、当該嵌合部を塑性変形させて前記ハブ輪の凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材が塑性結合されて一体化されていても良い。   Further, as in the invention described in claim 3, a hardened uneven portion is formed on the inner periphery of the hub wheel, and the outer joint member becomes a cup-shaped mouth portion and a bottom portion of the mouth portion. A stem portion that includes a shoulder portion, an inrow portion that extends in an axial direction from the shoulder portion, and is fitted into the hub wheel via a predetermined shimiro, and a fitting portion formed at an end portion of the inrow portion; And expanding the fitting portion to cause plastic deformation of the fitting portion to bite into the concavo-convex portion of the hub wheel and caulking, and the hub wheel and the outer joint member are plastically coupled and integrated. May be.

また、請求項４に記載の発明のように、前記車輪取付フランジにハブボルトを圧入した後に、前記ブレーキロータ取付面が旋削加工されていれば、ブレーキロータ取付面の面振れをさらに向上させることができると共に、従来のように、硬化された隅部との硬度差によりブレーキロータ取付面に旋削加工による段差が生じる恐れがない。
Moreover, if the brake rotor mounting surface is turned after the hub bolt is press-fitted into the wheel mounting flange as in the invention described in claim 4 , the runout of the brake rotor mounting surface can be further improved. In addition, unlike the prior art, there is no risk of a step due to turning on the brake rotor mounting surface due to the difference in hardness from the hardened corner.

本発明に係る車輪用軸受装置の製造方法は、ハブ輪と複列の転がり軸受および等速自在継手がユニット化された車輪用軸受装置の製造方法であって、外周に懸架装置に取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内側転走面が形成されたハブ輪、およびこのハブ輪に嵌合され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された前記等速自在継手の外側継手部材からなる内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体と、前記外方部材と内方部材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、前記ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装置の製造方法において、前記複列の転動体列のうちインナー側の転動体列のピッチ円直径がアウター側の転動体列のピッチ円直径よりも大径に設定され、このインナー側の転動体の個数が前記アウター側の転動体の個数よりも多く設定されると共に、前記ハブ輪が炭素０．４０〜０．８０重量％を含む中炭素鋼から旋削加工によって所望の形状・寸法に形成され、その後、所定の表面硬さに調質処理され、前記内側転走面と前記シールのシールランド部となる前記車輪取付フランジのインナー側の基部および内周に形成された凹凸部が高周波焼入れによって表面に所定の硬化層が形成され、その後、前記外側継手部材を前記凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材とが塑性結合されるので、軸受スペースを有効に活用して装置の軽量・コンパクト化を図り、軸受剛性の増大と軸受の長寿命化を図ると共に、車輪取付フランジの形状・寸法を変更することなく、また、現行の加工方法や既存設備のままでハブ輪の強度・耐久性を高めることができる。さらに、調質処理により、熱処理変形を抑制することができ、凹凸部の形成が正確にできる。
Method of manufacturing a wheel bearing device according to the present invention, since the rolling bearing and a constant velocity universal joint of the hub wheel and a double row method for manufacturing a unitized wheel bearing apparatus is mounted on the suspension unit on the outer circumference An outer member in which a double row outer rolling surface is formed on the inner periphery, a wheel mounting flange on one end, and an outer rolling in the double row on the outer periphery. The hub wheel in which one inner rolling surface facing the surface is formed, and the other inner rolling surface that is fitted to the hub wheel and that faces the outer rolling surface of the double row are formed on the outer periphery. An inner member composed of an outer joint member of a constant velocity universal joint, a double row rolling element accommodated between both rolling surfaces of the inner member and the outer member, and the outer member And a seal attached to an opening of an annular space formed between the inner member and the hub. A method of manufacturing the outer joint member is plastically bonded wheel support bearing assembly together, the pitch circle of the rolling element row pitch diameter of rolling element row of the inner side outer side of the rolling element row of the double row The diameter is set to be larger than the diameter, and the number of rolling elements on the inner side is set to be larger than the number of rolling elements on the outer side, and the hub ring includes 0.40 to 0.80% by weight of carbon. The inner side of the wheel mounting flange that is formed from a medium carbon steel into a desired shape and size by turning, and then tempered to a predetermined surface hardness and serves as a seal land portion of the inner rolling surface and the seal irregular portion formed on the base and the inner periphery of a predetermined hardened layer on the surface by induction hardening is formed, then, the outer joint member caulked by bite into the irregular portion, the hub wheel and the outer joint member Since the plastic bonded, by effectively utilizing the bearing space reducing the weight and size of the apparatus, together with the prolong the life of the increase and the bearing of the bearing stiffness, without changing the shape and dimensions of the wheel mounting flange, In addition, the strength and durability of the hub wheel can be increased with the current processing method and existing equipment. Furthermore, heat treatment deformation can be suppressed by the tempering treatment, and the uneven portion can be formed accurately.

ハブ輪と複列の転がり軸受および等速自在継手がユニット化された車輪用軸受装置の製造方法であって、外周に懸架装置に取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内側転走面と、この内側転走面から軸方向に延びる円筒状の小径段部が形成されたハブ輪、およびこのハブ輪に嵌合される中空状のステム部を一体に有し、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された前記等速自在継手の外側継手部材からなる内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体と、前記外方部材と内方部材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、前記ハブ輪の内周に硬化した凹凸部が形成されると共に、前記外側継手部材のステム部を拡径させて前記凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装置の製造方法において、前記複列の転動体列のうちインナー側の転動体列のピッチ円直径がアウター側の転動体列のピッチ円直径よりも大径に設定され、このインナー側の転動体の個数が前記アウター側の転動体の個数よりも多く設定されると共に、前記ハブ輪が炭素０．４０〜０．８０重量％を含む中炭素鋼から旋削加工によって所望の形状・寸法に形成され、その後、所定の表面硬さに調質処理されて表面硬さが３５ＨＲＣ以下に設定され、前記内側転走面と前記シールのシールランド部となる前記車輪取付フランジのインナー側の基部および内周に形成された凹凸部が高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化層が形成され、その後、前記外側継手部材を前記凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材とが塑性結合される。
A manufacturing method of a wheel bearing device in which a hub wheel, a double row rolling bearing and a constant velocity universal joint are unitized, and has a vehicle body mounting flange to be attached to a suspension device on the outer periphery, and on the inner periphery An outer member formed with a double row outer rolling surface, a wheel mounting flange integrally formed at one end, and one inner rolling surface facing the double row outer rolling surface on the outer periphery, A hub wheel having a cylindrical small-diameter step portion extending in the axial direction from the inner rolling surface and a hollow stem portion fitted to the hub wheel are integrally formed, and the outer circumferential rolling of the double row is arranged on the outer periphery. An inner member composed of an outer joint member of the constant velocity universal joint formed with the other inner rolling surface facing the running surface, and freely rollable between both rolling surfaces of the inner member and the outer member. A double row of rolling elements housed in the outer space and an annular space formed between the outer member and the inner member. A seal attached to the mouth, and a hardened uneven portion is formed on the inner periphery of the hub wheel, and the stem portion of the outer joint member is expanded to bite into the uneven portion and caulked, In the method of manufacturing a wheel bearing device in which the hub wheel and the outer joint member are integrally plastically coupled, a pitch circle diameter of an inner rolling element row of the double row rolling element rows is an outer rolling element row. The inner diameter of the rolling elements is set to be larger than the number of the outer rolling elements, and the hub wheel is carbon 0.40 to 0.80 weight. Is formed into a desired shape and dimensions by turning from medium carbon steel containing 50%, then tempered to a predetermined surface hardness to set the surface hardness to 35 HRC or less, and the inner rolling surface and the seal Before becoming the seal land part of Irregular portion formed on the base and the inner periphery of the inner side of the wheel mounting flange is hardened layer surface hardness in the range of 58~64HRC by high frequency induction quenching is formed, then allowed bite into the outer joint member to the concave-convex portion Then, the hub wheel and the outer joint member are plastically coupled.

以下、本発明の実施の形態を図面に基づいて詳細に説明する。
図１は、本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図である。なお、以下の説明では、車両に組み付けた状態で車両の外側寄りとなる側をアウター側（図面左側）、中央寄り側をインナー側（図面右側）という。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a wheel bearing device according to the present invention. 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、ハブ輪１と複列の転がり軸受２および等速自在継手３をユニット化して構成され、第４世代と称される構成を備えている。複列の転がり軸受２は、外方部材４と内方部材５、および両部材間に収容された複列の転動体（ボール）６、６とを備えている。   This wheel bearing device is configured by unitizing the hub wheel 1, the double row rolling bearing 2 and the constant velocity universal joint 3, and has a configuration referred to as a fourth generation. The double row rolling bearing 2 includes an outer member 4, an inner member 5, and double row rolling elements (balls) 6, 6 accommodated between the two members.

外方部材４はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、外周にナックル（図示せず）に取り付けられるための車体取付フランジ４ｃを一体に有し、内周に複列の外側転走面４ａ、４ｂが形成されている。そして、これら複列の外側転走面４ａ、４ｂが高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。   The outer member 4 is formed of medium carbon steel containing 0.40 to 0.80% by weight of carbon such as S53C, and integrally includes a vehicle body mounting flange 4c to be attached to a knuckle (not shown) on the outer periphery. Double row outer rolling surfaces 4a and 4b are formed on the inner periphery. And these double row outer side rolling surfaces 4a and 4b are hardened by induction hardening in the range of 58-64 HRC surface hardness.

内方部材５は、ハブ輪１と、このハブ輪１に内嵌された後述する外側継手部材１０とを備えている。ハブ輪１は、アウター側の端部に車輪（図示せず）を取り付けるための車輪取付フランジ７を一体に有し、外周に複列の外側転走面４ａ、４ｂに対向する一方（アウター側）の内側転走面１ａと、この内側転走面１ａから軸方向に延びる円筒状の小径段部１ｂが形成されている。車輪取付フランジ７の周方向等配には車輪を固定するハブボルト８が植設されている。このハブ輪１はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、内側転走面１ａをはじめ、後述するアウター側のシール１９のシールランド部となる車輪取付フランジ７のインナー側の基部２５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の範囲に所定の硬化層２１（図中クロスハッチングにて示す）が形成されている。   The inner member 5 includes a hub wheel 1 and an outer joint member 10 to be described later that is fitted into the hub wheel 1. The hub wheel 1 integrally has a wheel mounting flange 7 for mounting a wheel (not shown) at an end portion on the outer side, and is opposed to the double row outer rolling surfaces 4a and 4b on the outer periphery (outer side). ) And a cylindrical small-diameter step portion 1b extending in the axial direction from the inner rolling surface 1a. Hub bolts 8 for fixing the wheels are planted at equal intervals in the circumferential direction of the wheel mounting flange 7. The hub wheel 1 is made of medium carbon steel containing 0.40 to 0.80% by weight of carbon, such as S53C, and is attached to a wheel that serves as a seal land part of an outer side seal 19 to be described later, including the inner rolling surface 1a. A predetermined hardened layer 21 (indicated by cross-hatching in the figure) is formed in the range of 58 to 64 HRC by induction hardening from the base portion 25 on the inner side of the flange 7 to the small diameter step portion 1b.

ここで、ハブ輪１の内周には凹凸部９が形成されている。この凹凸部９はアヤメローレット状に形成され、旋削等により独立して形成された複数の環状溝と、ブローチ加工等により形成された複数の軸方向溝とを略直交させて構成した交叉溝、あるいは、互いに傾斜した螺旋溝で構成した交叉溝からなる。また、凹凸部９は、良好な食い込み性を確保するためにその凸部の先端部が三角形状等の尖塔形状に形成されると共に、高周波焼入れによって所定の硬化層２２（図中クロスハッチングにて示す）が形成されている。   Here, an uneven portion 9 is formed on the inner periphery of the hub wheel 1. The concavo-convex portion 9 is formed in an iris knurl shape, and a plurality of annular grooves formed independently by turning or the like and a plurality of axial grooves formed by broaching or the like are crossed grooves configured to be substantially orthogonal, Or it consists of the crossing groove | channel comprised by the helical groove | channel inclined mutually. In addition, in order to ensure good bite, the concavo-convex portion 9 has a tip portion of a convex portion formed in a spire shape such as a triangular shape and a predetermined hardened layer 22 (by cross-hatching in the figure) by induction hardening. Is formed).

等速自在継手３は、外側継手部材１０と、継手内輪１１と、ケージ１２およびトルク伝達ボール１３からなる。外側継手部材１０は、カップ状のマウス部１４と、このマウス部１４の底部をなす肩部１５と、この肩部１５から軸方向に延びる中空状のステム部１６が一体に形成されている。そして、肩部１５の外周に、外方部材４の複列の外側転走面４ａ、４ｂに対向する他方（インナー側）の内側転走面１０ａが形成されている。また、ステム部１６には、ハブ輪１の小径段部１ｂに所定のシメシロを介して円筒嵌合するインロウ部１６ａと、このインロウ部１６ａの端部に嵌合部１６ｂがそれぞれ形成されている。   The constant velocity universal joint 3 includes an outer joint member 10, a joint inner ring 11, a cage 12 and a torque transmission ball 13. The outer joint member 10 is integrally formed with a cup-shaped mouth portion 14, a shoulder portion 15 that forms the bottom portion of the mouth portion 14, and a hollow stem portion 16 that extends from the shoulder portion 15 in the axial direction. And the other (inner side) inner side rolling surface 10a which opposes the double row outer side rolling surfaces 4a and 4b of the outer member 4 is formed in the outer periphery of the shoulder part 15. As shown in FIG. The stem portion 16 is formed with an inrow portion 16a that is cylindrically fitted to the small-diameter step portion 1b of the hub wheel 1 via a predetermined shimiro, and a fitting portion 16b is formed at the end of the inrow portion 16a. .

外側継手部材１０はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、内側転走面１０ａをはじめ、肩部１５の外周からステム部１６のインロウ部１６ａに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に所定の硬化層２３（図中クロスハッチングにて示す）が形成されている。なお、嵌合部１６ｂは鍛造後の表面硬さの生のままとされている。   The outer joint member 10 is formed of medium carbon steel containing carbon of 0.40 to 0.80% by weight such as S53C, and the inner joint surface 10a and the outer periphery of the shoulder portion 15 to the inrow portion 16a of the stem portion 16 Thus, a predetermined hardened layer 23 (indicated by cross-hatching in the figure) is formed in a surface hardness of 58 to 64 HRC by induction hardening. In addition, the fitting part 16b is left with the raw surface hardness after forging.

外方部材４と内方部材５のそれぞれの転走面４ａ、１ａと４ｂ、１０ａ間に複列の転動体６、６が収容され、保持器１７、１８によりこれら複列の転動体６、６が転動自在に保持されている。また、外方部材４と内方部材５との間に形成される環状空間の開口部にはシール１９、２０が装着され、軸受内部に封入した潤滑グリースの漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。なお、ここでは、複列の転がり軸受２として転動体６にボールを用いた複列アンギュラ玉軸受を例示したが、これに限らず、例えば、転動体に円すいころを用いた複列円すいころ軸受であっても良い。   Double-row rolling elements 6, 6 are accommodated between the rolling surfaces 4a, 1a and 4b, 10a of the outer member 4 and the inner member 5, and these double-row rolling elements 6, 18 are held by the cages 17, 18; 6 is rotatably held. Further, seals 19 and 20 are attached to the opening of the annular space formed between the outer member 4 and the inner member 5, leakage of lubricating grease sealed inside the bearing, rainwater, dust, etc. from the outside Is prevented from entering the inside of the bearing. Here, the double-row angular contact ball bearing using balls as the rolling elements 6 is illustrated as the double-row rolling bearing 2, but not limited to this, for example, double-row tapered roller bearings using tapered rollers as the rolling elements. It may be.

ここで、本実施形態では、インナー側の転動体６列のピッチ円直径ＰＣＤｉがアウター側の転動体６列のピッチ円直径ＰＣＤｏよりも大径に設定されている。すなわち、複列の転動体６、６列のピッチ円直径ＰＣＤｏ、ＰＣＤｉの違いに伴い、内方部材５において、外側継手部材１０における内側転走面１０ａの溝底径はハブ輪１における内側転走面１ａの溝底径よりも拡径して形成されている。一方、外方部材４において、インナー側の外側転走面４ｂの溝底径がアウター側の外側転走面４ａの溝底径よりも拡径して形成されている。したがって、複列の転動体６、６の外径は同じであるが、軸受スペースを有効に活用してピッチ円直径ＰＣＤｏ、ＰＣＤｉを異ならすことができ、インナー側の転動体６列の個数をアウター側の転動体６列の個数よりも多く収容することができる。したがって、装置の軽量・コンパクト化を図ると共に、軸受剛性の増大と軸受の長寿命化を図ることができる。   Here, in the present embodiment, the pitch circle diameter PCDi of the six inner rolling elements is set larger than the pitch circle diameter PCDo of the outer six rolling elements. That is, the groove bottom diameter of the inner rolling surface 10a of the outer joint member 10 in the inner member 5 is the inner rolling force of the hub wheel 1 due to the difference between the double row rolling elements 6 and the pitch circle diameters PCDo and PCDi of the six rows. The diameter is larger than the groove bottom diameter of the running surface 1a. On the other hand, in the outer member 4, the groove bottom diameter of the inner side outer rolling surface 4b is formed larger than the groove bottom diameter of the outer side outer rolling surface 4a. Therefore, the outer diameters of the double-row rolling elements 6 and 6 are the same, but the pitch circle diameters PCDo and PCDi can be made different by effectively utilizing the bearing space, and the number of the inner-side rolling elements 6 rows can be reduced. It is possible to accommodate more than the number of the six rolling elements on the outer side. Therefore, it is possible to reduce the weight and size of the apparatus, increase the bearing rigidity, and extend the life of the bearing.

ハブ輪１と外側継手部材１０との一体化は、ハブ輪１に外側継手部材１０のステム部１６が所定のシメシロで圧入され、小径段部１ｂの端面に外側継手部材１０の肩部１５が衝合された状態で、嵌合部１６ｂの内径にマンドレル等の拡径治具をアウター側に押し込んで嵌合部１６ｂを拡径することにより行われる。すなわち、嵌合部１６ｂを塑性変形させてハブ輪１の凹凸部９に食い込ませて加締めることにより、ハブ輪１と外側継手部材１０が塑性結合されて一体化されている。これにより、結合部の緩みを防止し、長期間に亙って初期に設定された軸受予圧を維持することができる。符号２４は、外側継手部材１０の肩部１５に内嵌されたエンドキャップで、継手内部に封入された潤滑グリースの外部への漏洩と、外部から継手内部に雨水やダスト等の異物が侵入するのを防止している。   The integration of the hub wheel 1 and the outer joint member 10 is performed by press-fitting the stem portion 16 of the outer joint member 10 into the hub wheel 1 with a predetermined squeeze, and the shoulder 15 of the outer joint member 10 on the end surface of the small-diameter step portion 1b. In the abutted state, it is performed by pushing a diameter-expansion jig such as a mandrel into the inner diameter of the fitting portion 16b toward the outer side to increase the diameter of the fitting portion 16b. That is, the hub wheel 1 and the outer joint member 10 are plastically coupled and integrated by plastically deforming the fitting portion 16b and biting into the uneven portion 9 of the hub wheel 1 and caulking. As a result, loosening of the coupling portion can be prevented, and the initially set bearing preload can be maintained over a long period of time. Reference numeral 24 denotes an end cap that is fitted into the shoulder 15 of the outer joint member 10. Leakage of the lubricating grease sealed inside the joint and foreign matters such as rainwater and dust enter the joint from the outside. Is preventing.

ハブ輪１は、素材を熱間鍛造後、旋削加工によって所望の形状・寸法に形成され、その後、後述する調質処理が施されている。そして、図２に示すように、車輪取付フランジ７におけるアウター側の付け根部、すなわち、ブレーキロータ取付面２６と、ブレーキロータ（図示せず）の支持面となる円筒状のパイロット部２７との間の隅部２８は、ブレーキロータが干渉しない程度の曲率半径を有する円弧面（またはヌスミ）に形成されている。   The hub wheel 1 is formed into a desired shape / dimension by turning after hot forging the material, and then subjected to a tempering process to be described later. As shown in FIG. 2, the outer base portion of the wheel mounting flange 7, that is, between the brake rotor mounting surface 26 and the cylindrical pilot portion 27 serving as a support surface of the brake rotor (not shown). The corner 28 is formed in an arcuate surface (or a slug) having a radius of curvature that does not interfere with the brake rotor.

本実施形態では、ハブ輪１は、高周波による４００℃以上の高温焼戻しをして、トルースタイトまたはソルバイト組織にする、所謂調質処理が施されている。この調質処理により組織は粒状化し、引張、曲げ、衝撃値等の機械的性質が上昇して延性や靭性が高まる。ここでは、ハブ輪１の調質処理により、車輪取付フランジ７のブレーキロータ取付面２６とパイロット部２７および隅部２８の調質処理後の表面硬さが３５ＨＲＣ以下に設定されている。これにより、切削等の加工性が向上すると共に、熱処理変形を抑制することができる。また、車輪取付フランジ７に圧入されるハブボルト８のボルト孔８ａの表面硬さがハブボルト８の表面硬さに近付き、ハブボルト８を圧入する時に、ナール（セレーション）が潰れて固着力が低下するのを防止できると共に、圧入後のブレーキロータ取付面２６の変形を防止して、ブレーキジャダーの原因となる面振れを抑えることができる。   In the present embodiment, the hub wheel 1 is subjected to a so-called tempering treatment in which high-temperature tempering at 400 ° C. or higher with a high frequency is performed to obtain a troostite or sorbite structure. By this tempering treatment, the structure is granulated, and mechanical properties such as tension, bending, and impact value are increased, and ductility and toughness are increased. Here, the surface hardness of the brake rotor mounting surface 26, the pilot portion 27, and the corner portion 28 of the wheel mounting flange 7 after the tempering process is set to 35 HRC or less by the tempering process of the hub wheel 1. Thereby, workability, such as cutting, can be improved and heat treatment deformation can be suppressed. Further, the surface hardness of the bolt hole 8a of the hub bolt 8 press-fitted into the wheel mounting flange 7 approaches the surface hardness of the hub bolt 8, and when the hub bolt 8 is press-fitted, the knurles are crushed and the fixing force is reduced. Can be prevented, and deformation of the brake rotor mounting surface 26 after press-fitting can be prevented to suppress surface runout that causes brake judder.

このように、ハブ輪１を旋削加工後に調質処理を施し、所望の表面硬さに設定することにより、車輪取付フランジ７の形状・寸法を変更することなく、また現行の加工方法や既存設備のままで、回転曲げ疲労の最弱部となる隅部２８および基部２５の強度を高めることができ、ハブ輪１の軽量・コンパクト化を図りつつ、耐久性を向上させることができる。   In this way, the hub wheel 1 is subjected to a tempering process after turning and set to a desired surface hardness, so that the shape and dimensions of the wheel mounting flange 7 are not changed, and the current machining method and existing equipment are changed. As it is, the strength of the corner portion 28 and the base portion 25 which are the weakest portions of the rotating bending fatigue can be increased, and the durability can be improved while reducing the weight and size of the hub wheel 1.

なお、車輪取付フランジ７におけるブレーキロータ取付面２６の面振れをさらに向上させるため、ハブボルト８を圧入した後にブレーキロータ取付面２６を旋削加工することもできるので、従来のように、硬化された隅部との硬度差によりブレーキロータ取付面２６に旋削加工による段差が生じる恐れがない。   In order to further improve the surface runout of the brake rotor mounting surface 26 in the wheel mounting flange 7, the brake rotor mounting surface 26 can be turned after the hub bolt 8 is press-fitted, so that the hardened corners can be hardened as in the prior art. There is no possibility that a step due to the turning process occurs on the brake rotor mounting surface 26 due to the difference in hardness from the portion.

図３は本発明に係る車輪用軸受装置の第２の実施形態を示す縦断面図である。なお、この実施形態は、基本的には前述した実施形態と塑性結合部の構成が異なるだけで、その他第１の実施形態と同一部位、同一部品、あるいは同一の機能を有する部位には同じ符号を付けてその詳細な説明を省略する。   FIG. 3 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment basically differs from the above-described embodiment only in the configuration of the plastic coupling portion, and other parts having the same parts, the same parts, or the same functions as those of the first embodiment have the same reference numerals. The detailed description is omitted.

この車輪用軸受装置は、ハブ輪２９と複列の転がり軸受３０および等速自在継手３１をユニット化して構成され、第４世代と称される構成を備えている。複列の転がり軸受３０は、外方部材４と内方部材３２、および両部材間に収容された複列の転動体６、６とを備えている。   This wheel bearing device is configured by unitizing the hub wheel 29, the double-row rolling bearing 30 and the constant velocity universal joint 31, and has a configuration referred to as a fourth generation. The double row rolling bearing 30 includes an outer member 4, an inner member 32, and double row rolling elements 6 and 6 accommodated between both members.

内方部材３２は、ハブ輪２９と、このハブ輪２９に外嵌された後述する外側継手部材３５とを備えている。ハブ輪２９は、アウター側の端部に車輪取付フランジ７を一体に有し、外周に複列の外側転走面４ａ、４ｂに対向する一方（アウター側）の内側転走面１ａと、この内側転走面１ａから軸方向に延びる中空状のステム部３３が形成されている。このステム部３３は、外側継手部材３５に所定のシメシロを介して円筒嵌合するインロウ部３３ａと、このインロウ部３３ａの端部に嵌合部３３ｂがそれぞれ形成されている。   The inward member 32 includes a hub wheel 29 and an outer joint member 35 (described later) that is externally fitted to the hub wheel 29. The hub wheel 29 integrally has a wheel mounting flange 7 at an end portion on the outer side, and one (outer side) inner rolling surface 1a facing the double row outer rolling surfaces 4a and 4b on the outer periphery. A hollow stem portion 33 extending in the axial direction from the inner rolling surface 1a is formed. The stem portion 33 is formed with an in-row portion 33a that is cylindrically fitted to the outer joint member 35 via a predetermined shimiro, and a fitting portion 33b is formed at the end of the in-row portion 33a.

ハブ輪２９はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、内側転走面１ａをはじめ、アウター側のシール１９のシールランド部となる車輪取付フランジ７のインナー側の基部２５からステム部３３に亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に所定の硬化層３４（図中クロスハッチングにて示す）が形成されている。なお、嵌合部３３ｂは鍛造後の表面硬さの生のままとされている。   The hub wheel 29 is formed of medium carbon steel containing carbon of 0.40 to 0.80% by weight such as S53C, and the wheel mounting flange 7 serving as a seal land portion of the outer side seal 19 including the inner rolling surface 1a. A predetermined hardened layer 34 (indicated by cross-hatching in the figure) is formed with a surface hardness in the range of 58 to 64 HRC by induction hardening from the base portion 25 on the inner side to the stem portion 33. In addition, the fitting part 33b is left with the raw surface hardness after forging.

等速自在継手３１は、外側継手部材３５と、図示しない継手内輪とケージおよびトルク伝達ボールからなる。外側継手部材３５は、カップ状のマウス部１４と、このマウス部１４の底部をなす肩部３６と、この肩部３６から軸方向に延びる円筒状の小径段部３７が一体に形成されている。そして、肩部３６の外周に、外方部材４の複列の外側転走面４ａ、４ｂに対向する他方（インナー側）の内側転走面１０ａが形成されると共に、内周に硬化された凹凸部９が形成されている。   The constant velocity universal joint 31 includes an outer joint member 35, a joint inner ring (not shown), a cage, and a torque transmission ball. The outer joint member 35 is integrally formed with a cup-shaped mouth portion 14, a shoulder portion 36 that forms the bottom of the mouth portion 14, and a cylindrical small-diameter step portion 37 that extends in the axial direction from the shoulder portion 36. . And the other inner (inner side) inner rolling surface 10a facing the outer rolling surfaces 4a, 4b of the double row of the outer member 4 is formed on the outer periphery of the shoulder portion 36, and hardened to the inner periphery. Uneven portions 9 are formed.

外側継手部材３５はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中炭素鋼で形成され、内側転走面１０ａをはじめ、後述するインナー側のシール３８のシールランド部となる肩部３６の外周から小径段部３７に亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に所定の硬化層３９（図中クロスハッチングにて示す）が形成されている。   The outer joint member 35 is formed of medium carbon steel containing carbon of 0.40 to 0.80% by weight, such as S53C, and includes a shoulder portion serving as a seal land portion of an inner side seal 38 to be described later, including the inner rolling surface 10a. A predetermined hardened layer 39 (shown by cross-hatching in the figure) is formed in the range of 58 to 64 HRC by induction hardening from the outer periphery of 36 to the small diameter step portion 37.

外方部材４と内方部材３２のそれぞれの転走面４ａ、１ａと４ｂ、１０ａ間に複列の転動体６、６が収容され、保持器１７、１８によりこれら複列の転動体６、６が転動自在に保持されている。また、外方部材４と内方部材３２との間に形成される環状空間の開口部にはシール１９、３８が装着され、軸受内部に封入した潤滑グリースの漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   Double-row rolling elements 6 and 6 are accommodated between the rolling surfaces 4a, 1a and 4b and 10a of the outer member 4 and the inner member 32, and the double-row rolling elements 6 and 6 are held by the cages 17 and 18, respectively. 6 is rotatably held. Further, seals 19 and 38 are attached to the opening of the annular space formed between the outer member 4 and the inner member 32, leakage of lubricating grease sealed inside the bearing, rainwater, dust, etc. from the outside Is prevented from entering the inside of the bearing.

ここで、本実施形態では、前述した実施形態と同様、インナー側の転動体６列のピッチ円直径ＰＣＤｉがアウター側の転動体６列のピッチ円直径ＰＣＤｏよりも大径に設定されている。そして、インナー側の転動体６列の個数がアウター側の転動体６列の個数よりも多く設定されている。したがって、装置の軽量・コンパクト化を図ると共に、軸受剛性の増大と軸受の長寿命化を図ることができる。   Here, in this embodiment, the pitch circle diameter PCDi of the six rows of rolling elements on the inner side is set larger than the pitch circle diameter PCDo of the six rows of rolling elements on the outer side, as in the above-described embodiment. And the number of the inner side rolling element 6 row | line is set more than the number of the outer side rolling element 6 row | line | column. Therefore, it is possible to reduce the weight and size of the apparatus, increase the bearing rigidity, and extend the life of the bearing.

外側継手部材３５にハブ輪２９のステム部３３が所定のシメシロで圧入され、ハブ輪２９の嵌合部３３ｂの内径にマンドレル等の拡径治具を押し込んで嵌合部３３ｂを拡径することにより塑性変形させて外側継手部材３５の凹凸部９に食い込ませて加締めることにより、ハブ輪２９と外側継手部材３５が塑性結合されて一体化されている。   The stem portion 33 of the hub wheel 29 is press-fitted into the outer joint member 35 with a predetermined squeezing force, and the fitting portion 33b is expanded by pushing a diameter expanding jig such as a mandrel into the inner diameter of the fitting portion 33b of the hub wheel 29. Thus, the hub wheel 29 and the outer joint member 35 are plastically coupled and integrated by being plastically deformed and biting into the concavo-convex portion 9 of the outer joint member 35 and caulking.

ハブ輪２９は、素材を熱間鍛造後、旋削加工によって所望の形状・寸法に形成され、その後、高周波による４００℃以上の高温焼戻しをして調質処理が施されている。そして、ハブ輪２９の調質処理により、車輪取付フランジ７のブレーキロータ取付面２６とパイロット部２７および隅部２８の調質処理後の表面硬さが３５ＨＲＣ以下に設定されている。これにより、車輪取付フランジ７の形状・寸法を変更することなく、また現行の加工方法や既存設備のままで、回転曲げ疲労の最弱部となる隅部２８および基部２５の強度を高めることができ、ハブ輪２９の軽量・コンパクト化を図りつつ、耐久性を向上させることができる。   The hub wheel 29 is formed into a desired shape and size by turning after hot forging the material, and then subjected to a tempering treatment by high-temperature tempering at 400 ° C. or higher by high frequency. The surface hardness of the brake rotor mounting surface 26, the pilot portion 27, and the corner portion 28 of the wheel mounting flange 7 after the tempering processing is set to 35 HRC or less by the tempering processing of the hub wheel 29. Thereby, the strength of the corner portion 28 and the base portion 25 which are the weakest portions of the rotational bending fatigue can be increased without changing the shape and dimensions of the wheel mounting flange 7 and with the current processing method and existing equipment. This makes it possible to improve durability while reducing the weight and size of the hub wheel 29.

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の製造方法は、ハブ輪と外側継手部材が塑性結合された第４世代構造の車輪用軸受装置に適用することができる。 The method for manufacturing a wheel bearing device according to the present invention can be applied to a wheel bearing device having a fourth generation structure in which a hub wheel and an outer joint member are plastically coupled.

本発明に係る車輪用軸受装置の第１の実施形態を示す縦断面図である。It is a longitudinal section showing a 1st embodiment of a bearing device for wheels concerning the present invention. 図１のハブ輪単体を示す拡大図である。It is an enlarged view which shows the hub ring single-piece | unit of FIG. 本発明に係る車輪用軸受装置の第２の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 2nd Embodiment of the wheel bearing apparatus which concerns on this invention. 従来の車輪用軸受装置を示す縦断面図である。It is a longitudinal cross-sectional view which shows the conventional wheel bearing apparatus. 図４のハブ輪単体を示す拡大図である。It is an enlarged view which shows the hub ring single-piece | unit of FIG.

符号の説明Explanation of symbols

１、２９・・・・・・・・・・・・・ハブ輪
１ａ、１０ａ・・・・・・・・・・・内側転走面
１ｂ、３７・・・・・・・・・・・・小径段部
２、３０・・・・・・・・・・・・・複列の転がり軸受
３、３１・・・・・・・・・・・・・等速自在継手
４・・・・・・・・・・・・・・・・外方部材
４ａ、４ｂ・・・・・・・・・・・・外側転走面
４ｃ・・・・・・・・・・・・・・・車体取付フランジ
５、３２・・・・・・・・・・・・・内方部材
６・・・・・・・・・・・・・・・・転動体
７・・・・・・・・・・・・・・・・車輪取付フランジ
８・・・・・・・・・・・・・・・・ハブボルト
８ａ・・・・・・・・・・・・・・・ボルト孔
９・・・・・・・・・・・・・・・・凹凸部
１０、３５・・・・・・・・・・・・外側継手部材
１１・・・・・・・・・・・・・・・継手内輪
１２・・・・・・・・・・・・・・・ケージ
１３・・・・・・・・・・・・・・・トルク伝達ボール
１４・・・・・・・・・・・・・・・マウス部
１５、３６・・・・・・・・・・・・肩部
１６・・・・・・・・・・・・・・・ステム部
１６ａ、３３ａ・・・・・・・・・・インロウ部
１６ｂ、３３ｂ・・・・・・・・・・嵌合部
１７、１８・・・・・・・・・・・・保持器
１９、２０、３８・・・・・・・・・シール
２１、２２、２３、３４、３９・・・硬化層
２５・・・・・・・・・・・・・・・車輪取付フランジのインナー側の基部
２６・・・・・・・・・・・・・・・ブレーキロータ取付面
２７・・・・・・・・・・・・・・・パイロット部
２８・・・・・・・・・・・・・・・隅部
５０・・・・・・・・・・・・・・・内方部材
５１・・・・・・・・・・・・・・・ハブ輪
５２・・・・・・・・・・・・・・・内輪
５３、５４・・・・・・・・・・・・転動体
５５・・・・・・・・・・・・・・・外方部材
５６・・・・・・・・・・・・・・・等速自在継手
５７・・・・・・・・・・・・・・・ブレーキロータ
５８・・・・・・・・・・・・・・・車輪取付フランジ
５９・・・・・・・・・・・・・・・ブレーキロータ取付面
６０・・・・・・・・・・・・・・・パイロット部
６１・・・・・・・・・・・・・・・隅部
６２、６３、６５・・・・・・・・・表面硬化層
６４・・・・・・・・・・・・・・・セレーション部
ａ〜ｄ・・・・・・・・・・・・・・部位
ＰＣＤｉ・・・・・・・・・・・・・インナー側の転動体列のピッチ円直径
ＰＣＤｏ・・・・・・・・・・・・・アウター側の転動体列のピッチ円直径 1, 29 ... hub wheel 1a, 10a ... inner rolling surface 1b, 37 ...・ Small diameter step 2, 30 ... Double row rolling bearing 3, 31 ... Constant velocity universal joint 4 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer members 4a, 4b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer rolling surface 4c ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・Car body mounting flange 5, 32 ..... Inward member 6 ........ Rolling element 7 ...・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 8 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub bolt 8a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Bolt hole 9 ・ ・················ Uneven portion 10, 35 ·················· Outer joint member 11・ ・ ・ ・ ・ ・ ・ ・ ・ Fitting inner ring 12 ・ ・ ・ ・ ・ ・ Cage 13 ・ ・ ・ ・ ・ ・ Torque Transmission ball 14 ... Mouse part 15, 36 ... Shoulder part 16 ... ... Stem parts 16a, 33a ... In-row parts 16b, 33b ... Fitting parts 17, 18 ...・ Retainer 19, 20, 38 ......... Seal 21, 22, 23, 34, 39 ... Hardened layer 25 ......... Wheel mounting Flange inner base 26 ... Brake rotor mounting surface 27 ... Pilot 28 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Corner 50 ・... inner member 51 ... hub wheel 52 ... Inner rings 53, 54 ... Rolling elements 55 ... Outer members 56 ... ... Constant velocity universal joint 57 ... Brake rotor 58 ... Wheel mounting flange 59 ... Brake rotor mounting surface 60 ... Pilot part 61 ... Corner 62, 63, 65... Hardened surface layer 64.. ..Part PCDi .................. Piping of the rolling element row on the inner side H Circle diameter PCDo: Pitch circle diameter of the outer rolling element row

Claims (4)

ハブ輪と複列の転がり軸受および等速自在継手がユニット化された車輪用軸受装置の製造方法であって、
外周に懸架装置に取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、
一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内側転走面が形成されたハブ輪、およびこのハブ輪に嵌合され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された前記等速自在継手の外側継手部材からなる内方部材と、
この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体と、
前記外方部材と内方部材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、
前記ハブ輪と外側継手部材とが一体に塑性結合された車輪用軸受装置の製造方法において、
前記複列の転動体列のうちインナー側の転動体列のピッチ円直径がアウター側の転動体列のピッチ円直径よりも大径に設定され、このインナー側の転動体の個数が前記アウター側の転動体の個数よりも多く設定されると共に、
前記ハブ輪が炭素０．４０〜０．８０重量％を含む中炭素鋼から旋削加工によって所望の形状・寸法に形成され、その後、所定の表面硬さに調質処理され、前記内側転走面と前記シールのシールランド部となる前記車輪取付フランジのインナー側の基部および内周に形成された凹凸部が高周波焼入れによって表面に所定の硬化層が形成され、その後、前記外側継手部材を前記凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材とが塑性結合されることを特徴とする車輪用軸受装置の製造方法。 A manufacturing method of a wheel bearing device in which a hub wheel and a double row rolling bearing and a constant velocity universal joint are unitized,
An outer member integrally having a vehicle body mounting flange to be attached to the suspension device on the outer periphery, and having a double row outer rolling surface formed on the inner periphery;
A hub wheel integrally having a wheel mounting flange at one end portion and having one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and fitted to the hub wheel, An inner member composed of an outer joint member of the constant velocity universal joint on which the other inner rolling surface facing the outer rolling surface of the double row is formed;
A double row rolling element housed so as to be freely rollable between both rolling surfaces of the inner member and the outer member;
A seal attached to an opening of an annular space formed between the outer member and the inner member;
In the method of manufacturing a wheel bearing device in which the hub wheel and the outer joint member are integrally plastically coupled,
The pitch circle diameter of the inner side rolling element row of the double row rolling element rows is set larger than the pitch circle diameter of the outer side rolling element row, and the number of inner side rolling elements is the outer side. And more than the number of rolling elements of
The hub wheel is formed from a medium carbon steel containing 0.40 to 0.80% by weight of carbon into a desired shape and size by turning, and then tempered to a predetermined surface hardness, and the inner rolling surface A predetermined hardened layer is formed on the surface of the inner side base and inner periphery of the wheel mounting flange that becomes the seal land portion of the seal by induction hardening , and then the outer joint member is A method for manufacturing a wheel bearing device , wherein the hub wheel and the outer joint member are plastically coupled by being bitten into a portion and crimped . 前記ハブ輪の調質処理後の表面硬さが３５ＨＲＣ以下に設定されている請求項１に記載の車輪用軸受装置の製造方法。 The method for manufacturing a wheel bearing device according to claim 1, wherein the surface hardness of the hub wheel after the tempering treatment is set to 35 HRC or less. 前記ハブ輪の内周に硬化した凹凸部が形成されると共に、前記外側継手部材が、カップ状のマウス部と、このマウス部の底部となる肩部と、この肩部から軸方向に延び、前記ハブ輪に所定のシメシロを介して内嵌されるインロウ部、およびこのインロウ部の端部に形成された嵌合部とからなるステム部とを備え、前記嵌合部を拡径することにより、当該嵌合部を塑性変形させて前記ハブ輪の凹凸部に食い込ませて加締め、前記ハブ輪と外側継手部材が塑性結合されて一体化されている請求項１または２に記載の車輪用軸受装置の製造方法。 A hardened uneven portion is formed on the inner periphery of the hub wheel, and the outer joint member extends in the axial direction from the cup-shaped mouth portion, a shoulder portion serving as the bottom portion of the mouth portion, and the shoulder portion, A stem portion including an inrow portion fitted into the hub wheel via a predetermined shimoshiro and a fitting portion formed at an end portion of the inrow portion, and by expanding the diameter of the fitting portion 3. The wheel according to claim 1, wherein the fitting portion is plastically deformed so as to bite into the concavo-convex portion of the hub wheel and caulked, and the hub wheel and the outer joint member are plastically coupled and integrated. Manufacturing method of bearing device. 前記車輪取付フランジにハブボルトを圧入した後に、ブレーキロータ取付面が旋削加工されている請求項１に記載の車輪用軸受装置の製造方法。
The method for manufacturing a wheel bearing device according to claim 1 , wherein after the hub bolt is press-fitted into the wheel mounting flange, the brake rotor mounting surface is turned.
JP2007130614A 2007-05-16 2007-05-16 Manufacturing method of wheel bearing device Expired - Fee Related JP5252834B2 (en)

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