JP2008057713A - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

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JP2008057713A
JP2008057713A JP2006237137A JP2006237137A JP2008057713A JP 2008057713 A JP2008057713 A JP 2008057713A JP 2006237137 A JP2006237137 A JP 2006237137A JP 2006237137 A JP2006237137 A JP 2006237137A JP 2008057713 A JP2008057713 A JP 2008057713A
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Prior art keywords
wheel
mounting flange
diameter
rolling
hub
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Japanese (ja)
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Kazuo Komori
和雄 小森
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2006237137A priority Critical patent/JP2008057713A/en
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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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
    • F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
    • F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
    • F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
    • F16C19/386—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings 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
    • 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a wheel bearing device which is highly rigid as well as made light/compact while improving the life of a bearing. <P>SOLUTION: A pitch circle diameter PCDi of a ball group 4 located far from a wheel mounting flange 7, out of double row ball groups 3, 4, is set to be larger than a pitch circle diameter PCDo of the ball group 3 located close to the wheel mounting flange 7. A ball diameter di of the ball group 4 located far from the wheel mounting flange 7 is set to be larger than a ball diameter do of the ball group 3 located close to the wheel mounting flange 7, the ball number of the former is set to be more than that of the latter. A mortary recessed portion 14 is formed in the end of a hub ring 5 on the side of the wheel mounting flange 7. The depth of the mortary recessed portion 14 ranges approximately over at least an inside rolling face 5a of the hub ring 5, and the shell of the hub ring 5 is shaped with its thickness approximately uniform corresponding to the recessed portion 14. This solves problems on the device which has a longer life and is lighter/compacter as well as highly rigid. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、自動車等の車輪を回転自在に支承する車輪用軸受装置、特に、軸受寿命を向上させると共に、高剛性化と軽量・コンパクト化を図った車輪用軸受装置に関するものである。   The present invention relates to a wheel bearing device that rotatably supports a wheel of an automobile or the like, and more particularly to a wheel bearing device that improves the bearing life and achieves high rigidity, light weight, and compactness.

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転がり軸受を介して回転自在に支承するもので、駆動輪用と従動輪用とがある。構造上の理由から、駆動輪用では内輪回転方式が、従動輪用では内輪回転と外輪回転の両方式が一般的に採用されている。この車輪用軸受装置には、所望の軸受剛性を有し、ミスアライメントに対しても耐久性を発揮すると共に、燃費向上の観点から回転トルクが小さい複列アンギュラ玉軸受が多用されている。この複列アンギュラ玉軸受は、固定輪と回転輪との間に複数のボールを介在させ、このボールに所定の接触角を付与して固定輪および回転輪に接触させている。   2. Description of the Related Art Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like is such that a hub wheel for mounting a wheel is rotatably supported via a rolling bearing, and there are a drive wheel and a driven wheel. For structural reasons, an inner ring rotation method is generally used for driving wheels, and an inner ring rotation method and an outer ring rotation method are generally used for driven wheels. As the wheel bearing device, a double-row angular ball bearing having a desired bearing rigidity, exhibiting durability against misalignment, and having a small rotational torque from the viewpoint of improving fuel efficiency is often used. In this double row angular contact ball bearing, a plurality of balls are interposed between a fixed ring and a rotating ring, and a predetermined contact angle is given to the balls so as to contact the fixed ring and the rotating ring.

また、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。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。   Further, the 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. Second generation structure in which body mounting flange or wheel mounting flange is formed directly on the outer periphery of the member, third generation structure in which one inner rolling surface is directly formed on the outer periphery of the hub wheel, or hub wheel, etc. 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 speed universal joint. 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).

こうした複列の転がり軸受で構成された車輪用軸受装置において、従来は左右両列の軸受が同一仕様のため、静止時には充分な剛性を有するが、車両の旋回時には必ずしも最適な剛性が得られていない。すなわち、静止時の車重は複列の転がり軸受の略中央に作用するように車輪との位置関係が決められているが、旋回時には、旋回方向の反対側（右旋回の場合は車両の左側）の車軸に、より大きなラジアル荷重やアキシアル荷重が負荷される。したがって、旋回時には、インナー側の軸受列よりもアウター側の軸受列の剛性を高めることが有効とされている。そこで、装置を大型化させることなく高剛性化を図った車輪用軸受装置として、図５に示すものが知られている。   In such a wheel bearing device composed of double-row rolling bearings, the left and right rows of bearings have the same specifications so far. Absent. That is, the position of the vehicle weight when stationary is determined so that it acts on the approximate center of the double row rolling bearing, but when turning, the opposite side of the turning direction (when turning right, the vehicle Larger radial load or axial load is applied to the left axle. Therefore, at the time of turning, it is effective to increase the rigidity of the outer bearing row rather than the inner bearing row. Then, what is shown in FIG. 5 is known as a bearing device for wheels which achieved high rigidity without enlarging an apparatus.

この車輪用軸受装置５０は、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５１ｃを一体に有し、内周に複列の外側転走面５１ａ、５１ｂが形成された外方部材５１と、一端部に車輪（図示せず）を取り付けるための車輪取付フランジ５３を一体に有し、外周に複列の外側転走面５１ａ、５１ｂに対向する一方の内側転走面５２ａと、この内側転走面５２ａから軸方向に延びる小径段部５２ｂが形成されたハブ輪５２、およびこのハブ輪５２の小径段部５２ｂに外嵌され、複列の外側転走面５１ａ、５１ｂに対向する他方の内側転走面５４ａが形成された内輪５４からなる内方部材５５と、これら両転走面間に収容された複列のボール５６、５７と、これら複列のボール５６、５７を転動自在に保持する保持器５８、５９とを備えた複列アンギュラ玉軸受で構成されている。   This wheel bearing device 50 has a vehicle body mounting flange 51c integrally attached to a knuckle (not shown) on the outer periphery, and an outer side in which double row outer rolling surfaces 51a and 51b are formed on the inner periphery. A member 51 and a wheel mounting flange 53 for mounting a wheel (not shown) at one end are integrally formed, and one inner rolling surface 52a facing the double row outer rolling surfaces 51a and 51b on the outer periphery. The hub wheel 52 formed with a small diameter step portion 52b extending in the axial direction from the inner rolling surface 52a and the small diameter step portion 52b of the hub wheel 52 are externally fitted to the double row outer rolling surface 51a, 51b. An inner member 55 composed of an inner ring 54 formed with the other inner rolling surface 54a facing each other, double rows of balls 56, 57 accommodated between both rolling surfaces, and these double rows of balls 56, 57 A retainer 58 for freely rolling It is composed of a double row angular contact ball bearing with a 9.

内輪５４は、ハブ輪５２の小径段部５２ｂを径方向外方に塑性変形させて形成した加締部５２ｃによって軸方向に固定されている。そして、外方部材５１と内方部材５５との間に形成される環状空間の開口部にシール６０、６１が装着され、軸受内部に封入された潤滑グリースの漏洩と、外部から軸受内部に雨水やダスト等が侵入するのを防止している。   The inner ring 54 is fixed in the axial direction by a caulking portion 52c formed by plastically deforming a small diameter step portion 52b of the hub wheel 52 radially outward. Seals 60 and 61 are attached to the opening of the annular space formed between the outer member 51 and the inner member 55, leakage of the lubricating grease sealed inside the bearing, and rainwater from the outside into the bearing. And dust are prevented from entering.

ここで、アウター側のボール５６のピッチ円直径Ｄ１が、インナー側のボール５７のピッチ円直径Ｄ２よりも大径に設定されている。これに伴い、ハブ輪５２の内側転走面５２ａが内輪５４の内側転走面５４ａよりも拡径され、あわせて外方部材５１のアウター側の外側転走面５１ａがインナー側の外側転走面５１ｂよりも拡径されている。そして、アウター側のボール５６がインナー側のボール５７よりも多数収容されている。このように、各ピッチ円直径Ｄ１、Ｄ２をＤ１＞Ｄ２に設定することにより、車両の静止時だけでなく旋回時においても剛性が向上し、車輪用軸受装置５０の長寿命化を図ることができる。
特開２００４−１０８４４９号公報 Here, the pitch circle diameter D1 of the outer side ball 56 is set to be larger than the pitch circle diameter D2 of the inner side ball 57. Along with this, the inner rolling surface 52a of the hub wheel 52 is expanded in diameter than the inner rolling surface 54a of the inner ring 54, and the outer rolling surface 51a on the outer side of the outer member 51 is also rolled on the inner side. The diameter is larger than that of the surface 51b. The outer side balls 56 are accommodated more than the inner side balls 57. As described above, by setting the pitch circle diameters D1 and D2 to D1> D2, the rigidity is improved not only when the vehicle is stationary but also when turning, and the life of the wheel bearing device 50 can be extended. it can.
JP 2004-108449 A

こうした従来の車輪用軸受装置５０では、アウター側のボール５６のピッチ円直径Ｄ１が、インナー側のボール５７のピッチ円直径Ｄ２よりも大径に設定されると共に、アウター側のボール５６がインナー側のボール５７よりも多数収容されているので、アウター側のボール５６列における剛性を増大させることができる。然しながら、その反面、アウター側に対してインナー側のボール５７列における軸受寿命がアウター側ボール５６列に対して不利になるため、軸受寿命を向上させ、また剛性を増大させるかが課題となっていた。   In such a conventional wheel bearing device 50, the pitch circle diameter D1 of the outer-side ball 56 is set to be larger than the pitch circle diameter D2 of the inner-side ball 57, and the outer-side ball 56 is Therefore, the rigidity of the outer side balls 56 row can be increased. However, on the other hand, the bearing life of the inner side ball 57 row with respect to the outer side is disadvantageous with respect to the outer side ball 56 row, so it is a problem to improve the bearing life and increase the rigidity. It was.

本発明は、このような事情に鑑みてなされたもので、軸受寿命を向上させると共に、高剛性化と軽量・コンパクト化を図った車輪用軸受装置を提供することを目的としている。   The present invention has been made in view of such circumstances, and an object of the present invention is to provide a wheel bearing device that improves the bearing life and achieves high rigidity, light weight, and compactness.

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、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軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入された内輪からなり、前記ハブ輪および／または前記内輪の外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体群とを備えた車輪用軸受装置において、前記複列の転動体群のうち前記車輪取付フランジに遠い側の転動体群のピッチ円直径が、前記車輪取付フランジに近い側の転動体群のピッチ円直径よりも大径に設定されると共に、前記車輪取付フランジに遠い側の転動体群の転動体サイズが、前記車輪取付フランジに近い側の転動体群の転動体サイズよりも大きく、かつ、その転動体の個数が多く設定されている。   In order to achieve the object, the invention according to claim 1 of the present invention includes an outer member having a double row outer rolling surface formed on the inner periphery, and a wheel mounting flange for mounting the wheel at one end. The hub wheel and / or the outer periphery of the inner ring, comprising a hub wheel integrally formed and formed with a small diameter stepped portion extending in the axial direction from the wheel mounting flange, and an inner ring press-fitted into the small diameter stepped portion of the hub wheel. An inner member formed with a double-row inner rolling surface opposite to the double-row outer rolling surface, and is accommodated in a freely rollable manner between both rolling surfaces of the inner member and the outer member. In the wheel bearing device comprising the double row rolling element group, the pitch circle diameter of the rolling element group on the side farther from the wheel mounting flange in the double row rolling element group is closer to the wheel mounting flange. The rolling element group is set to a diameter larger than the pitch circle diameter of the rolling element group, Rolling element size of the rolling element groups distant the mounting flange side is the greater than the rolling element size of the rolling element groups closer to the wheel mounting flange, and the number of the rolling elements is often set.

このように、複列の転がり軸受からなる車輪用軸受装置において、複列の転動体群のうち車輪取付フランジに遠い側の転動体群のピッチ円直径が、車輪取付フランジに近い側の転動体群のピッチ円直径よりも大径に設定されると共に、車輪取付フランジに遠い側の転動体群の転動体サイズが、車輪取付フランジに近い側の転動体群の転動体サイズよりも大きく、かつ、その転動体の個数が多く設定されているので、軸受スペースを有効に活用して装置の軽量・コンパクト化を図ると共に、アウター側の軸受列に比べ、インナー側軸受列の長寿命化を図ることができると共に、軸受剛性を増大させることができる。   Thus, in the wheel bearing device including the double row rolling bearings, the pitch circle diameter of the rolling element group on the side farther from the wheel mounting flange in the double row rolling element group is closer to the wheel mounting flange. And the rolling element size of the rolling element group on the side farther from the wheel mounting flange is larger than the rolling element size of the rolling element group on the side close to the wheel mounting flange, and Since the number of rolling elements is set to be large, the bearing space is effectively utilized to reduce the weight and size of the device, and the inner side bearing row has a longer life than the outer side bearing row. And the bearing stiffness can be increased.

また、請求項２に記載の発明のように、前記転動体がボールであっても良いし、また、請求項３に記載の発明のように、前記転動体が円錐ころからなり、前記車輪取付フランジに遠い側の円錐ころ群のころ直径が、前記車輪取付フランジに近い側の円錐ころ群のころ直径よりも大きく設定されていても良い。   Further, as in the invention described in claim 2, the rolling element may be a ball, and as in the invention described in claim 3, the rolling element is formed of a tapered roller, and the wheel mounting The roller diameter of the tapered roller group on the side farther from the flange may be set larger than the roller diameter of the tapered roller group on the side closer to the wheel mounting flange.

また、請求項４に記載の発明のように、前記ハブ輪における内側転走面の大径側には前記円錐ころを案内するための大鍔が形成されておらず、前記外方部材における外側転走面の大径側に当該大鍔が形成されていれば、ハブ輪の鍛造および切削加工が容易となるだけでなく、ハブ輪に発生する応力集中を緩和することができ、強度・耐久性を向上させることができる。   Further, as in the invention according to claim 4, a large collar for guiding the tapered roller is not formed on the large diameter side of the inner rolling surface of the hub wheel, and the outer side of the outer member is not formed. If the large ridge is formed on the large diameter side of the rolling surface, not only can the hub ring be forged and cut, but also the stress concentration generated on the hub ring can be reduced, and the strength and durability can be reduced. Can be improved.

また、請求項５に記載の発明のように、前記内方部材が、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状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、およびこのハブ輪の小径段部に圧入され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された内輪で構成され、前記ハブ輪の前記車輪取付フランジ側の端部にすり鉢状の凹所が形成され、この凹所の深さが少なくとも前記ハブ輪の軸状部付近とされ、前記ハブ輪の外郭形状が当該凹所に対応して略均一な肉厚となるように形成されていれば、装置の軽量・コンパクト化と高剛性化という相反する課題を解決することができる。   Further, as in the invention described in claim 5, the inner member has one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a shaft-shaped portion from the inner rolling surface. Through which a small-diameter step portion extending in the axial direction is formed, and the other inner rolling surface which is press-fitted into the small-diameter step portion of the hub wheel and faces the double-row outer rolling surface is formed on the outer periphery. A mortar-shaped recess is formed at an end of the hub wheel on the wheel mounting flange side, and the depth of the recess is at least near the shaft-shaped portion of the hub wheel. If the outer shape of the device is formed so as to have a substantially uniform thickness corresponding to the recess, the conflicting problems of the light weight, compactness, and high rigidity of the device can be solved.

本発明に係る車輪用軸受装置は、内周に複列の外側転走面が形成された外方部材と、一端部に車輪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軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入された内輪からなり、前記ハブ輪および／または前記内輪の外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体群とを備えた車輪用軸受装置において、前記複列の転動体群のうち前記車輪取付フランジに遠い側の転動体群のピッチ円直径が、前記車輪取付フランジに近い側の転動体群のピッチ円直径よりも大径に設定されると共に、前記車輪取付フランジに遠い側の転動体群の転動体サイズが、前記車輪取付フランジに近い側の転動体群の転動体サイズよりも大きく、かつ、その転動体の個数が多く設定されているので、軸受スペースを有効に活用して装置の軽量・コンパクト化を図ると共に、アウター側の軸受列に比べ、インナー側軸受列の長寿命化を図ることができると共に、軸受剛性を増大させることができる。   The wheel bearing device according to the present invention integrally includes an outer member having a double-row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting the wheel at one end. A hub ring formed with a small-diameter step portion extending in the axial direction from the inner ring and an inner ring press-fitted into the small-diameter step portion of the hub ring, and the outer rolling surface of the double row on the outer periphery of the hub ring and / or the inner ring An inner member in which a double-row inner rolling surface facing the inner member is formed, and a double-row rolling element group that is slidably accommodated between the inner member and the outer member. In the wheel bearing device provided, the pitch circle diameter of the rolling element group on the side farther from the wheel mounting flange in the double row rolling element group is greater than the pitch circle diameter of the rolling element group on the side closer to the wheel mounting flange. Is set to a large diameter, and the wheel on the far side of the wheel mounting flange is Since the rolling element size of the body group is larger than the rolling element size of the rolling element group on the side close to the wheel mounting flange, and the number of rolling elements is set larger, the bearing space is effectively utilized. The device can be reduced in weight and size, and the life of the inner side bearing row can be increased as compared with the outer side bearing row, and the bearing rigidity can be increased.

外周にナックルに取り付けられるための車体取付フランジを一体に有し、内周に複列の外側転走面が形成された外方部材と、一端部に車輪を取り付けるための車輪取付フランジを一体に有し、外周に前記複列の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小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に転動自在に収容された複列のボール群とを備えた車輪用軸受装置において、前記複列のボール群のうち前記車輪取付フランジに遠い側のボール群のピッチ円直径が、前記車輪取付フランジに近い側のボール群のピッチ円直径よりも大径に設定され、前記車輪取付フランジに遠い側のボール群のボール直径が、前記車輪取付フランジに近い側のボール群のボール直径よりも大きく、かつ、そのボール個数が多く設定されると共に、前記ハブ輪の前記車輪取付フランジ側の端部にすり鉢状の凹所が形成され、この凹所の深さが少なくとも前記ハブ輪の内側転走面を越える付近とされ、前記ハブ輪の外郭形状が当該凹所に対応して略均一な肉厚となるように形成されている。   A body mounting flange for mounting to the knuckle on the outer periphery is integrated, an outer member with a double row outer raceway formed on the inner periphery, and a wheel mounting flange for mounting the wheel on one end is integrated. A hub wheel having one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, a small diameter step portion extending in the axial direction from the inner rolling surface, and a small diameter of the hub wheel An inner member consisting of an inner ring that is press-fitted into a stepped portion and has the other inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and both rolling of the inner member and the outer member In a wheel bearing device comprising a double row ball group accommodated so as to roll freely between surfaces, the pitch circle diameter of the ball group farther from the wheel mounting flange in the double row ball group, Larger than the pitch circle diameter of the ball group near the wheel mounting flange And the diameter of the ball group on the side far from the wheel mounting flange is larger than the diameter of the ball group on the side close to the wheel mounting flange, and the number of balls is set larger, and the hub wheel A mortar-shaped recess is formed at an end of the wheel mounting flange side of the wheel, and the depth of the recess is at least near the inner rolling surface of the hub wheel, and the outer shape of the hub wheel is the recess. It is formed so as to have a substantially uniform thickness corresponding to the location.

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。
この車輪用軸受装置は第３世代と呼称される従動輪用であって、内方部材１と外方部材２、および両部材１、２間に転動自在に収容された複列のボール３、４群を備えている。内方部材１は、ハブ輪５と、このハブ輪５に所定のシメシロを介して圧入された内輪６とからなる。 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.
This wheel bearing device is for a driven wheel called a third generation, and includes an inner member 1 and an outer member 2, and a double row of balls 3 accommodated between the members 1 and 2 so as to roll freely. 4 groups. The inner member 1 includes a hub ring 5 and an inner ring 6 press-fitted into the hub ring 5 through a predetermined shimiro.

ハブ輪５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、外周に一方（アウター側）の内側転走面５ａと、この内側転走面５ａから軸方向に延びる軸状部８を介して小径段部５ｂが形成されている。車輪取付フランジ７にはハブボルト７ａが周方向等配に植設されると共に、これらハブボルト７ａ間には円孔７ｂが形成されている。この円孔７ｂは軽量化に寄与できるだけでなく、装置の組立・分解工程において、レンチ等の締結治具をこの円孔７ｂから挿入することができ作業を簡便化することができる。   The hub wheel 5 integrally has a wheel mounting flange 7 for attaching a wheel (not shown) to an end portion on the outer side, one (outer side) inner rolling surface 5a on the outer periphery, and this inner rolling. A small-diameter step portion 5b is formed through an axial portion 8 extending in the axial direction from the surface 5a. Hub bolts 7a are planted on the wheel mounting flange 7 in a circumferentially uniform manner, and circular holes 7b are formed between the hub bolts 7a. The circular hole 7b not only contributes to weight reduction, but also a fastening jig such as a wrench can be inserted from the circular hole 7b in the assembly / disassembly process of the apparatus, and the work can be simplified.

内輪６は、外周に他方（インナー側）の内側転走面６ａが形成され、ハブ輪５の小径段部５ｂに肩部８ａと突合せ状態で圧入され、背面合せタイプの複列アンギュラ玉軸受を構成している。そして、小径段部５ｂの端部を塑性変形（揺動加締）させて形成した加締部５ｃによって内輪６が軸方向に所定の軸受予圧が付与された状態で固定されている。なお、内輪６およびボール３、４はＳＵＪ２等の高炭素クロム鋼で形成され、ズブ焼入れによって芯部まで５８〜６４ＨＲＣの範囲に硬化処理されている。   The inner ring 6 is formed with the other (inner side) inner rolling surface 6a on the outer periphery, and is press-fitted into the small-diameter step portion 5b of the hub wheel 5 in a state of abutting with the shoulder portion 8a. It is composed. The inner ring 6 is fixed in a state where a predetermined bearing preload is applied in the axial direction by a caulking portion 5c formed by plastic deformation (oscillation caulking) of an end portion of the small diameter step portion 5b. The inner ring 6 and the balls 3 and 4 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core part by quenching.

ハブ輪５はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、内側転走面５ａをはじめ、車輪取付フランジ７のインナー側の基部７ｃから小径段部５ｂに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。なお、加締部５ｃは鍛造加工後の表面硬さのままとされている。これにより、車輪取付フランジ７に負荷される回転曲げ荷重に対して充分な機械的強度を有し、内輪６の嵌合部となる小径段部５ｂの耐フレッティング性が向上すると共に、微小なクラック等の発生がなく加締部５ｃの塑性加工をスムーズに行うことができる。   The hub wheel 5 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the inner raceway surface 5a and the base portion 7c on the inner side of the wheel mounting flange 7 to the small diameter step portion 5b. Thus, the surface hardness is set to a range of 58 to 64 HRC by induction hardening. The caulking portion 5c is kept in the surface hardness after forging. Thereby, it has sufficient mechanical strength with respect to the rotational bending load applied to the wheel mounting flange 7, the fretting resistance of the small-diameter step portion 5b serving as the fitting portion of the inner ring 6 is improved, and the minute There is no occurrence of cracks and the like, and the plastic working of the caulking portion 5c can be performed smoothly.

外方部材２は、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２ｃを一体に有し、内周にハブ輪５の内側転走面５ａに対向するアウター側の外側転走面２ａと、内輪６の内側転走面６ａに対向するインナー側の外側転走面２ｂが一体に形成されている。これら両転走面間に複列のボール３、４群が収容され、保持器９、１０によって転動自在に保持されている。   The outer member 2 integrally has a vehicle body mounting flange 2c to be attached to a knuckle (not shown) on the outer periphery, and the outer side outer rolling facing the inner rolling surface 5a of the hub wheel 5 on the inner circumference. The surface 2a and the inner side outer rolling surface 2b facing the inner rolling surface 6a of the inner ring 6 are integrally formed. A double row of balls 3 and 4 is accommodated between these rolling surfaces, and is held by the cages 9 and 10 so as to roll freely.

この外方部材２はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、複列の外側転走面２ａ、２ｂが高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。そして、外方部材２と内方部材１との間に形成される環状空間の開口部にはシール１１、１２が装着され、軸受内部に封入されたグリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   This outer member 2 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the double row outer rolling surfaces 2a and 2b have a surface hardness in the range of 58 to 64HRC by induction hardening. Has been cured. Seals 11 and 12 are attached to the opening of the annular space formed between the outer member 2 and the inner member 1, and leakage of grease sealed inside the bearing and rainwater from the outside. And dust are prevented from entering the bearing.

本実施形態では、内輪６が肉厚に形成され、インナー側のボール４群のピッチ円直径ＰＣＤｉがアウター側のボール３群のピッチ円直径ＰＣＤｏよりも大径に設定されている。これにより、内輪６自体の剛性を高め、揺動加締により内輪６に発生するフープ応力を抑えて耐久性を向上させることができる。また、各ピッチ円直径ＰＣＤｉ、ＰＣＤｏの違いに伴い、インナー側のボール４群におけるボール個数がアウター側のボール３群におけるボール個数よりも多く設定されると共に、インナー側のボール４群におけるボール直径ｄｉがアウター側のボール３群におけるボール直径ｄｏよりも大径に設定されている。このように、各ピッチ円直径ＰＣＤｏ、ＰＣＤｉがＰＣＤｉ＞ＰＣＤｏに設定されると共に、インナー側のボール４群におけるボール個数がアウター側のボール３群におけるボール個数よりも多く設定され、さらに、インナー側のボール４群におけるボール直径ｄｉがアウター側のボール３群におけるボール直径ｄｏよりも大径に設定されているので、インナー側のボール４群における長寿命化と共に車輪軸受装置の高剛性化を図ることができる。   In this embodiment, the inner ring 6 is formed thick, and the pitch circle diameter PCDi of the inner side balls 4 group is set larger than the pitch circle diameter PCDo of the outer side balls 3 group. As a result, the rigidity of the inner ring 6 itself can be increased, and the hoop stress generated in the inner ring 6 by swinging caulking can be suppressed to improve the durability. Further, along with the difference between the pitch circle diameters PCDi and PCDo, the number of balls in the inner side ball 4 group is set larger than the number of balls in the outer side ball 3 group, and the ball diameter in the inner side ball 4 group is set. di is set larger than the ball diameter do in the group 3 of balls on the outer side. Thus, each pitch circle diameter PCDo, PCDi is set to PCDi> PCDo, the number of balls in the inner side ball 4 group is set larger than the number of balls in the outer side ball 3 group, and the inner side Since the ball diameter di of the ball 4 group is set larger than the ball diameter do of the outer side ball 3 group, the life of the inner side ball 4 group is increased and the rigidity of the wheel bearing device is increased. be able to.

ハブ輪５の外郭形状は、内側転走面５ａの溝底部からカウンタ部１３と、このカウンタ部１３から軸方向に延びる軸状部８および内輪６が突き合わされる肩部８ａを介して小径段部５ｂに続いている。また、ハブ輪５のアウター側の端部にはすり鉢状の凹所１４が形成されている。この凹所１４の深さは内側転走面５ａの溝底部を越えて軸状部８付近までの深さとされ、ハブ輪５のアウター側の端部が略均一な肉厚に形成されている。   The outer shape of the hub wheel 5 is a small diameter step through a counter part 13 from the groove bottom part of the inner rolling surface 5a, a shaft part 8 extending in the axial direction from the counter part 13 and a shoulder part 8a against which the inner ring 6 is abutted. It continues to part 5b. A mortar-shaped recess 14 is formed at the outer end of the hub wheel 5. The depth of the recess 14 is a depth that extends beyond the groove bottom portion of the inner rolling surface 5a to the vicinity of the shaft-shaped portion 8, and the outer end portion of the hub wheel 5 is formed to have a substantially uniform thickness. .

一方、外方部材２において、ピッチ円直径ＰＣＤｏ、ＰＣＤｉの違いに伴い、インナー側の外側転走面２ｂがアウター側の外側転走面２ａよりも拡径して形成され、アウター側の外側転走面２ａから円筒状の小径側肩部１５と円弧状に形成された段部１５ａを介して円筒状の大径側肩部１６に続き、インナー側の外側転走面２ｂに到っている。そして、この外側転走面２ｂの溝底径と大径側の肩部１５の内径が略同一径になるように形成されている。   On the other hand, in the outer member 2, the outer side rolling surface 2 b on the inner side is formed with a larger diameter than the outer side rolling surface 2 a on the outer side in accordance with the difference between the pitch circle diameters PCDo and PCDi. From the running surface 2a through the cylindrical small-diameter shoulder 15 and the step portion 15a formed in an arc shape, the cylindrical large-diameter shoulder 16 continues to the inner-side outer rolling surface 2b. . And it forms so that the groove bottom diameter of this outer side rolling surface 2b and the internal diameter of the shoulder part 15 of a large diameter side may become substantially the same diameter.

こうした構成の車輪用軸受装置では、インナー側のボール４群のピッチ円直径ＰＣＤｉがアウター側のボール３群のピッチ円直径ＰＣＤｏよりも大径に形成され、その分、ボール３、４群のボール個数もインナー側のボール４群におけるボール個数がアウター側のボール３群におけるボール個数よりも多く設定されると共に、インナー側のボール４群のボール直径ｄｉがアウター側のボール３群のボール直径ｄｏよりも大径に設定されているため、軸受スペースを有効に活用して装置の軽量・コンパクト化を図ると共に、アウター側の軸受列に比べ、インナー側軸受列の長寿命化を図ることができると共に、軸受剛性を増大させることができる。さらに、ハブ輪５のアウター側端部に凹所１４が外郭形状に沿って形成され、ハブ輪５のアウター側の端部が均一な肉厚に設定されているので、装置の軽量・コンパクト化と高剛性化という相反する課題を解決することができる。   In the wheel bearing device having such a configuration, the pitch circle diameter PCDi of the inner four balls is formed larger than the pitch circle diameter PCDo of the outer three balls. The number of balls in the inner side balls 4 group is set larger than the number of balls in the outer side balls 3 group, and the ball diameter di of the inner side balls 4 group is equal to the ball diameter do of the outer side balls 3 group. Since the diameter is set larger than that of the bearing, the bearing space can be effectively utilized to reduce the weight and size of the device, and the inner side bearing row can have a longer life than the outer side bearing row. At the same time, the bearing rigidity can be increased. Furthermore, since the recess 14 is formed along the outer shape at the outer end of the hub wheel 5 and the outer end of the hub wheel 5 is set to a uniform thickness, the device is lighter and more compact. And the conflicting problem of high rigidity can be solved.

図２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。この実施形態は、前述した第１の実施形態と基本的にはインナー側の軸受列の構成が異なるだけで、その他前述した実施形態と同一部品同一部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。   FIG. 2 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention. This embodiment is basically the same as the first embodiment described above, except for the configuration of the inner side bearing row, and is the same as the parts or portions having the same parts or the same functions as the above-described embodiments. Reference numerals are assigned and detailed description is omitted.

この車輪用軸受装置は第３世代と呼称される従動輪用であって、内方部材１７と外方部材２、および両部材１７、２間に転動自在に収容された複列のボール３、４群を備えている。内方部材１７は、ハブ輪１８と、このハブ輪１８に所定のシメシロを介して圧入された内輪１９とからなる。   This wheel bearing device is for a driven wheel called a third generation, and is an inner member 17, an outer member 2, and a double row of balls 3 accommodated in a freely rolling manner between both members 17, 2. 4 groups. The inner member 17 includes a hub ring 18 and an inner ring 19 that is press-fitted into the hub ring 18 through a predetermined shimiro.

ハブ輪１８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、外周に一方（アウター側）の内側転走面５ａと、この内側転走面５ａから軸方向に延びる軸状部８を介して小径段部１８ａが形成されている。このハブ輪１８はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、内側転走面５ａをはじめ、車輪取付フランジ７のインナー側の基部７ｃから小径段部１８ａに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。   The hub wheel 18 integrally has a wheel mounting flange 7 at an end on the outer side, one (outer side) inner rolling surface 5a on the outer periphery, and an axial portion extending in the axial direction from the inner rolling surface 5a. A small-diameter step portion 18 a is formed through 8. The hub wheel 18 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and includes the inner rolling surface 5a and the base portion 7c on the inner side of the wheel mounting flange 7 to the small diameter step portion 18a. As a result, the surface hardness is set to a range of 58 to 64 HRC by induction hardening.

内輪１９は、外周に他方（インナー側）の内側転走面６ａが形成され、ハブ輪１８の小径段部１８ａに肩部８ａと突合せ状態で圧入され、背面合せタイプの複列アンギュラ玉軸受を構成している。そして、小径段部１８ａの端部を塑性変形（揺動加締）させて形成した加締部５ｃによって内輪１９が軸方向に所定の軸受予圧が付与された状態で固定されている。なお、内輪１９はＳＵＪ２等の高炭素クロム鋼で形成され、ズブ焼入れによって芯部まで５８〜６４ＨＲＣの範囲に硬化処理されている。   The inner ring 19 is formed with the other (inner side) inner rolling surface 6a on the outer periphery, and is press-fitted into the small-diameter step portion 18a of the hub ring 18 in abutment with the shoulder portion 8a. It is composed. The inner ring 19 is fixed in a state where a predetermined bearing preload is applied in the axial direction by a crimped portion 5c formed by plastic deformation (oscillating crimping) of an end portion of the small-diameter stepped portion 18a. The inner ring 19 is made of high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core portion by quenching.

本実施形態では、ハブ輪１８の小径段部１８ａが前述した第１の実施形態のものより大径に形成され、この小径段部１８ａに大径の内輪１９が圧入固定されることにより、インナー側のボール４群のピッチ円直径ＰＣＤｉがアウター側のボール３群のピッチ円直径ＰＣＤｏよりも大径に設定されている。これにより、ハブ輪１８の小径段部１８ａの強度・剛性を高めて耐久性を向上させることができる。   In this embodiment, the small-diameter step portion 18a of the hub wheel 18 is formed to have a larger diameter than that of the first embodiment described above, and the large-diameter inner ring 19 is press-fitted and fixed to the small-diameter step portion 18a. The pitch circle diameter PCDi of the side balls 4 group is set larger than the pitch circle diameter PCDo of the outer balls 3 group. Thereby, the strength and rigidity of the small-diameter step portion 18a of the hub wheel 18 can be increased, and the durability can be improved.

図３は、本発明に係る車輪用軸受装置の第３の実施形態を示す縦断面図である。なお、前述した実施形態と同一部品同一部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。   FIG. 3 is a longitudinal sectional view showing a third embodiment of the wheel bearing device according to the present invention. In addition, the same code | symbol is attached | subjected to the components and site | parts which have the same components same site | part or the same function as embodiment mentioned above, and detailed description is abbreviate | omitted.

この車輪用軸受装置は第３世代と呼称される従動輪用であって、内方部材２０と外方部材２１、および両部材２０、２１間に転動自在に収容された複列円錐ころ２２、２３群を備えている。内方部材２０は、ハブ輪２４と、このハブ輪２４に所定のシメシロを介して圧入された内輪２５とからなる。   This wheel bearing device is for a driven wheel called the third generation, and includes an inner member 20, an outer member 21, and a double row tapered roller 22 accommodated in a freely rolling manner between both members 20, 21. , 23 groups. The inner member 20 includes a hub ring 24 and an inner ring 25 press-fitted into the hub ring 24 through a predetermined shimiro.

ハブ輪２４は、一端部に車輪取付フランジ７を一体に有し、外周に一方（アウター側）のテーパ状の内側転走面２４ａと、この内側転走面２４ａから軸方向に延びる軸状部８を介して小径段部５ｂが形成されている。このハブ輪２４における内側転走面２４ａの大径側には円錐ころ２２を案内するための大鍔が形成されておらず、後述する外方部材２１に大鍔２６が形成されている。さらに、内側転走面２４ａの小径側には円錐ころ２２を保持するための小鍔は形成されておらず、円弧状に形成された車輪取付フランジ７のインナー側の基部７ｃから滑らかに内側転走面２４ａが続き、この内側転走面２４ａの小径側から軸方向に延びる軸状部８および肩部８ａを介して小径段部５ｂに到っている。こうした構成を採用することにより、ハブ輪２４の鍛造および切削加工が容易となるだけでなく、ハブ輪２４に発生する応力集中を緩和することができ、強度・耐久性を向上させることができる。   The hub wheel 24 has a wheel mounting flange 7 integrally at one end, one outer (outer side) tapered inner rolling surface 24a on the outer periphery, and an axial portion extending in the axial direction from the inner rolling surface 24a. A small diameter step portion 5 b is formed via 8. A large flange for guiding the tapered roller 22 is not formed on the large diameter side of the inner raceway 24a of the hub wheel 24, and a large flange 26 is formed on the outer member 21 described later. Further, a small flange for holding the tapered roller 22 is not formed on the small diameter side of the inner rolling surface 24a, and the inner rolling is smoothly performed from the base portion 7c on the inner side of the wheel mounting flange 7 formed in an arc shape. The running surface 24a continues, and reaches the small-diameter step portion 5b via the shaft-shaped portion 8 and the shoulder portion 8a extending in the axial direction from the small-diameter side of the inner rolling surface 24a. By adopting such a configuration, not only forging and cutting of the hub wheel 24 can be facilitated, but stress concentration generated in the hub wheel 24 can be reduced, and strength and durability can be improved.

内輪２５の外周には他方（インナー側）のテーパ状の内側転走面２５ａが形成され、この内側転走面２５ａの大径側に円錐ころ２３を案内するための大鍔２５ｂと、小径側に円錐ころ２３の脱落を防止するための小鍔２５ｃがそれぞれ形成されている。そして、この内輪２５はハブ輪２４の小径段部５ｂに所定のシメシロを介して圧入されると共に、この小径段部５ｂの端部を塑性変形させて形成した加締部５ｃによって所定の軸受予圧が付与された状態で軸方向に固定されている。これにより、軽量・コンパクト化を図ると共に、初期に設定した予圧を長期間に亘って維持するセルフリテイン構造を提供することができる。   On the outer periphery of the inner ring 25, the other (inner side) tapered inner rolling surface 25a is formed. A large flange 25b for guiding the tapered roller 23 to the large diameter side of the inner rolling surface 25a, and a small diameter side Further, a small scissors 25c for preventing the tapered rollers 23 from falling off are formed. The inner ring 25 is press-fitted into the small-diameter step portion 5b of the hub wheel 24 through a predetermined shimiro, and a predetermined bearing preload is applied by a caulking portion 5c formed by plastically deforming an end portion of the small-diameter step portion 5b. Is fixed in the axial direction. As a result, it is possible to provide a self-retaining structure that achieves light weight and compactness and that maintains the initially set preload for a long period of time.

外方部材２１は、外周に車体取付フランジ２ｃを一体に有し、内周にハブ輪２４の内側転走面２４ａに対向するアウター側のテーパ状の外側転走面２１ａと、内輪２５の内側転走面２５ａに対向するインナー側のテーパ状の外側転走面２１ｂが一体に形成されている。本実施形態では、アウター側の円錐ころ２２を案内するための大鍔２６がこの外方部材２１に設けられている。すなわち、外方部材２１におけるアウター側の外側転走面２１ａの大径側に円錐ころ２２の大端面に当接してこの円錐ころ２２を案内する大鍔２６が一体に設けられている。これにより、円錐ころ２２を介して負荷される荷重に対してハブ輪２４への応力集中が緩和され、車輪取付フランジ７に大きなモーメント荷重が負荷されてもハブ輪２４に疲労が生じ難く、強度・耐久性を確保することができる。   The outer member 21 integrally has a vehicle body mounting flange 2 c on the outer periphery, and has an outer tapered outer rolling surface 21 a facing the inner rolling surface 24 a of the hub wheel 24 on the inner periphery and an inner side of the inner ring 25. An inner tapered outer rolling surface 21b facing the rolling surface 25a is integrally formed. In this embodiment, the outer member 21 is provided with a large collar 26 for guiding the outer side tapered roller 22. That is, a large collar 26 that abuts on the large end surface of the tapered roller 22 and guides the tapered roller 22 is integrally provided on the outer diameter side of the outer side outer rolling surface 21 a of the outer member 21. As a result, the stress concentration on the hub wheel 24 with respect to the load applied via the tapered roller 22 is alleviated, and even if a large moment load is applied to the wheel mounting flange 7, the hub wheel 24 is not easily fatigued. -Durability can be ensured.

外方部材２１はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、大鍔２６および複列の外側転走面２１ａ、２１ｂが高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。そして、両転走面２１ａ、２４ａおよび２１ｂ、２５ａ間に保持器２７、２８を介して複列の円錐ころ２２、２３群が転動自在にそれぞれ収容されている。また、外方部材２１と内方部材２０との間に形成された環状空間の開口部にはシール１１とスリンガ２９が装着され、軸受内部に封入されたグリースの外部への漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。なお、アウター側のスリンガ２９には磁気エンコーダが一体に接合されている。   The outer member 21 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and the outer surface 21a, 21b of the large punch 26 and the double row has a surface hardness of 58 to 58 by induction hardening. Hardened to a range of 64 HRC. And the double-row tapered rollers 22 and 23 group are accommodated so that rolling is possible between the rolling surfaces 21a, 24a and 21b, 25a via the retainers 27, 28, respectively. Further, a seal 11 and a slinger 29 are attached to the opening of the annular space formed between the outer member 21 and the inner member 20, and leakage of grease sealed inside the bearing to the outside and from the outside. Rain water and dust are prevented from entering the bearing. A magnetic encoder is integrally joined to the outer slinger 29.

また、ハブ輪２４はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、アウター側のシール１１が摺接する車輪取付フランジ７の基部７ｃから内側転走面２４ａ、軸状部８、肩部８ａおよび小径段部５ｂに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理が施されている。また、内輪２５および円錐ころ２２、２３は、ＳＵＪ２等の高炭素クロム鋼で形成され、ズブ焼入れによって芯部まで５８〜６４ＨＲＣの範囲に硬化処理されている。   Further, the hub wheel 24 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and from the base portion 7c of the wheel mounting flange 7 to which the outer seal 11 is in sliding contact, the inner rolling surface 24a, the shaft The surface hardness of the shape portion 8, the shoulder portion 8a, and the small-diameter step portion 5b is subjected to a hardening process within a range of 58 to 64 HRC by induction hardening. Further, the inner ring 25 and the tapered rollers 22 and 23 are made of high carbon chrome steel such as SUJ2, and are hardened in the range of 58 to 64 HRC to the core part by quenching.

本実施形態は、内輪２５が肉厚に形成され、インナー側の円錐ころ２３群のピッチ円直径ＰＣＤｉがアウター側の円錐ころ２２群のピッチ円直径ＰＣＤｏよりも大径に設定されている。これにより、内輪２５自体の剛性を高め、揺動加締により内輪２５に発生するフープ応力と大鍔２５ｂの倒れを抑えて内輪２５の耐久性を向上させることができる。   In this embodiment, the inner ring 25 is formed thick, and the pitch circle diameter PCDi of the inner side tapered roller 23 group is set larger than the pitch circle diameter PCDo of the outer side tapered roller 22 group. As a result, the rigidity of the inner ring 25 itself can be increased, and the durability of the inner ring 25 can be improved by suppressing the hoop stress generated in the inner ring 25 by swinging and caulking and the fall of the large collar 25b.

また、各ピッチ円直径ＰＣＤｉ、ＰＣＤｏの違いに伴い、インナー側の円錐ころ２３群のピッチ円直径ＰＣＤｉがアウター側の円錐ころ２２群のピッチ円直径ＰＣＤｏよりも大径に設定されると共に、インナー側の円錐ころ２３群のころ本数がアウター側の円錐ころ２２群のころ本数がよりも多く設定され、さらに、インナー側の円錐ころ２３群のころ直径Ｄｉが、アウター側の円錐ころ２２群のころ直径Ｄｏよりも大径に設定されている。これにより、転動体に円錐ころ２２、２３を使用して装置の軽量・コンパクト化を図ると共に、重量アップを抑えつつアウター側の軸受列に比べインナー側の軸受列の長寿命化を図ることができると共に、軸受剛性を増大させることができる。   Further, with the difference between the pitch circle diameters PCDi and PCDo, the pitch circle diameter PCDi of the inner side tapered roller group 23 is set to be larger than the pitch circle diameter PCDo of the outer side tapered roller group 22 and The number of rollers in the side tapered roller 23 group is set to be larger than the number of rollers in the outer side tapered roller 22 group, and the roller diameter Di of the inner side tapered roller 23 group is set to be larger than that of the outer side tapered roller 22 group. The diameter is set larger than the roller diameter Do. As a result, the tapered rollers 22 and 23 are used as rolling elements to reduce the weight and size of the device, and to increase the life of the inner side bearing row compared to the outer side bearing row while suppressing an increase in weight. In addition, the bearing rigidity can be increased.

ここで、ハブ輪２４のアウター側の端部にすり鉢状の凹所１４が鍛造加工によって形成されている。この凹所１４の深さは、内側転走面２４ａの小径側付近までとされ、ハブ輪２４のアウター側の端部が略均一な肉厚に形成されている。これにより、装置の軽量・コンパクト化と高剛性化という相反する課題を同時に解決することができる。   Here, a mortar-shaped recess 14 is formed at the outer end of the hub wheel 24 by forging. The depth of the recess 14 extends to the vicinity of the small diameter side of the inner rolling surface 24a, and the outer end of the hub wheel 24 is formed with a substantially uniform thickness. As a result, it is possible to simultaneously solve the conflicting problems of the light weight, compactness, and high rigidity of the apparatus.

図４は、本発明に係る車輪用軸受装置の第４の実施形態を示す縦断面図である。この実施形態は、前述した第３の実施形態と基本的にはインナー側の軸受列の構成が異なるだけで、その他前述した実施形態と同一部品同一部位あるいは同一機能を有する部品や部位には同じ符号を付して詳細な説明を省略する。   FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the wheel bearing device according to the present invention. This embodiment basically differs from the above-described third embodiment only in the configuration of the inner-side bearing row, and is the same as other parts or parts having the same function or the same function as the above-described embodiments. Reference numerals are assigned and detailed description is omitted.

この車輪用軸受装置は第３世代と呼称される従動輪用であって、内方部材３０と外方部材２１、および両部材３０、２１間に転動自在に収容された複列円錐ころ２２、２３群を備えている。内方部材３０は、ハブ輪３１と、このハブ輪３１に所定のシメシロを介して圧入された内輪３２とからなる。   This wheel bearing device is for a driven wheel called a third generation, and includes an inner member 30, an outer member 21, and a double row tapered roller 22 accommodated in a freely rolling manner between both members 30, 21. , 23 groups. The inner member 30 includes a hub ring 31 and an inner ring 32 that is press-fitted into the hub ring 31 via a predetermined shimiro.

ハブ輪３１は、一端部に車輪取付フランジ７を一体に有し、外周に一方（アウター側）のテーパ状の内側転走面２４ａと、この内側転走面２４ａから軸方向に延びる軸状部８を介して小径段部１８ａが形成されている。このハブ輪３１はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、内側転走面２４ａをはじめ、車輪取付フランジ７のインナー側の基部７ｃから小径段部１８ａに亙って高周波焼入れによって表面硬さを５８〜６４ＨＲＣの範囲に硬化処理されている。   The hub wheel 31 has a wheel mounting flange 7 integrally at one end, one (outer side) tapered inner rolling surface 24a on the outer periphery, and an axial portion extending in the axial direction from the inner rolling surface 24a. A small-diameter step portion 18 a is formed through 8. The hub wheel 31 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and includes the inner rolling surface 24a and the base portion 7c on the inner side of the wheel mounting flange 7 to the small diameter step portion 18a. As a result, the surface hardness is set to a range of 58 to 64 HRC by induction hardening.

内輪３２は、外周に他方（インナー側）のテーパ状の内側転走面２５ａが形成され、ハブ輪３１の小径段部１８ａに肩部８ａと突合せ状態で圧入され、背面合せタイプの複列円錐ころ軸受を構成している。なお、内輪３２はＳＵＪ２等の高炭素クロム鋼で形成され、ズブ焼入れによって芯部まで５８〜６４ＨＲＣの範囲に硬化処理されている。   The inner ring 32 is formed with the other (inner side) tapered inner rolling surface 25a on the outer periphery, and is press-fitted into the small-diameter step portion 18a of the hub ring 31 in abutment with the shoulder portion 8a. It constitutes a roller bearing. The inner ring 32 is made of high carbon chrome steel such as SUJ2, and is hardened in the range of 58 to 64 HRC up to the core part by quenching.

本実施形態では、ハブ輪３１の小径段部１８ａが前述した第３の実施形態のものより大径に形成され、この小径段部１８ａに大径の内輪３２が圧入固定されることにより、インナー側のボール４群のピッチ円直径ＰＣＤｉがアウター側のボール３群のピッチ円直径ＰＣＤｏよりも大径に設定されている。これにより、ハブ輪３１の小径段部１８ａの強度・剛性を高めて耐久性を向上させることができる。   In this embodiment, the small-diameter step portion 18a of the hub wheel 31 is formed to have a larger diameter than that of the third embodiment described above, and the inner ring 32 having a large diameter is press-fitted and fixed to the small-diameter step portion 18a. The pitch circle diameter PCDi of the side balls 4 group is set larger than the pitch circle diameter PCDo of the outer balls 3 group. Thereby, the strength and rigidity of the small-diameter step portion 18a of the hub wheel 31 can be increased, and the durability can be improved.

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、従動輪用の第３世代構造の車輪用軸受装置に適用することができる。   The wheel bearing device according to the present invention can be applied to a third-generation wheel bearing device for a driven wheel.

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. 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. 本発明に係る車輪用軸受装置の第３の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 3rd Embodiment of the wheel bearing apparatus which concerns on this invention. 本発明に係る車輪用軸受装置の第４の実施形態を示す縦断面図である。It is a longitudinal cross-sectional view which shows 4th Embodiment of the wheel bearing apparatus which concerns on this invention. 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.

符号の説明Explanation of symbols

１、１７、２０、３０・・・・・内方部材
２、２１・・・・・・・・・・・外方部材
３、４・・・・・・・・・・・・ボール
５、１８・・・・・・・・・・・ハブ輪
５ａ、６ａ、２４ａ、２５ａ・・内側転走面
５ｂ、１８ａ・・・・・・・・・小径段部
５ｃ・・・・・・・・・・・・・加締部
６、１９、２５、３２・・・・・内輪
７・・・・・・・・・・・・・・車輪取付フランジ
７ａ・・・・・・・・・・・・・ハブボルト
７ｂ・・・・・・・・・・・・・円孔
７ｃ・・・・・・・・・・・・・基部
８・・・・・・・・・・・・・・軸状部
８ａ・・・・・・・・・・・・・肩部
９、１０、２７、２８・・・・・保持器
１１、１２・・・・・・・・・・シール
１３・・・・・・・・・・・・・カウンタ部
１４・・・・・・・・・・・・・凹所
１５・・・・・・・・・・・・・小径側肩部
１６・・・・・・・・・・・・・大径側肩部
２２、２３・・・・・・・・・・円錐ころ
２５ｂ、２６・・・・・・・・・大鍔
２５ｃ・・・・・・・・・・・・小鍔
２９・・・・・・・・・・・・・スリンガ
５０・・・・・・・・・・・・・車輪用軸受装置
５１・・・・・・・・・・・・・外方部材
５１ａ・・・・・・・・・・・・アウター側の外側転走面
５１ｂ・・・・・・・・・・・・インナー側の外側転走面
５１ｃ・・・・・・・・・・・・車体取付フランジ
５２・・・・・・・・・・・・・ハブ輪
５２ａ、５４ａ・・・・・・・・内側転走面
５２ｂ・・・・・・・・・・・・小径段部
５２ｃ・・・・・・・・・・・・加締部
５３・・・・・・・・・・・・・車輪取付フランジ
５４・・・・・・・・・・・・・内輪
５５・・・・・・・・・・・・・内方部材
５６、５７・・・・・・・・・・ボール
５８、５９・・・・・・・・・・保持器
６０、６１・・・・・・・・・・シール
Ｄ１・・・・・・・・・・・・・アウター側のボールのピッチ円直径
Ｄ２・・・・・・・・・・・・・インナー側のボールのピッチ円直径
Ｄｉ・・・・・・・・・・・・・インナー側の円錐ころの直径
Ｄｏ・・・・・・・・・・・・・アウター側の円錐ころの直径
ｄｉ・・・・・・・・・・・・・インナー側のボールの直径
ｄｏ・・・・・・・・・・・・・アウター側のボールの直径
Ｌｉ・・・・・・・・・・・・・インナー側の円錐ころの長さ
Ｌｏ・・・・・・・・・・・・・アウター側の円錐ころの長さ
ＰＣＤｉ・・・・・・・・・・・インナー側の転動体のピッチ円直径
ＰＣＤｏ・・・・・・・・・・・アウター側の転動体のピッチ円直径 1, 17, 20, 30... Inner member 2, 21... Outer member 3, 4,. 18 ························ Hub Wheels 5a, 6a, 24a, 25a ... Inside Rolling Surface 5b, 18a ... Small Diameter Step 5c ... ·················································································· 6 ········ Hub bolt 7b ···································································・ Shaft-shaped part 8a ............ Shoulders 9, 10, 27, 28 ... Retainer 11, 12 ......... Seal 13 ··············· counter section 14 ························· 5 ········· Small diameter side shoulder 16 ··········· Large diameter side shoulders 22 and 23 Tapered rollers 25b, 26 ···························································· Slinger 50・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel bearing device 51 ・ ・ ・ ・ ・ ・ ・ ・ External member 51a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer rolling on the outer side Surface 51b ·················· Outer rolling surface 51c on the inner side ...・ Hub wheels 52a, 54a ... Inner rolling surface 52b ... Small diameter step 52c ... Caulking part 53 ... Wheel mounting flange 54 ... .... Inner ring 55 ... Inner members 56, 57 ... Balls 58, 59 ... ··············································································· Pitch circle diameter D2 of the ball on the outer side・ ・ ・ ・ Pitch circle diameter Di of inner side ball ・ ・ ・ ・ ・ ・ ・ ・ Dia of inner roller tapered Do ・ ・ ・ ・ ・ ・ ・ ・ Outer side Tapered roller diameter di ... Inner side ball diameter do ... Outer side ball diameter Li ... ............ Inner side tapered roller length Lo ......... Outer side tapered roller length PCDi ... Rolling on the inner side Pitch circle diameter of the body PCDo ............ Pitch circle diameter of the outer rolling element

Claims (5)

内周に複列の外側転走面が形成された外方部材と、
一端部に車輪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軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に圧入された内輪からなり、前記ハブ輪および／または前記内輪の外周に前記複列の外側転走面に対向する複列の内側転走面が形成された内方部材と、
この内方部材と前記外方部材の両転走面間に転動自在に収容された複列の転動体群とを備えた車輪用軸受装置において、
前記複列の転動体群のうち前記車輪取付フランジに遠い側の転動体群のピッチ円直径が、前記車輪取付フランジに近い側の転動体群のピッチ円直径よりも大径に設定されると共に、前記車輪取付フランジに遠い側の転動体群の転動体サイズが、前記車輪取付フランジに近い側の転動体群の転動体サイズよりも大きく、かつ、その転動体の個数が多く設定されていることを特徴とする車輪用軸受装置。 An outer member having a double row outer raceway formed on the inner periphery;
From a hub ring integrally having a wheel mounting flange for mounting a wheel at one end, a small diameter step portion extending in the axial direction from the wheel mounting flange, and an inner ring press-fitted into the small diameter step portion of the hub ring An inner member in which a double-row inner rolling surface facing the double-row outer rolling surface is formed on the outer periphery of the hub wheel and / or the inner ring,
In the wheel bearing device including the inner member and a double row rolling element group accommodated in a freely rolling manner between both rolling surfaces of the outer member,
In the double row rolling element group, the pitch circle diameter of the rolling element group far from the wheel mounting flange is set to be larger than the pitch circle diameter of the rolling element group near the wheel mounting flange. The rolling element size of the rolling element group on the side far from the wheel mounting flange is larger than the rolling element size of the rolling element group on the side close to the wheel mounting flange, and the number of the rolling elements is set to be large. A wheel bearing device characterized by that. 前記転動体がボールからなる請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein the rolling elements are balls. 前記転動体が円錐ころからなり、前記車輪取付フランジに遠い側の円錐ころ群のころ直径が、前記車輪取付フランジに近い側の円錐ころ群のころ直径よりも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 roller body is composed of a tapered roller, and the roller diameter of the tapered roller group on the side farther from the wheel mounting flange is set larger than the roller diameter of the tapered roller group on the side closer to the wheel mounting flange. The wheel bearing device described. 前記ハブ輪における内側転走面の大径側には前記円錐ころを案内するための大鍔が形成されておらず、前記外方部材における外側転走面の大径側に当該大鍔が形成されている請求項３に記載の車輪用軸受装置。   A large flange for guiding the tapered roller is not formed on the large diameter side of the inner rolling surface of the hub wheel, and the large flange is formed on the large diameter side of the outer rolling surface of the outer member. The wheel bearing device according to claim 3. 前記内方部材が、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状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、およびこのハブ輪の小径段部に圧入され、外周に前記複列の外側転走面に対向する他方の内側転走面が形成された内輪で構成され、前記ハブ輪の前記車輪取付フランジ側の端部にすり鉢状の凹所が形成され、この凹所の深さが少なくとも前記ハブ輪の軸状部付近とされ、前記ハブ輪の外郭形状が当該凹所に対応して略均一な肉厚となるように形成されている請求項１乃至４いずれかに記載の車輪用軸受装置。   The inner member has one inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and a small-diameter step portion extending in the axial direction from the inner rolling surface via the shaft-shaped portion. The wheel mounting of the hub wheel is composed of a hub wheel and an inner ring that is press-fitted into a small-diameter step portion of the hub wheel and has an outer ring formed on the outer periphery thereof that faces the double-row outer rolling surface. A mortar-shaped recess is formed at the end on the flange side, and the depth of the recess is at least near the shaft-shaped portion of the hub wheel, and the outer shape of the hub wheel is substantially uniform corresponding to the recess. The wheel bearing device according to any one of claims 1 to 4, wherein the wheel bearing device is formed to have a large thickness.
JP2006237137A 2006-09-01 2006-09-01 Wheel bearing device Pending JP2008057713A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010005896U1 (en) 2010-04-20 2010-07-29 Nsk Deutschland Gmbh roller bearing
JP2019066027A (en) * 2017-10-05 2019-04-25 日本精工株式会社 Double row roller bearing

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010005896U1 (en) 2010-04-20 2010-07-29 Nsk Deutschland Gmbh roller bearing
JP2019066027A (en) * 2017-10-05 2019-04-25 日本精工株式会社 Double row roller bearing

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