JP2013224718A - Bearing device for wheel - Google Patents

Bearing device for wheel Download PDF

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Publication number
JP2013224718A
JP2013224718A JP2012097833A JP2012097833A JP2013224718A JP 2013224718 A JP2013224718 A JP 2013224718A JP 2012097833 A JP2012097833 A JP 2012097833A JP 2012097833 A JP2012097833 A JP 2012097833A JP 2013224718 A JP2013224718 A JP 2013224718A
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Prior art keywords
wheel
bearing device
seal
cap
deflector
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JP2012097833A
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Japanese (ja)
Inventor
Keisuke Morii
佳祐 森井
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2012097833A priority Critical patent/JP2013224718A/en
Publication of JP2013224718A publication Critical patent/JP2013224718A/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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7869—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward
    • F16C33/7873—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section
    • F16C33/7876—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted with a cylindrical portion to the inner surface of the outer race and having a radial portion extending inward with a single sealing ring of generally L-shaped cross-section with sealing lips
    • 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
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
    • 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
    • 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

PROBLEM TO BE SOLVED: To provide a bearing device for a wheel capable of maintaining bearing performance over a long period of time, by improving sealing performance of a seal.SOLUTION: The bearing device has a cylindrical fitting part 14 for installing a cap 13 on the end part outer periphery of an outer member 2, and a bending part 16 extending radially inside from the one end part and set so that a diameter difference between the inner diameter and an end part inner diameter of the outer member 2 is 0.3 mm or more. A pocket part 17 is arranged on the road surface side of the bending part 16. A bottom part 17a is tapered so as to expand by a predetermined inclination. A gutter part 18 is formed in the axial direction. A distal end part is set so as to open closer to the inner side than a vehicle body installation flange 2b. A step part 19 is formed between a side surface 6c of a wheel installation flange 6 and a base part 6b. The inner edge of the bending part 16 is opposed via a radial gap of 0.3-3.0 mm. A labyrinth 20 is formed.

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、密封性能の向上を図った車輪用軸受装置に関するものである。   The present invention relates to a wheel bearing device for rotatably supporting a wheel of an automobile or the like, and more particularly to a wheel bearing device with improved sealing performance.

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。一方、オフロードカーやトラック等、車体重量が嵩む車両には複列円錐ころ軸受が使用されている。   2. Description of the Related Art Conventionally, a wheel bearing device for supporting a wheel of an automobile or the like 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. On the other hand, double row tapered roller bearings are used in vehicles such as off-road cars and trucks that have a heavy vehicle body weight.

これらの車輪用軸受装置は泥水等がかかり易い部位に配置されるため、シール装置が装着されて外方部材と内方部材との間を密封するように構成されている。一般的に、シール装置は、シールリップを備えたシール部材が固定側部材となる外方部材に装着され、シールリップが内方部材の外周面に摺接されている。   Since these wheel bearing devices are arranged at sites where muddy water or the like is easily applied, a seal device is mounted to seal between the outer member and the inner member. Generally, in a sealing device, a sealing member having a sealing lip is attached to an outer member serving as a stationary member, and the sealing lip is slidably contacted with an outer peripheral surface of the inner member.

こうした車輪用軸受装置における密封装置の一例を図１５に示す。車輪取付フランジ５０の基部５０ａに金属環５１が嵌着され、シール５２は、この金属環５１に摺接するように配設されている。シール５２は、外方部材５３の端部内周に嵌合される芯金５４と、この芯金５４に加硫接着等により一体に接合されたシール部材５５とからなる。   An example of the sealing device in such a wheel bearing device is shown in FIG. A metal ring 51 is fitted on the base 50 a of the wheel mounting flange 50, and the seal 52 is disposed so as to be in sliding contact with the metal ring 51. The seal 52 includes a cored bar 54 fitted to the inner periphery of the end of the outer member 53 and a seal member 55 integrally joined to the cored bar 54 by vulcanization adhesion or the like.

シール部材５５は、芯金５４の外周部に接合され、径方向外方に傾斜して延びる一対のサイドリップ５５ａ、５５ｂと、芯金５４の内縁部に接合され、軸受内方側に傾斜して延びるグリースリップ５５ｃとを有している。   The seal member 55 is joined to the outer peripheral portion of the cored bar 54, joined to a pair of side lips 55a and 55b extending obliquely outward in the radial direction, and the inner edge of the cored bar 54, and tilted to the bearing inward side. And a grease lip 55c extending.

金属環５１は、耐食性を有するオーステナイト系ステンレス鋼板等からプレス加工にて形成され、ハブ輪５６の肩部５６ａに外嵌される円筒状の嵌合部５１ａと、円弧状に形成された基部５０ａに対応して円弧状に形成された湾曲部５１ｂと、この湾曲部５１ｂから径方向外方に延び、車輪取付フランジ５０の側面５０ｂに密着される円板部５１ｃと、この円板部５１ｃの外径部から車輪取付フランジ５０に対して軸方向に離間して延びる円筒状の傘部５１ｄと、この傘部５１ｄから径方向外方に突出して形成された折曲部５１ｅとを備えている。   The metal ring 51 is formed by press working from an austenitic stainless steel plate or the like having corrosion resistance, and a cylindrical fitting portion 51a that is externally fitted to the shoulder portion 56a of the hub wheel 56, and a base portion 50a that is formed in an arc shape. Corresponding to the curved portion 51b, a circular portion 51c extending radially outward from the curved portion 51b and in close contact with the side surface 50b of the wheel mounting flange 50, and the circular portion 51c. A cylindrical umbrella portion 51d extending away from the outer diameter portion in the axial direction with respect to the wheel mounting flange 50, and a bent portion 51e formed to protrude radially outward from the umbrella portion 51d are provided. .

基部５０ａは、ハブ輪５６の肩部５６ａと車輪取付フランジ５０との間の角部に所定の曲率半径ｒからなる円弧面に形成されている。そして、この円弧面に対応して、金属環５１の湾曲部５１ｂは所定の曲率半径Ｒからなる円弧面からなり、それぞれの曲率半径Ｒ、ｒがＲ≧ｒになるように設定されている。これにより、金属環５１を基部５０ａに嵌合した時に基部５０ａの円弧面に金属環５１の湾曲部５１ｂが干渉して浮き上がるのを防止している。   The base portion 50 a is formed in an arc surface having a predetermined radius of curvature r at a corner portion between the shoulder portion 56 a of the hub wheel 56 and the wheel mounting flange 50. Corresponding to this arc surface, the curved portion 51b of the metal ring 51 is formed of an arc surface having a predetermined radius of curvature R, and the respective curvature radii R and r are set such that R ≧ r. This prevents the curved portion 51b of the metal ring 51 from interfering with the circular arc surface of the base portion 50a when the metal ring 51 is fitted to the base portion 50a.

金属環５１の傘部５１ｄは、外方部材５３の端部外周に沿って僅かな環状の隙間Ａを介して対向配置され、ラビリンスが構成されている。この環状の隙間Ａは０．０５〜１．０ｍｍ（直径）の範囲に設定されている。そして、傘部５１ｄの周方向に複数の排水孔５７が穿設されている。   The umbrella portion 51d of the metal ring 51 is disposed so as to face the outer periphery of the outer member 53 through a slight annular gap A, thereby forming a labyrinth. The annular gap A is set in a range of 0.05 to 1.0 mm (diameter). A plurality of drain holes 57 are formed in the circumferential direction of the umbrella portion 51d.

このように、傘部５１ｄの内周面と外方部材５３の外周面とによって形成されたラビリンス効果により、シール５２と金属環５１との摺接部に泥水等が浸入するのを防止することができると共に、この僅かな環状の隙間Ａから金属環５１の内部に泥水等が浸入したとしても、図中矢印にて示すように、金属環５１の回転に伴う遠心力によって排出されると共に、傘部５１ｄに穿設された排水孔５７によって容易に外部に排出され、サイドリップ５５ａ上に滞留することはない。したがって、泥水等がサイドリップ５５ａの摺接面に付着して摩耗するのを防止し、長期間に亘って安定した密封性を保持することができる。   As described above, the labyrinth effect formed by the inner peripheral surface of the umbrella portion 51d and the outer peripheral surface of the outer member 53 prevents muddy water from entering the sliding contact portion between the seal 52 and the metal ring 51. Even if muddy water or the like enters the inside of the metal ring 51 from this slight annular gap A, as shown by the arrow in the figure, it is discharged by the centrifugal force accompanying the rotation of the metal ring 51, The drain hole 57 formed in the umbrella portion 51d is easily discharged to the outside and does not stay on the side lip 55a. Therefore, muddy water or the like can be prevented from adhering to the sliding contact surface of the side lip 55a and worn, and a stable sealing performance can be maintained over a long period of time.

また、車両の停止時、金属環５１の内部に浸入した泥水等は、シール５２のサイドリップ５５ａを伝って下方に流動し、路面に近い傘部５１ｄの下側に穿設された排水孔５７から排出される。   Further, when the vehicle is stopped, the muddy water or the like that has entered the metal ring 51 flows downward through the side lip 55a of the seal 52, and the drain hole 57 formed below the umbrella portion 51d near the road surface. Discharged from.

さらに、外方部材５３の端部外周にキャップ５８が圧入されている。このキャップ５８は金属環５１の端部近傍に圧入される円筒部５８ａと、この円筒部５８ａから径方向外方に延びる立板部５８ｂとからなり、オーステナイト系ステンレス鋼板等からプレス加工にて断面が略Ｌ字状に形成されている。そして、金属環５１の折曲部５１ｅと立板部５８ｂとが僅かな軸方向隙間Ｂを介して対峙し、ラビリンスが構成されている。   Further, a cap 58 is press-fitted into the outer periphery of the end portion of the outer member 53. The cap 58 includes a cylindrical portion 58a press-fitted in the vicinity of the end of the metal ring 51, and a standing plate portion 58b extending radially outward from the cylindrical portion 58a. The cross section is formed by pressing from an austenitic stainless steel plate or the like. Is formed in a substantially L-shape. And the bending part 51e and the standing board part 58b of the metal ring 51 oppose via the slight axial gap B, and the labyrinth is comprised.

これにより、外方部材５３の外周面を伝って浸入してくる泥水等をこのキャップ５８で阻止し、金属環５１の内部に泥水等が浸入するのを防止すると共に、ラビリンスによって、内部に浸入した泥水等が、金属環５１の回転に伴う遠心力によって排出するのを妨げることがないため長期間に亘って安定した密封性を保持することができる（例えば、特許文献１参照。）。   Thus, the muddy water entering the outer peripheral surface of the outer member 53 is blocked by the cap 58, preventing the muddy water from entering the metal ring 51, and entering the inside by the labyrinth. Since the muddy water and the like are not prevented from being discharged by the centrifugal force accompanying the rotation of the metal ring 51, stable sealing performance can be maintained over a long period of time (see, for example, Patent Document 1).

特開２０１０−５３８９３号公報JP 2010-53893 A

こうした従来の車輪用軸受装置のシール装置では、外方部材５３に装着されたシール５２とハブ輪５６との間に金属環５１を配設し、シールリップの摺接面の錆を防止すると共に、さらに、外方部材５３の外周面にキャップ５８を配設し、ハブ輪５６と外方部材５３とのすきまから異物が侵入するのを防止して密封性を高めている。然しながら、このシール構造は、外部からの異物侵入を防ぐことが主目的であり、軸受内部からの潤滑グリース、オイル等が漏れた場合、漏れたグリースあるいはオイル等が遠心力で金属環５１を伝って軸受外部に飛散する可能性がある。この場合、軸受の外方部にはブレーキ部品が配置されており、グリース、オイル等が飛散すれば、ブレーキ性能に影響がでる恐れがある。   In such a conventional sealing device for a wheel bearing device, the metal ring 51 is disposed between the seal 52 mounted on the outer member 53 and the hub wheel 56 to prevent rust on the sliding surface of the seal lip. In addition, a cap 58 is disposed on the outer peripheral surface of the outer member 53 to prevent foreign matter from entering from the gap between the hub wheel 56 and the outer member 53, thereby improving the sealing performance. However, the main purpose of this seal structure is to prevent foreign matter from entering from the outside. When lubricating grease or oil leaks from the inside of the bearing, the leaked grease or oil or the like travels through the metal ring 51 by centrifugal force. May be scattered outside the bearing. In this case, brake parts are arranged on the outer side of the bearing, and if grease, oil, or the like scatters, there is a risk that the brake performance will be affected.

本発明は、このような事情に鑑みてなされたもので、シールの密封性能の向上を図り、軸受性能を長期間に亘って維持することができる車輪用軸受装置を提供することを目的としている。   This invention is made | formed in view of such a situation, and aims at the improvement of the sealing performance of a seal | sticker, and it aims at providing the wheel bearing apparatus which can maintain bearing performance over a long period of time. .

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、外周に車体取付フランジを一体に有し、内周に複列の外側転走面が一体に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所定のシメシロを介して圧入され、外周に前記複列の外側転走面の内側転走面が形成された少なくとも一つの内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列の転動体と、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両側開口部に装着されたシールとを備え、これらシールのうちアウター側のシールが、前記外方部材の端部内周に嵌合される芯金と、この芯金に一体に接合され、径方向外方に傾斜して延びるサイドリップと、軸受内方側に傾斜して延びるグリースリップとを有するシール部材からなる一体型のシールで構成された車輪用軸受装置において、前記外方部材のアウター側の端部外周に円環状のキャップが装着され、このキャップが、前記外方部材の端部外周に圧入される円筒状の嵌合部と、この嵌合部の一端部から径方向内方に延びる折曲部を備え、この折曲部の路面側にポケット部が設けられ、このポケット部から軸方向に延びる樋部が一体に形成されている。   In order to achieve such an object, the invention according to claim 1 of the present invention includes an outer member integrally including a vehicle body mounting flange on the outer periphery and a double row outer rolling surface formed integrally on the inner periphery. , A hub wheel integrally having a wheel mounting flange for mounting a wheel at one end, and a small-diameter step portion extending in the axial direction on the outer periphery, and press-fitting the small-diameter step portion of this hub wheel through a predetermined shimiro An inner member composed of at least one inner ring formed on the outer periphery with an inner rolling surface of the double row outer rolling surface, and a cage between both rolling surfaces of the inner member and the outer member. A plurality of rolling elements accommodated so as to be freely rollable via a seal, and seals mounted on both side openings of an annular space formed between the outer member and the inner member. Of these, the outer side seal is fitted to the inner periphery of the end of the outer member, A wheel bearing device comprising an integral seal formed of a seal member integrally joined to gold and having a side lip extending obliquely outward in the radial direction and a grease lip extending inclined toward the inner side of the bearing In this, an annular cap is attached to the outer periphery of the outer end of the outer member, and the cap is fitted into a cylindrical fitting portion that is press-fitted into the outer periphery of the outer member. A bent portion extending inward in the radial direction from one end of the bent portion, a pocket portion is provided on the road surface side of the bent portion, and a flange portion extending in the axial direction from the pocket portion is integrally formed.

このように、外方部材のアウター側の端部外周に円環状のキャップが装着され、このキャップが、外方部材の端部外周に圧入される円筒状の嵌合部と、この嵌合部の一端部から径方向内方に延びる折曲部を備え、この折曲部の路面側にポケット部が設けられ、このポケット部から軸方向に延びる樋部が一体に形成されているので、外部から浸入した泥水等がシール部への浸入を防止するだけでなく、シールを介して漏洩されたグリースあるいはオイルが遠心力によって飛散したとしてもブレーキ部品に付着することがなく、流出してきたグリースあるいはオイルをこのポケット部で回収し、このポケット部からインナー側に延びる樋部を伝わせて泥水やオイルを路面側へ排出することができる。   Thus, an annular cap is attached to the outer periphery of the outer side end of the outer member, and this cap is a cylindrical fitting portion that is press-fitted into the outer periphery of the outer member, and this fitting portion. A bent portion extending inward in the radial direction from one end of the pocket, a pocket portion is provided on the road surface side of the bent portion, and a flange portion extending in the axial direction from the pocket portion is integrally formed. In addition to preventing intrusion of muddy water from the seals into the seal part, grease or oil leaked through the seals will not adhere to the brake parts even if the grease or oil is scattered by centrifugal force. Oil can be collected in this pocket portion, and muddy water and oil can be discharged to the road surface side along a flange extending from the pocket portion toward the inner side.

好ましくは、請求項２に記載の発明のように、前記樋部の先端部が前記車体取付フランジよりもインナー側に開口するように設定されていれば、ブレーキ性能に悪影響を及ぼすのを確実に防止することができ、シールの密封性能の向上を図り、軸受性能を長期間に亘って維持することができる車輪用軸受装置を提供することができる。   Preferably, as in the invention described in claim 2, if the tip end portion of the flange portion is set so as to open to the inner side of the vehicle body mounting flange, it is ensured that the brake performance is adversely affected. Thus, it is possible to provide a wheel bearing device that can be prevented, improve the sealing performance of the seal, and maintain the bearing performance over a long period of time.

また、請求項３に記載の発明のように、前記ポケット部の底部が、前記嵌合部の一部が拡径し、インナー側に所定の傾斜角だけ広がるテーパ状に形成されていれば、キャップのオイル溜り部にインナー側へ拡張する方向に角度をつけることができ、オイルの排出性能を向上させることができる。   Further, as in the invention according to claim 3, if the bottom portion of the pocket portion is formed in a tapered shape in which a part of the fitting portion is enlarged in diameter and widened by a predetermined inclination angle on the inner side, The oil reservoir of the cap can be angled in the direction of expansion toward the inner side, and the oil discharge performance can be improved.

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のインナー側の側面と基部との間には段部が形成され、この段部と前記キャップの折曲部の内縁が僅かな径方向すきまを介して対向し、ラビリンスが構成されていれば、キャップと軸受間にてラビリンス構造をとっていることにより、外部からの泥水浸入防止の効果があり、耐泥水性能が向上する。   Further, as in the invention described in claim 4, a step portion is formed between the inner side surface of the wheel mounting flange and the base portion, and the inner edge of the step portion and the bent portion of the cap is slight. If the labyrinth is configured so as to face each other through the radial clearance, the labyrinth structure is formed between the cap and the bearing, so that there is an effect of preventing muddy water from entering from the outside, and the muddy water resistance is improved.

また、請求項５に記載の発明のように、前記ラビリンスの径方向すきまが直径で０．３〜３．０ｍｍの範囲に設定されていれば、良好なラビリンス効果が得られると共に、軸受の組立時に段部との干渉を避けるために綿密な芯合わせをする必要がなくなって作業性が向上する。   If the radial clearance of the labyrinth is set in the range of 0.3 to 3.0 mm in diameter as in the invention described in claim 5, a good labyrinth effect can be obtained and the assembly of the bearing can be achieved. Sometimes it is not necessary to align the cores closely in order to avoid interference with the stepped portion, thereby improving workability.

また、請求項６に記載の発明のように、前記キャップの折曲部の内径と前記外方部材の端部内径との径差が片側で０．３ｍｍ以上に設定されていれば、キャップを外方部材に圧入治具によって圧入する時、外方部材の端面を基準に位置決めすることができ、精度良く、かつ容易にキャップを外方部材に固定することができる。   Further, as in the invention according to claim 6, if the difference in diameter between the inner diameter of the bent portion of the cap and the inner diameter of the end of the outer member is set to 0.3 mm or more on one side, the cap is removed. When the outer member is press-fitted by a press-fitting jig, the end surface of the outer member can be positioned as a reference, and the cap can be fixed to the outer member accurately and easily.

また、請求項７に記載の発明のように、前記ハブ輪の段部に環状溝が形成されていれば、シールから漏洩したグリースあるいはオイルがハブ輪の回転に伴う遠心力によって飛散しても、キャップ側へ誘導させて路面側に流出させることができる。   Further, as in the seventh aspect of the present invention, if an annular groove is formed in the step portion of the hub wheel, grease or oil leaking from the seal may be scattered by centrifugal force accompanying the rotation of the hub wheel. , Can be guided to the cap side and flow out to the road surface side.

また、請求項８に記載の発明のように、前記ハブ輪の外周に、前記車輪取付フランジのインナー側の側面の根元部から前記小径段部に亙って高周波焼入れによって所定の硬化層が形成されていれば、車輪取付フランジを介して繰り返しモーメント荷重がハブ輪に負荷され、基部に応力が集中しても充分な強度を確保することができる。   Further, as in the invention according to claim 8, a predetermined hardened layer is formed on the outer periphery of the hub wheel by induction quenching from the root portion of the inner side surface of the wheel mounting flange to the small diameter step portion. If so, a sufficient moment strength can be secured even if a moment load is repeatedly applied to the hub wheel via the wheel mounting flange and stress concentrates on the base.

また、請求項９に記載の発明のように、前記車輪取付フランジのインナー側の基部が所定の曲率半径ｒからなる円弧状に形成され、この基部に鋼板からプレス加工にて形成されたディフレクタが嵌着され、このディフレクタが、前記ハブ輪の肩部に外嵌される円筒状の嵌合部と、前記基部の形状に対応して円弧状に形成された湾曲部と、この湾曲部から径方向外方に延び、前記基部の側面に密着される円板部とを備え、前記シール部材の少なくともサイドリップが前記ディフレクタに摺接されると共に、前記ディフレクタの湾曲部が前記基部の円弧面に対応して所定の曲率半径Ｒからなる円弧面に形成され、それぞれの曲率半径Ｒ、ｒが、Ｒ＞ｒになるように設定されていれば、良好なシール摺接面を得ることができ、リップ摩耗を抑制して劣悪な環境で使用されても、シールの密封性能の維持を図ることができると共に、ディフレクタを基部に嵌合した時に基部の円弧面にディフレクタの湾曲部が干渉して浮き上がるのを防止し、基部の側面とディフレクタの円板部との間に隙間が生じるのを防止することができ、両者が密着してサイドリップのシメシロのバラツキを抑えて安定した密封性を確保することができる。   Further, as in the invention described in claim 9, a base portion on the inner side of the wheel mounting flange is formed in an arc shape having a predetermined radius of curvature r, and a deflector formed by pressing a steel plate on the base portion is provided. The deflector includes a cylindrical fitting portion that is fitted on the shoulder portion of the hub wheel, a curved portion that is formed in an arc shape corresponding to the shape of the base portion, and a diameter from the curved portion. A disc portion that extends outward in the direction and is in close contact with a side surface of the base portion, and at least a side lip of the seal member is slidably contacted with the deflector, and a curved portion of the deflector is on an arc surface of the base portion. Correspondingly, if it is formed on a circular arc surface having a predetermined radius of curvature R, and the respective curvature radii R and r are set so that R> r, a good seal sliding contact surface can be obtained, Suppress lip wear Even when used in a bad environment, the sealing performance of the seal can be maintained, and when the deflector is fitted to the base, it prevents the curved part of the deflector from interfering with the arcuate surface of the base, and the base It is possible to prevent a gap from being formed between the side surface of the plate and the disc portion of the deflector, and the two can be in close contact with each other to suppress variations in the side lip and secure a stable sealing performance.

また、請求項１０に記載の発明のように、前記ディフレクタの円板部が前記段部の最外径部よりも突出して形成されていれば、外部から浸入した泥水等がシール部への浸入を防止するだけでなく、シールから漏洩したグリースあるいはオイルがハブ輪の回転に伴う遠心力によって飛散しても、このキャップ側へ誘導させて路面側に流出させることができる。   Further, as in the invention described in claim 10, if the disc portion of the deflector is formed so as to protrude from the outermost diameter portion of the stepped portion, muddy water or the like entering from the outside enters the seal portion. In addition, the grease or oil leaked from the seal can be guided to the cap side and flow out to the road surface side even if the grease or oil leaked by the centrifugal force accompanying the rotation of the hub wheel.

また、請求項１１に記載の発明のように、前記ディフレクタの円板部の先端部に加硫接着により弾性部材が一体に接合され、この弾性部材が前記基部の側面に弾性接触していれば、基部の側面とディフレクタの円板部との間にすきまが生じるのを確実に防止することができ、当部から泥水等がディフレクタに浸漬し、ハブ輪の基部が発錆するのを防止することができる。   Further, as in the invention described in claim 11, if an elastic member is integrally joined to the distal end portion of the disk portion of the deflector by vulcanization adhesion, and the elastic member is in elastic contact with the side surface of the base portion The gap between the side of the base and the disk part of the deflector can be reliably prevented, and muddy water can be immersed in the deflector from this part, preventing the base of the hub wheel from rusting. be able to.

また、請求項１２に記載の発明のように、前記ディフレクタが、その表面にショットブラスト処理によって無数のディンプルが形成され、表面粗さがＲａ１．０〜５．０の範囲に粗面化処理されていれば、良好なシール摺接面を得ることができ、リップ摩耗を抑制すると共に、劣悪な環境で使用されても、シールの密封性能の維持を図ることができる。   Further, as in the invention described in claim 12, the deflector is formed with innumerable dimples on the surface thereof by shot blasting, and the surface roughness is roughened in the range of Ra 1.0 to 5.0. If so, a good seal sliding contact surface can be obtained, lip wear can be suppressed, and the sealing performance of the seal can be maintained even when used in a poor environment.

本発明に係る車輪用軸受装置は、外周に車体取付フランジを一体に有し、内周に複列の外側転走面が一体に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の一方に対向する内側転走面と、この内側転走面から軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列の転動体と、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両側開口部に装着されたシールとを備え、これらシールのうちアウター側のシールが、前記外方部材の端部内周に嵌合される芯金と、この芯金に一体に接合され、径方向外方に傾斜して延びるサイドリップと、軸受内方側に傾斜して延びるグリースリップとを有するシール部材からなる一体型のシールで構成された車輪用軸受装置において、前記外方部材のアウター側の端部外周に円環状のキャップが装着され、このキャップが、前記外方部材の端部外周に圧入される円筒状の嵌合部と、この嵌合部の一端部から径方向内方に延びる折曲部を備え、この折曲部の路面側にポケット部が設けられ、このポケット部から軸方向に延びる樋部が一体に形成されているので、外部から浸入した泥水等がシール部への浸入を防止するだけでなく、シールを介して漏洩されたグリースあるいはオイルが遠心力によって飛散したとしてもブレーキ部品に付着することがなく、流出してきたグリースあるいはオイルをこのポケット部で回収し、このポケット部からインナー側に延びる樋部を伝わせて泥水やオイルを路面側へ排出することができる。   A wheel bearing device according to the present invention has a vehicle body mounting flange integrally formed on the outer periphery, an outer member integrally formed with a double row outer rolling surface on the inner periphery, and a wheel for mounting a wheel on one end. A hub wheel integrally having a wheel mounting flange and having an inner rolling surface facing one of the outer rolling surfaces of the double row on the outer periphery and a small-diameter step portion extending in the axial direction from the inner rolling surface, And an inner member formed of an inner ring that is press-fitted into a small-diameter step portion of the hub ring through a predetermined shimoshiro and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery, A double row rolling element housed between a rolling surface of the inner member and the outer member via a cage, and a ring formed between the outer member and the inner member. Seals attached to the openings on both sides of the space. A metal core fitted to the inner periphery of the end of the member; a side lip integrally joined to the metal core and extending obliquely outward in the radial direction; and a grease lip extending inclined toward the inner side of the bearing In the wheel bearing device constituted by an integral seal made of a seal member, an annular cap is attached to the outer periphery of the outer side end of the outer member, and the cap is connected to the outer periphery of the end of the outer member. A cylindrical fitting portion that is press-fitted into the fitting portion, and a bent portion that extends radially inward from one end portion of the fitting portion, and a pocket portion is provided on the road surface side of the bent portion. Since the flange extending in the axial direction is integrally formed, not only does muddy water entering from the outside prevent entry into the seal part, but also grease or oil leaked through the seal is scattered by centrifugal force. As well as brake parts Without adhering, a has leaked grease or oil recovered in this pocket portion, the muddy water and oil can be discharged to the road surface by Tsutawa gutter portion extending inner side from the pocket portion.

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の一方のシール部を示す要部拡大図である。It is a principal part enlarged view which shows one seal part of FIG. 本発明に係るキャップを示す要部拡大図である。It is a principal part enlarged view which shows the cap which concerns on this invention. （ａ）は、図１のキャップ単体を示す正面図、（ｂ）は、（ａ）のＩＶ−ＩＶ線断面図、（ｃ）は、（ａ）の裏面図である。(A) is the front view which shows the cap single-piece | unit of FIG. 1, (b) is the IV-IV sectional view taken on the line of (a), (c) is the back view of (a). 図２のキャップの変形例を示す要部拡大図である。It is a principal part enlarged view which shows the modification of the cap of FIG. 図５のキャップの圧入状態を示す説明図である。It is explanatory drawing which shows the press-fit state of the cap of FIG. 図５の外方部材の変形例を示す要部拡大図である。It is a principal part enlarged view which shows the modification of the outward member of FIG. 図５のハブ輪の変形例を示す要部拡大図である。It is a principal part enlarged view which shows the modification of the hub ring of FIG. 図８のハブ輪の硬化層を示す断面図である。It is sectional drawing which shows the hardened layer of the hub ring of FIG. 図９のハブ輪の変形例を示す断面図である。It is sectional drawing which shows the modification of the hub ring of FIG. 図２の変形例を示す要部拡大図である。It is a principal part enlarged view which shows the modification of FIG. 図１１のディフレクタの変形例を示す要部拡大図である。It is a principal part enlarged view which shows the modification of the deflector 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. 図１３の一方のシール部を示す要部拡大図である。It is a principal part enlarged view which shows one seal | sticker part of FIG. 従来の車輪用軸受装置のシール装置を示す要部拡大図である。It is a principal part enlarged view which shows the sealing device of the conventional wheel bearing apparatus.

外周に車体取付フランジを一体に有し、内周に複列の外側転走面が一体に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の一方に対向する内側転走面と、この内側転走面から軸方向に延びる小径段部が形成されたハブ輪、およびこのハブ輪の小径段部に所定のシメシロを介して圧入され、外周に前記複列の外側転走面の他方に対向する内側転走面が形成された内輪からなる内方部材と、この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列の転動体と、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両側開口部に装着されたシールとを備え、これらシールのうちアウター側のシールが、前記外方部材の端部内周に嵌合される芯金と、この芯金に一体に接合され、径方向外方に傾斜して延びるサイドリップとダストリップ、および軸受内方側に傾斜して延びるグリースリップとを有するシール部材からなる一体型のシールで構成された車輪用軸受装置において、前記外方部材のアウター側の端部外周に円環状のキャップが装着され、このキャップが、耐食性を有する鋼板からプレス加工にて形成され、前記外方部材の端部外周に圧入される円筒状の嵌合部と、この嵌合部の一端部から径方向外方に延びる鍔部と、前記嵌合部の他端部から径方向内方に延び、この内径と前記外方部材の端部内径との径差が０．３ｍｍ（片側）以上に設定された折曲部を備え、この折曲部の路面側にポケット部が設けられ、このポケット部の底部が、前記嵌合部の一部が拡径し、インナー側に所定の傾斜角だけ広がるテーパ状に形成され、当該ポケット部から軸方向に延びる樋部が一体に形成されて、この樋部の先端部が前記車体取付フランジよりもインナー側に開口するように設定されると共に、前記車輪取付フランジのインナー側の側面と基部との間に段部が形成され、この段部と前記キャップの折曲部の内縁が０．３〜３．０ｍｍ（直径）の範囲の径方向すきまを介して対向し、ラビリンスが構成されている。   A body mounting flange is integrally formed on the outer periphery, an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, and a wheel mounting flange for mounting a wheel on one end is integrated. A hub ring formed with an inner rolling surface facing one of the outer rolling surfaces of the double row, a small-diameter step portion extending in the axial direction from the inner rolling surface, and a small-diameter step portion of the hub ring. An inner member formed of an inner ring that is press-fitted through the outer periphery and has an inner rolling surface facing the other of the outer rolling surfaces of the double row on the outer periphery, and both the inner member and the outer member. A double row rolling element accommodated between the rolling surfaces via a cage, and a seal attached to both side openings of an annular space formed between the outer member and the inner member Of these seals, the outer seal being fitted to the inner periphery of the end of the outer member And a seal member having a side lip and a dust lip that are integrally joined to the metal core and extend obliquely outward in the radial direction, and a grease lip that extends obliquely inward of the bearing. In the configured wheel bearing device, an annular cap is attached to the outer periphery of the outer side end of the outer member, and the cap is formed by pressing from a corrosion-resistant steel plate. A cylindrical fitting portion press-fitted into the outer periphery of the end portion, a flange portion extending radially outward from one end portion of the fitting portion, and extending radially inward from the other end portion of the fitting portion, There is a bent portion in which the diameter difference between the inner diameter and the inner diameter of the end of the outer member is set to 0.3 mm (one side) or more, and a pocket portion is provided on the road surface side of the bent portion. The bottom part is a part of the fitting part, and the inner diameter is increased. And a flange portion extending in the axial direction from the pocket portion is integrally formed, and the tip end portion of the flange portion opens to the inner side of the vehicle body mounting flange. And a step is formed between the inner side surface of the wheel mounting flange and the base, and the inner edge of the step and the bent portion of the cap is 0.3 to 3.0 mm (diameter). The labyrinths are configured to face each other via a radial clearance in the range.

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、図２は、図１の一方のシール部を示す要部拡大図、図３は、本発明に係るキャップを示す要部拡大図、図４（ａ）は、図１のキャップ単体を示す正面図、（ｂ）は、（ａ）のＩＶ−ＩＶ線断面図、（ｃ）は、（ａ）の裏面図、図５は、図２のキャップの変形例を示す要部拡大図、図６は、図５のキャップの圧入状態を示す説明図、図７は、図５の外方部材の変形例を示す要部拡大図、図８は、図５のハブ輪の変形例を示す要部拡大図、図９は、図８のハブ輪の硬化層を示す断面図、図１０は、図９のハブ輪の変形例を示す断面図、図１１は、図２の変形例を示す要部拡大図、図１２は、図１１のディフレクタの変形例を示す要部拡大図である。なお、以下の説明では、車両に組み付けた状態で車両の外側寄りとなる側をアウター側（図１の左側）、中央寄り側をインナー側（図１の右側）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, FIG. 2 is an enlarged view of a main part showing one seal portion of FIG. 1, and FIG. 3 is according to the present invention. FIG. 4A is a front view showing the single cap of FIG. 1, FIG. 4B is a cross-sectional view taken along the line IV-IV of FIG. 1A, and FIG. FIG. 5 is an enlarged view of a main part showing a modification of the cap of FIG. 2, FIG. 6 is an explanatory view showing a press-fitted state of the cap of FIG. 5, and FIG. 7 is a modification of the outer member of FIG. FIG. 8 is an enlarged view of a main part showing a modification of the hub wheel of FIG. 5, FIG. 9 is a cross-sectional view showing a hardened layer of the hub wheel of FIG. 8, and FIG. 11 is a cross-sectional view showing a modification of the hub wheel, FIG. 11 is an enlarged view of a main part showing a modification of FIG. 2, and FIG. 12 is an enlarged view of a main part showing a modification of the deflector in FIG. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outer side (left side in FIG. 1), and the side closer to the center is referred to as the inner side (right side in FIG. 1).

車輪用軸受装置は図示しない車軸管に固定されると共に、駆動軸にトルク伝達可能に連結されている。この車輪用軸受装置は第３世代と呼称され、内方部材１と、この内方部材１に複列の転動体（ボール）３を介して外挿された外方部材２とを備えている。内方部材１は、ハブ輪４と、このハブ輪４に固定された内輪５とからなる。   The wheel bearing device is fixed to an axle tube (not shown) and connected to the drive shaft so as to be able to transmit torque. This wheel bearing device is referred to as a third generation, and includes an inner member 1 and an outer member 2 inserted on the inner member 1 via double-row rolling elements (balls) 3. . The inner member 1 includes a hub ring 4 and an inner ring 5 fixed to the hub ring 4.

ハブ輪４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６を一体に有し、外周に一方（アウター側）の内側転走面４ａと、この内側転走面４ａから軸方向に延びる小径段部４ｂが形成され、内周に駆動軸が係合するセレーション（またはスプライン）４ｃが形成されている。車輪取付フランジ６にはハブボルト６ａが周方向等配に植設されている。   The hub wheel 4 integrally has a wheel mounting flange 6 for mounting a wheel (not shown) at an end portion on the outer side, and has one (outer side) inner rolling surface 4a on the outer periphery and the inner rolling surface. A small diameter step 4b extending in the axial direction from the surface 4a is formed, and a serration (or spline) 4c with which the drive shaft engages is formed on the inner periphery. Hub bolts 6a are planted on the wheel mounting flange 6 at equal intervals in the circumferential direction.

内輪５は、外周に他方（インナー側）の内側転走面５ａが形成され、ハブ輪４の小径段部４ｂに所定のシメシロを介して圧入され、小径段部４ｂの端部を径方向外方に塑性変形させて形成した加締部４ｄによって所定の軸受予圧が付与された状態でハブ輪４に対して軸方向に固定されている。   The inner ring 5 is formed with the other (inner side) inner rolling surface 5a on the outer periphery, and is press-fitted into the small-diameter step portion 4b of the hub wheel 4 through a predetermined shimiro, and the end of the small-diameter step portion 4b is radially outward. It is fixed to the hub wheel 4 in the axial direction in a state where a predetermined bearing preload is applied by a caulking portion 4d formed by plastic deformation in the direction.

ハブ輪４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４ａをはじめ、車輪取付フランジ６のインナー側の基部６ｂから小径段部４ｂ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４ｄは鍛造加工後の表面硬さのままで未焼入れ部とされている。これにより、車輪取付フランジ６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５の嵌合部となる小径段部４ｂの耐フレッティング性が向上すると共に、加締加工によって加締部４ｄに微小クラック等が発生するのを防止している。   The hub wheel 4 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 4a and the base portion 6b on the inner side of the wheel mounting flange 6 are connected to the small diameter step portion 4b. Thus, the surface hardness is set to a range of 58 to 64 HRC by induction hardening. The caulking portion 4d is an unquenched portion with the surface hardness after forging. This has sufficient mechanical strength against the rotational bending load applied to the wheel mounting flange 6, improves the fretting resistance of the small-diameter stepped portion 4b serving as the fitting portion of the inner ring 5, and performs caulking. A micro crack or the like is prevented from occurring in the caulking portion 4d due to the processing.

外方部材２は、外周に車軸管に取り付けられるための車体取付フランジ２ｂを一体に有し、内周に内方部材１の複列の内側転走面４ａ、５ａに対向する複列の外側転走面２ａ、２ａが一体に形成されている。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、少なくとも複列の外側転走面２ａ、２ａ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。一方、内輪５および転動体３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。そして、外方部材２と内方部材１の両転走面間に複列の転動体３、３が収容され、保持器７、７によって転動自在に保持されて背面合せタイプの複列アンギュラ玉軸受が構成されている。   The outer member 2 integrally has a vehicle body mounting flange 2b to be attached to the axle tube on the outer periphery, and the outer side of the double row facing the inner rolling surfaces 4a, 5a of the inner row 1 on the inner periphery. The rolling surfaces 2a and 2a are integrally formed. The outer member 2 is formed of medium-high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 2a and 2a have a surface hardness of 58 to 64 HRC by induction hardening. Hardened to range. On the other hand, the inner ring 5 and the rolling element 3 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 portion by quenching. And the double row rolling elements 3 and 3 are accommodated between both rolling surfaces of the outer member 2 and the inner member 1, and are held by the cages 7 and 7 so as to roll freely. A ball bearing is configured.

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８、９が装着されている。これらのシール８、９によって、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浸入するのを防止している。なお、インナー側のシール９においては、ハブ輪４のセレーション４ｃを通してデフオイルが軸受内部に浸入するのを防止している。   Seals 8 and 9 are attached to the opening of the annular space formed between the outer member 2 and the inner member 1. These seals 8 and 9 prevent the grease sealed inside the bearing from leaking outside and preventing rainwater, dust, and the like from entering the bearing from the outside. The inner seal 9 prevents the differential oil from entering the bearing through the serrations 4 c of the hub wheel 4.

ハブ輪４のアウター側端部の開口部にはキャップ１０が圧入されている。このキャップ１０は、オーステナイト系ステンレス鋼板（ＪＩＳ規格のＳＵＳ３０４系等）、あるいは、防錆処理された冷間圧延鋼板（ＪＩＳ規格のＳＰＣＣ系等）からなり、プレス加工によって環状に形成されている。キャップ１０は、断面略コの字形に形成された鋼板製の芯金１０ａと、この芯金１０ａの少なくとも外部に露出する外表面に加硫接着等により接合されたゴム等の弾性部材１０ｂとからなる。そして、この弾性部材１０ｂが嵌合面に弾性変形して入り込み、液密に内部を密封している。したがって、デフオイルの外部への流出と、外部から雨水やダスト等が駆動軸内に浸入してデフオイル内に混入するのを確実に防止することができる。   A cap 10 is press-fitted into the opening at the end on the outer side of the hub wheel 4. The cap 10 is made of an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold-rolled steel plate (JIS standard SPCC type or the like), and is formed in an annular shape by press working. The cap 10 includes a steel core 10a having a substantially U-shaped cross section, and an elastic member 10b such as rubber joined to the outer surface of the core 10a exposed to at least the outside by vulcanization adhesion or the like. Become. The elastic member 10b is elastically deformed and enters the fitting surface to seal the inside in a liquid-tight manner. Therefore, it is possible to reliably prevent the diff oil from flowing out and rainwater, dust, and the like from the outside to enter the drive shaft and enter the def oil.

アウター側のシール８は、図２に拡大して示すように、外方部材２のアウター側の端部内周に嵌合される芯金１１と、この芯金１１に加硫接着等により一体に接合されたシール部材１２とからなる一体型のシールで構成されている。この芯金１１は、オーステナイト系ステンレス鋼板（ＪＩＳ規格のＳＵＳ３０４系等）や防錆処理された冷間圧延鋼板（ＪＩＳ規格のＳＰＣＣ系等）の耐食性に優れた鋼板からプレス加工にて断面が略コの字状に形成されている。   As shown in an enlarged view in FIG. 2, the outer side seal 8 is integrally formed with a core metal 11 fitted to the inner periphery of the outer side end of the outer member 2, and the core metal 11 by vulcanization adhesion or the like. It is composed of an integrated seal composed of the joined seal member 12. The core 11 has a substantially cross-sectional shape by pressing from a steel plate having excellent corrosion resistance such as an austenitic stainless steel plate (JIS standard SUS304 type or the like) or a rust-proof cold rolled steel plate (JIS standard SPCC type or the like). It is formed in a U shape.

一方、シール部材１２は、ＮＢＲ（アクリロニトリル−ブタジエンゴム）等の合成ゴムからなり、芯金１１の外周部に接合され、径方向外方に傾斜して延びるサイドリップ１２ａ、１２ｂ、および芯金１１の内縁部に接合され、軸受内方側に傾斜して延びるグリースリップ１２ｃを有している。これらのサイドリップ１２ａ、１２ｂおよびグリースリップ１２ｃは、車輪取付フランジ６のインナー側の基部６ｂに摺接されている。また、芯金１１の外方部にはシール部材１２が回り込んで接合され、所謂ハーフメタル構造をなし、外方部材２と芯金１１との嵌合部から泥水等の異物が軸受内部に浸入するのを防止している。なお、シール部材１２の材質としては、例示したＮＢＲ以外にも、例えば、耐熱性に優れたＨＮＢＲ（水素化アクリロニトリル・ブタジエンゴム）、ＥＰＤＭ（エチレンプロピレンゴム）等をはじめ、耐熱性、耐薬品性に優れたＡＣＭ（ポリアクリルゴム）、ＦＫＭ（フッ素ゴム）、あるいはシリコンゴム等を例示することができる。   On the other hand, the seal member 12 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber), joined to the outer peripheral portion of the core metal 11, and side lips 12 a and 12 b extending in a radially outward direction and the core metal 11. The grease lip 12c is inclined and extends inwardly of the bearing. These side lips 12 a and 12 b and the grease lip 12 c are in sliding contact with the base 6 b on the inner side of the wheel mounting flange 6. Further, a seal member 12 wraps around and is joined to the outer portion of the core metal 11 to form a so-called half metal structure, and foreign matter such as muddy water enters the inside of the bearing from the fitting portion between the outer member 2 and the core metal 11. Prevents intrusion. In addition to the exemplified NBR, the material of the seal member 12 includes, for example, HNBR (hydrogenated acrylonitrile butadiene rubber), EPDM (ethylene propylene rubber), etc., which have excellent heat resistance, and heat resistance and chemical resistance. Examples thereof include ACM (polyacrylic rubber), FKM (fluororubber), and silicon rubber, which are excellent in the above.

なお、ここでは、転動体３にボールを使用した複列アンギュラ玉軸受で構成された車輪用軸受装置を例示したが、無論これに限らず、転動体に円錐ころを使用した複列円錐ころ軸受で構成されていても良い。   In addition, although the wheel bearing apparatus comprised by the double row angular contact ball bearing which used the ball for the rolling element 3 was illustrated here, of course, it is not restricted to this, The double row tapered roller bearing which used the tapered roller for the rolling element It may consist of.

ここで、本実施形態では、外方部材２のアウター側の端部外周にキャップ１３が装着されている。このキャップ１３は、耐食性を有する鋼板、例えば、オーステナイト系ステンレス鋼板、あるいは、防錆処理された冷間圧延鋼板からプレス加工にて形成され、外方部材２の端部外周に圧入される円筒状の嵌合部１４と、この嵌合部１４の一方（インナー側）の端部から径方向外方に折曲された鍔部１５と、嵌合部１５の他方（アウター側）の端部から径方向内方に延びる折曲部１６とを備えている。この鍔部１５によりキャップ１３の剛性を高めると共に、外方部材２への圧入性を向上させている。そして、この折曲部１６の路面側に最も近い部分にポケット部１７が設けられ、このポケット部１７から軸方向に延びる樋部１８が一体に形成されている（図１、図４参照）。   Here, in the present embodiment, the cap 13 is attached to the outer periphery of the outer end portion of the outer member 2. The cap 13 is formed of a steel plate having corrosion resistance, such as an austenitic stainless steel plate, or a cold-rolled steel plate that has been rust-proofed by press working, and is pressed into the outer periphery of the end portion of the outer member 2. From the fitting portion 14, the flange 15 bent radially outward from one end (inner side) of the fitting portion 14, and the other (outer side) end of the fitting portion 15 And a bent portion 16 extending inward in the radial direction. The flange portion 15 increases the rigidity of the cap 13 and improves the press-fitting property to the outer member 2. And the pocket part 17 is provided in the part nearest to the road surface side of this bending part 16, and the collar part 18 extended from this pocket part 17 to an axial direction is integrally formed (refer FIG. 1, FIG. 4).

なお、キャップ１３は、例示した耐食性を有する鋼板以外に、加工性が良好で、廉価な冷間圧延鋼板に、カチオン電着塗装によって防錆皮膜を形成したものであっても良い。なお、カチオン電着塗装は、正電極に対して、製品側を負電極として通電するものであるが、負電極に対して、製品側を正電極として通電するアニオン型の電着塗装であっても良い。このアニオン型の電着塗装の場合、塗装色の安定性や焼付温度を低く設定できる特徴を備えているが、この種のキャップ１３においては、防錆力と密着力に優れた強力な塗装膜が形成できるエポキシ樹脂系等からなるカチオン電着塗装の方が好ましい。   The cap 13 may be formed by forming a rust preventive film by cationic electrodeposition coating on an inexpensive cold rolled steel sheet having good workability other than the exemplified steel sheet having corrosion resistance. The cationic electrodeposition coating is an anionic electrodeposition coating in which the product side is energized with the product side as the negative electrode while the positive electrode is energized with the product side as the positive electrode. Also good. In the case of this anionic electrodeposition coating, the coating color stability and the baking temperature can be set low, but this type of cap 13 has a strong coating film excellent in rust prevention and adhesion. Cationic electrodeposition coating made of an epoxy resin system or the like that can be formed is more preferable.

車輪取付フランジ６のインナー側の側面６ｃと基部６ｂとの間には段部１９が形成されている。この段部１９は、基部６ｂの最外径部から車輪取付フランジ６の側面６ｃに亙って滑らかな円弧状の曲面に形成され、キャップ１３の折曲部１６の内縁との間に僅かな径方向すきまＣを介して対向し、ラビリンス２０が構成されている。これにより、シール８から漏洩したグリースあるいはオイルがハブ輪４の回転に伴う遠心力によって飛散しても、このキャップ１３で集めて路面側（図１の下側）に流出させることができる。   A step portion 19 is formed between the inner side surface 6c of the wheel mounting flange 6 and the base portion 6b. The step portion 19 is formed into a smooth arcuate curved surface from the outermost diameter portion of the base portion 6 b to the side surface 6 c of the wheel mounting flange 6, and is slightly between the inner edge of the bent portion 16 of the cap 13. The labyrinth 20 is configured to face each other via a radial clearance C. Thereby, even if the grease or oil leaked from the seal 8 is scattered by the centrifugal force accompanying the rotation of the hub wheel 4, it can be collected by the cap 13 and discharged to the road surface side (lower side in FIG. 1).

このラビリンス２０の径方向すきまＣは０．３〜３．０ｍｍ（直径）の範囲に設定されている。なお、径方向すきまＣが０．３ｍｍ未満では、軸受の組立時に段部１９との干渉を避けるために綿密な芯合わせが必要になって作業性が悪くなる。また、径方向すきまＣが３．０ｍｍを超えると、ラビリンス２０の効果が半減して好ましくない。   The radial clearance C of the labyrinth 20 is set in a range of 0.3 to 3.0 mm (diameter). If the radial clearance C is less than 0.3 mm, close alignment is required to avoid interference with the stepped portion 19 during the assembly of the bearing, resulting in poor workability. Moreover, when the radial clearance C exceeds 3.0 mm, the effect of the labyrinth 20 is halved, which is not preferable.

キャップ１３は円環状に形成され、図４に示すように、嵌合部１４の径方向内方の路面側の最下部に受け皿状のポケット部１７が一体に形成されている。このポケット部１７は、図３に拡大して示すように、嵌合部１４の一部が拡径して形成された底部１７ａと、この底部１７ａの端部に径方向外方に湾曲して形成された縁部１７ｂと、この縁部１７ｂの一部が開口され、軸方向に傾斜して延びる樋部１８を一体に備えている。樋部１８の先端部には水平に折曲された排出口１８ａが形成されている。   The cap 13 is formed in an annular shape, and, as shown in FIG. 4, a tray-like pocket portion 17 is integrally formed at the lowermost portion on the road surface side radially inward of the fitting portion 14. As shown in FIG. 3 in an enlarged manner, the pocket portion 17 has a bottom portion 17a formed by expanding the diameter of a part of the fitting portion 14, and is curved radially outward at an end portion of the bottom portion 17a. The formed edge portion 17b and a part of the edge portion 17b are opened, and a flange portion 18 that is inclined and extends in the axial direction is integrally provided. A discharge port 18 a that is bent horizontally is formed at the tip of the flange portion 18.

ポケット部１７の底部１７ａは、インナー側（図中右方向）に所定の傾斜角α（α＝１〜１５°）だけ傾斜したテーパ状に形成されている。これにより、キャップ１３から流出してきたグリースあるいはオイルをこのポケット部１７で回収し、このポケット部１７から樋部１８を介して外部にスムーズに排出させることができる。なお、樋部１８は外方部材２の車体取付フランジ２ｂを避けた部分に配置され、この樋部１８の先端部１８ａがこの車体取付フランジ２ｂよりもインナー側に開口するように設定されている（図１参照）。これにより、排出されたグリースあるいはオイルが遠心力によって飛散したとしてもブレーキ部品に付着することがなく、ブレーキ性能に悪影響を及ぼすのを確実に防止することができる。   The bottom portion 17a of the pocket portion 17 is formed in a tapered shape that is inclined toward the inner side (rightward in the figure) by a predetermined inclination angle α (α = 1 to 15 °). As a result, grease or oil that has flowed out of the cap 13 can be collected in the pocket portion 17 and can be smoothly discharged from the pocket portion 17 to the outside through the flange portion 18. The flange portion 18 is disposed in a portion of the outer member 2 away from the vehicle body mounting flange 2b, and the distal end portion 18a of the flange portion 18 is set to open to the inner side of the vehicle body mounting flange 2b. (See FIG. 1). As a result, even if the discharged grease or oil is scattered by centrifugal force, it does not adhere to the brake parts, and it is possible to reliably prevent the brake performance from being adversely affected.

また、図５に変形例を示す。このキャップ２１は、耐食性を有する鋼板、例えば、オーステナイト系ステンレス鋼板、あるいは、防錆処理された冷間圧延鋼板からプレス加工にて形成され、外方部材２の端部外周に圧入される円筒状の嵌合部１４と、この嵌合部１４の一方の端部から径方向外方に折曲された鍔部１５と、嵌合部１５の他方の端部から径方向内方に延びる折曲部２１ａとを備えている。ここで、この折曲部２１ａの内径と外方部材２の端部内径との径差Ｌが０．３ｍｍ（片側）以上に設定されている。これにより、図６に示すように、キャップ２１を外方部材２に圧入治具２２によって圧入する時、外方部材２の端面２ｃを基準に位置決めすることができ、精度良く、かつ容易にキャップ２１を外方部材２に固定することができる。   FIG. 5 shows a modification. The cap 21 is formed of a steel plate having corrosion resistance, such as an austenitic stainless steel plate, or a cold-rolled steel plate that has been rust-proofed by press working, and is pressed into the outer periphery of the end of the outer member 2. The fitting portion 14, a flange 15 bent radially outward from one end of the fitting portion 14, and a bent extending radially inward from the other end of the fitting portion 15. Part 21a. Here, the diameter difference L between the inner diameter of the bent portion 21a and the inner diameter of the end portion of the outer member 2 is set to 0.3 mm (one side) or more. Thereby, as shown in FIG. 6, when the cap 21 is press-fitted into the outer member 2 by the press-fitting jig 22, the end surface 2c of the outer member 2 can be positioned as a reference, and the cap can be accurately and easily 21 can be fixed to the outer member 2.

また、図７に変形例を示す。ここでは、外方部材２’のアウター側の端部外周に環状の嵌合溝２３が形成されている。そして、この嵌合溝２３の段部２３ａにキャップ２１の鍔部１５を衝合させることにより、キャップ２１を外方部材２’に精度良く、かつ容易に位置決め固定することができる。   FIG. 7 shows a modification. Here, an annular fitting groove 23 is formed on the outer periphery of the outer end portion of the outer member 2 ′. Then, the cap 21 can be positioned and fixed to the outer member 2 ′ with high accuracy and easily by engaging the flange portion 15 of the cap 21 with the step portion 23 a of the fitting groove 23.

図８にハブ輪４の変形例を示す。なお、前述した実施形態と基本的にはハブ輪２４が異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符合を付して詳細な説明を省略する。   FIG. 8 shows a modification of the hub wheel 4. It should be noted that the hub wheel 24 is basically different from the above-described embodiment, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals and detailed description thereof is omitted.

車輪取付フランジ６のインナー側の側面６ｃとハブ輪２４の基部６ｂとの間に段部２５が形成されている。この段部２５には環状溝２５ａが形成され、キャップ２１の折曲部２１ａの内縁との間に僅かな径方向すきまを介して対向し、ラビリンス２０が構成されている。これにより、シール８から漏洩したグリースあるいはオイルがハブ輪２４の回転に伴う遠心力によって飛散しても、このキャップ２１側へ誘導させて路面側に流出させることができる。   A step portion 25 is formed between the inner side surface 6 c of the wheel mounting flange 6 and the base portion 6 b of the hub wheel 24. An annular groove 25 a is formed in the step portion 25, and the labyrinth 20 is configured to face the inner edge of the bent portion 21 a of the cap 21 via a slight radial clearance. Thereby, even if the grease or oil leaked from the seal 8 is scattered by the centrifugal force accompanying the rotation of the hub wheel 24, it can be guided to the cap 21 side and flow out to the road surface side.

次に、ハブ輪２４の硬化層パターンを説明する。図９に示すように、ハブ輪２４は、車輪取付フランジ６のインナー側の側面６ｃの根元部から小径段部（図示せず）に亙って高周波焼入れによって所定の硬化層２６が形成されている。すなわち、この硬化層２６の範囲を段部２５の環状溝２５ａを越えて車輪取付フランジ６のインナー側の側面６ｃの根元部に亙って形成することにより、車輪取付フランジ６を介して繰り返しモーメント荷重がハブ輪２４に負荷され、環状溝２５ａに応力が集中しても充分な強度を確保することができる。   Next, the hardened layer pattern of the hub wheel 24 will be described. As shown in FIG. 9, the hub wheel 24 has a predetermined hardened layer 26 formed by induction hardening from a root portion of the side surface 6 c on the inner side of the wheel mounting flange 6 to a small diameter step portion (not shown). Yes. That is, by forming the range of the hardened layer 26 over the root portion of the inner side surface 6c of the wheel mounting flange 6 beyond the annular groove 25a of the step portion 25, the repeated moment through the wheel mounting flange 6 is achieved. Even if a load is applied to the hub wheel 24 and stress concentrates on the annular groove 25a, sufficient strength can be ensured.

また、図１０に示すように、ハブ輪２４の段部２５の角部に面取り部２７を形成することにより、高周波焼入れの際に、角部が昇温して溶損したり、また、脆性化して欠損したりするのを防止することができる。   Further, as shown in FIG. 10, by forming a chamfered portion 27 at the corner portion of the step portion 25 of the hub wheel 24, the corner portion is heated and melted during induction hardening or becomes brittle. Can be prevented from being lost.

図１１は、図２の変形例を示す。なお、前述した実施形態と基本的にはディフレクタの有無が異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符合を付して詳細な説明を省略する。   FIG. 11 shows a modification of FIG. It should be noted that, basically, only the presence or absence of the deflector is different from the above-described embodiment, and the same parts are denoted by the same reference numerals, and detailed description thereof is omitted.

アウター側のシール８は、サイドリップ１２ａ、１２ｂおよびグリースリップ１２ｃを備えている。これらのサイドリップ１２ａ、１２ｂおよびグリースリップ１２ｃは、車輪取付フランジ６のインナー側の基部６ｂに嵌着されたディフレクタ２８に摺接されている。   The outer seal 8 includes side lips 12a and 12b and a grease lip 12c. These side lips 12 a and 12 b and the grease lip 12 c are in sliding contact with a deflector 28 fitted to the base 6 b on the inner side of the wheel mounting flange 6.

ディフレクタ２８は、耐食性を有する鋼板、例えば、オーステナイト系ステンレス鋼板、あるいは、防錆処理された冷間圧延鋼板からプレス加工にて形成され、ハブ輪４の基部６ｂに外嵌される円筒状の嵌合部２８ａと、円弧状に形成された基部６ｂに対応して円弧状に形成された湾曲部２８ｂと、この湾曲部２８ｂから径方向外方に延び、段部１９の側面１９ａに密着される円板部２８ｃとを備えている。そして、円板部２８ｃは段部１９の最外径部よりも突出して形成され、キャップ１３の折曲部１６との間で、ラビリンス２０を構成している。   The deflector 28 is formed by press working from a corrosion-resistant steel plate, such as an austenitic stainless steel plate, or a cold-rolled steel plate that has been rust-proofed, and is fitted into a cylindrical fitting that is externally fitted to the base portion 6 b of the hub wheel 4. A joint portion 28a, a curved portion 28b formed in an arc shape corresponding to the base portion 6b formed in an arc shape, and extends radially outward from the curved portion 28b, and is in close contact with the side surface 19a of the step portion 19. And a disc portion 28c. The disc portion 28 c is formed so as to protrude from the outermost diameter portion of the step portion 19, and constitutes the labyrinth 20 with the bent portion 16 of the cap 13.

このディフレクタ２８は、素材となる鋼板の表面粗さがＲａ０．２〜０．６の範囲に設定され、表面にショットブラスト処理によって無数のディンプルが形成され、表面が粗面化処理、具体的には、Ｒａ１．０〜５．０の範囲に形成されている。このディンプルは、図示はしないが、ディフレクタ２８を回転治具に載置させると共に、ショットブラスト用のノズルをディフレクタ２８に対向させた状態で、回転治具を旋回させ、スチールビーズ等のメディアを噴射させることにより行われる。ここで、スチールビーズの粒径は２０〜１００μｍ、噴射時間は約９０秒、噴射圧は１〜３ｋｇ／ｃｍ２の条件でノズルを所定範囲に移動させながらショットブラスト加工が施される。これにより、良好なシール摺接面を得ることができ、リップ摩耗を抑制すると共に、劣悪な環境で使用されても、シール８の密封性能の維持を図ることができる。なお、Ｒａは、ＪＩＳの粗さ形状パラメータの一つで（ＪＩＳ Ｂ０６０１−１９９４）、算術平均粗さのことで、平均線から絶対値偏差の平均値を言う。 In this deflector 28, the surface roughness of the steel plate as the material is set in the range of Ra 0.2 to 0.6, and innumerable dimples are formed on the surface by shot blasting, and the surface is roughened. Is formed in the range of Ra 1.0 to 5.0. Although not shown, this dimple is placed with the deflector 28 placed on the rotating jig, and with the shot blast nozzle facing the deflector 28, the rotating jig is swung to eject media such as steel beads. Is done. Here, shot blasting is performed while moving the nozzle to a predetermined range under the conditions that the particle size of the steel beads is 20 to 100 μm, the injection time is about 90 seconds, and the injection pressure is 1 to 3 kg / cm 2 . Thereby, a favorable seal sliding contact surface can be obtained, lip wear can be suppressed, and the sealing performance of the seal 8 can be maintained even when used in a poor environment. Note that Ra is one of JIS roughness shape parameters (JIS B0601-1994), and is an arithmetic average roughness, which means an average value of absolute value deviations from an average line.

基部６ｂは所定の曲率半径ｒからなる円弧面に形成され、この円弧面に対応して、ディフレクタ２８の湾曲部２８ｂは所定の曲率半径Ｒからなる円弧面からなる。そして、それぞれの曲率半径Ｒ、ｒがＲ＞ｒになるように設定されている。これにより、ディフレクタ２８を基部６ｂに嵌合した時に基部６ｂの円弧面にディフレクタ２８の湾曲部２８ｂが干渉して浮き上がるのを防止でき、段部１９の側面１９ａとディフレクタ２８の円板部２８ｃとの間に隙間が生じるのが防止されて両者が密着し、サイドリップ１２ａ、１２ｂのシメシロのバラツキを抑えて安定した密封性を確保することができる。   The base portion 6b is formed on an arc surface having a predetermined radius of curvature r, and the curved portion 28b of the deflector 28 is formed of an arc surface having a predetermined radius of curvature R corresponding to the arc surface. The curvature radii R and r are set so that R> r. Thus, when the deflector 28 is fitted to the base portion 6b, the curved portion 28b of the deflector 28 can be prevented from interfering with the arc surface of the base portion 6b and lifted, and the side surface 19a of the step portion 19 and the disc portion 28c of the deflector 28 can be prevented. It is possible to prevent a gap from being formed between the two, and to bring them into close contact with each other, thereby suppressing the unevenness of the side lips 12a and 12b and ensuring a stable sealing performance.

さらに、本実施形態では、ディフレクタ２８の円板部２８ｃの先端部に加硫接着等により弾性部材（パッキン）２９が一体に接合されている。この弾性部材２９はＮＢＲ等の合成ゴムからなり、段部１９の側面１９ａに弾性接触している。これにより、段部（基部）１９の側面１９ａとディフレクタ２８の円板部２８ｃとの間にすきまが生じるのを確実に防止することができ、当部から泥水等がディフレクタ２８に浸漬し、ハブ輪４の基部６ｂが発錆するのを防止することができる。   Further, in the present embodiment, an elastic member (packing) 29 is integrally joined to the distal end portion of the disc portion 28c of the deflector 28 by vulcanization adhesion or the like. The elastic member 29 is made of synthetic rubber such as NBR, and is in elastic contact with the side surface 19 a of the stepped portion 19. As a result, it is possible to reliably prevent a gap between the side surface 19a of the stepped portion (base portion) 19 and the disk portion 28c of the deflector 28, and muddy water or the like is immersed in the deflector 28 from this portion, and the hub The base portion 6b of the ring 4 can be prevented from rusting.

図１２は、前述したディフレクタ２８の変形例である。なお、前述した実施形態と基本的にはディフレクタの構成が一部異なるだけで、その他同一部品同一部位あるいは同様の機能を有する部品や部位には同じ符合を付して詳細な説明を省略する。   FIG. 12 shows a modified example of the deflector 28 described above. It should be noted that, basically, the configuration of the deflector is only partially different from that of the above-described embodiment, and the same reference numerals are given to the same parts having the same parts or parts having the same functions, and detailed description thereof is omitted.

アウター側のシール８は、サイドリップ１２ａ、１２ｂおよびグリースリップ１２ｃを備えている。これらのサイドリップ１２ａ、１２ｂおよびグリースリップ１２ｃは、車輪取付フランジ６のインナー側の基部６ｂに嵌着されたディフレクタ３０に摺接されている。   The outer seal 8 includes side lips 12a and 12b and a grease lip 12c. These side lips 12 a and 12 b and the grease lip 12 c are in sliding contact with a deflector 30 fitted to the base portion 6 b on the inner side of the wheel mounting flange 6.

ディフレクタ３０は、耐食性を有する鋼板、例えば、オーステナイト系ステンレス鋼板、あるいは、防錆処理された冷間圧延鋼板からプレス加工にて形成され、ハブ輪４の基部６ｂに外嵌される円筒状の嵌合部２８ａと、円弧状に形成された基部６ｂに対応して円弧状に形成された湾曲部２８ｂと、この湾曲部２８ｂから径方向外方に延び、段部１９の側面１９ａに密着される円板部３０ａとを備えている。そして、円板部３０ａは段部１９の最外径部よりも突出して軸受側（インナー側）に湾曲して形成され、キャップ１３の折曲部１６との間で、ラビリンス２０を構成している。   The deflector 30 is formed by press working from a corrosion-resistant steel plate, such as an austenitic stainless steel plate or a rust-proof cold-rolled steel plate, and is fitted into a cylindrical fitting that is externally fitted to the base portion 6 b of the hub wheel 4. A joint portion 28a, a curved portion 28b formed in an arc shape corresponding to the base portion 6b formed in an arc shape, and extends radially outward from the curved portion 28b, and is in close contact with the side surface 19a of the step portion 19. And a disc portion 30a. And the disc part 30a protrudes rather than the outermost diameter part of the step part 19, is curved and formed in the bearing side (inner side), and comprises the labyrinth 20 between the bending parts 16 of the cap 13. Yes.

本実施形態では、ディフレクタ３０の円板部３０ａの先端部に加硫接着等により弾性部材３１が一体に接合されている。この弾性部材３１はＮＢＲ等の合成ゴムからなり、段部１９の側面１９ａに弾性接触している。これにより、段部（基部）１９の側面１９ａとディフレクタ２８の円板部３０ａとの間にすきまが生じるのを確実に防止することができ、当部から泥水等がディフレクタ３０に浸漬し、ハブ輪４の基部６ｂが発錆するのを防止することができると共に、外方部材２とのすきまを小さくすることができ、外部から浸入した泥水等がシール８への浸入を防止するだけでなく、シール８から漏洩したグリースあるいはオイルがハブ輪４の回転に伴う遠心力によって飛散しても、このキャップ１３側へ誘導させて路面側に流出させることができる。   In the present embodiment, the elastic member 31 is integrally joined to the distal end portion of the disc portion 30a of the deflector 30 by vulcanization adhesion or the like. The elastic member 31 is made of synthetic rubber such as NBR, and is in elastic contact with the side surface 19 a of the stepped portion 19. As a result, it is possible to reliably prevent a gap between the side surface 19a of the stepped portion (base portion) 19 and the disc portion 30a of the deflector 28, and muddy water or the like is immersed in the deflector 30 from this portion. The base 6b of the wheel 4 can be prevented from rusting, and the clearance with the outer member 2 can be reduced, and not only the muddy water entering from the outside prevents the intrusion into the seal 8. Even if the grease or oil leaked from the seal 8 is scattered due to the centrifugal force accompanying the rotation of the hub wheel 4, it can be guided to the cap 13 side and flow out to the road surface side.

図１３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、図１４は、図１３のアウター側のシール部を示す要部拡大図である。なお、この実施形態は、前述した実施形態（図１）と基本的には軸受構造が異なるだけで、その他同一部品同一部位あるいは同様の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. 13 is a longitudinal sectional view showing a second embodiment of the wheel bearing device according to the present invention, and FIG. 14 is an enlarged view of a main part showing a seal part on the outer side of FIG. This embodiment is basically different from the above-described embodiment (FIG. 1) only in the bearing structure, and other parts and parts having the same parts or parts having the same functions are denoted by the same reference numerals. The detailed explanation is omitted.

図１３に示す車輪用軸受装置は第２世代と呼称され、ハブ輪３２と、このハブ輪３２に固定された車輪用軸受３３を備えている。車輪用軸受３３は、外周に車体取付フランジ２ｂを一体に有し、内周に外向きに開いたテーパ状の複列の外側転走面３４ａ、３４ａが形成された外方部材３４と、外周に前記複列の外側転走面３４ａ、３４ａに対向するテーパ状の内側転走面３５ａが形成された一対の内輪３５、３５’と、両転走面間に収容された複列の円錐ころ３６、３６と、これらの円錐ころ３６を転動自在に保持する保持器３７、３７と、外方部材３４の両端部に装着されたシール９、９’とを備え、一対の内輪３５、３５’の正面側端面が突き合された状態でセットされた背面合せタイプの複列の円錐ころ軸受を構成している。   The wheel bearing device shown in FIG. 13 is called the second generation, and includes a hub wheel 32 and a wheel bearing 33 fixed to the hub wheel 32. The wheel bearing 33 has an outer member 34 integrally formed with a vehicle body mounting flange 2b on the outer periphery and formed with tapered double-row outer rolling surfaces 34a, 34a opened outward on the inner periphery. A pair of inner rings 35, 35 'formed with a tapered inner rolling surface 35a facing the double row outer rolling surfaces 34a, 34a, and a double row tapered roller accommodated between both rolling surfaces. 36, 36, retainers 37, 37 for holding these tapered rollers 36 in a rollable manner, and seals 9, 9 'mounted on both ends of the outer member 34, and a pair of inner rings 35, 35 This is a back-to-back type double row tapered roller bearing set with the end face of the front side butted.

ハブ輪３２は、アウター側の端部に車輪取付フランジ６を一体に有し、この車輪取付フランジ６から肩部（基部）３２ａを介して軸方向に延びる軸部３２ｂが形成され、内周に駆動軸が係合するセレーション４ｃが形成されている。   The hub wheel 32 integrally has a wheel mounting flange 6 at an end portion on the outer side, and a shaft portion 32b extending in the axial direction from the wheel mounting flange 6 via a shoulder portion (base portion) 32a is formed on the inner periphery. A serration 4c with which the drive shaft engages is formed.

内輪３５、３５’は、外周に内側転走面３５ａが形成され、ハブ輪３２の軸部３２ｂに所定のシメシロを介して圧入され、軸部３２ｂの端部を径方向外方に塑性変形させて形成した加締部４ｄによって所定の軸受予圧が付与された状態でハブ輪３２に対して軸方向に固定されている。すなわち、このハブ輪３２と、このハブ輪３２の軸部３２ｂに圧入された一対の内輪３５、３５’をもって内方部材３８と言う。   The inner races 35 and 35 ′ are formed with an inner rolling surface 35 a on the outer periphery, and are press-fitted into the shaft portion 32 b of the hub wheel 32 through a predetermined shimoshiro to cause the end portion of the shaft portion 32 b to be plastically deformed radially outward. It is fixed to the hub wheel 32 in the axial direction in a state where a predetermined bearing preload is applied by the caulking portion 4d formed in this manner. That is, the hub ring 32 and the pair of inner rings 35 and 35 ′ press-fitted into the shaft portion 32 b of the hub ring 32 are referred to as the inner member 38.

内輪３５、３５’の内側転走面３５ａの大径側端部には大鍔部（案内鍔）３５ｂが形成され、円錐ころ３６の大端面を案内している。また、内側転走面３５ａの小径側端部には径方向外方に突出する小鍔部３５ｃが形成され、円錐ころ３６が脱落するのを防止している。なお、内輪３５、３５’のうちアウター側の内輪３５’は、インナー側の内輪３５と基本的にはハブ輪３２の肩部３２ａの面取り部に対応する面取り部の大きさが異なるだけである。   A large collar portion (guide rod) 35b is formed at the large diameter side end portion of the inner raceway 35a of the inner ring 35, 35 ', and guides the large end surface of the tapered roller 36. Further, a small flange portion 35c protruding outward in the radial direction is formed at the small diameter side end portion of the inner rolling surface 35a to prevent the tapered roller 36 from falling off. Of the inner rings 35, 35 ′, the inner ring 35 ′ on the outer side basically differs from the inner ring 35 on the inner side only in the size of the chamfered portion corresponding to the chamfered portion of the shoulder portion 32 a of the hub ring 32. .

ハブ輪３２はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、肩部３２ａから軸部３２ｂに亙って高周波焼入れによって表面硬さを５０〜６４ＨＲＣの範囲に硬化処理されている。   The hub wheel 32 is made of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and hardened to a surface hardness of 50 to 64 HRC by induction hardening from the shoulder portion 32a to the shaft portion 32b. Has been processed.

外方部材３４はＳ５３Ｃ等の炭素０．４０〜０．８０ｗｔ％を含む中高炭素鋼で形成され、少なくとも複列の外側転走面３４ａ、３４ａ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。一方、内輪３５、３５’および円錐ころ３６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 outer member 34 is formed of medium and high carbon steel containing 0.40 to 0.80 wt% of carbon such as S53C, and at least the double row outer rolling surfaces 34a and 34a have a surface hardness in the range of 58 to 64HRC by induction hardening. Has been cured. On the other hand, the inner rings 35, 35 ′ and the tapered roller 36 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.

ここで、本実施形態では、前述した実施形態と同様、外方部材３４のアウター側の端部外周にキャップ１３が装着されている。このキャップ１３は、外方部材３４の端部外周に圧入される円筒状の嵌合部１４と、この嵌合部１４の一方（インナー側）の端部から径方向外方に折曲された鍔部１５と、嵌合部１５の他方（アウター側）の端部から径方向内方に延びる折曲部１６とを備えている。そして、この折曲部１６の路面側に最も近い部分にポケット部１７が設けられ、このポケット部１７から軸方向に延びる樋部１８が一体に形成されている。   Here, in this embodiment, the cap 13 is attached to the outer periphery of the outer end portion of the outer member 34 as in the above-described embodiment. The cap 13 is bent radially outward from one end (inner side) of the cylindrical fitting portion 14 which is press-fitted into the outer periphery of the end portion of the outer member 34. A flange portion 15 and a bent portion 16 that extends radially inward from the other end (outer side) of the fitting portion 15 are provided. And the pocket part 17 is provided in the part nearest to the road surface side of this bending part 16, and the collar part 18 extended from this pocket part 17 to an axial direction is integrally formed.

図１４に示すように、車輪取付フランジ６のインナー側の側面６ｃと肩部３２ａとの間には段部１９が形成されている。この段部１９は、肩部３２ａの最外径部から車輪取付フランジ６の側面６ｃに亙って滑らかな円弧状の曲面に形成され、キャップ１３の折曲部１６の内縁との間に僅かな径方向すきまＣを介して対向し、ラビリンス２０が構成されている。これにより、シール８から漏洩したグリースあるいはオイルがハブ輪３２の回転に伴う遠心力によって飛散しても、このキャップ１３で集めて路面側（図１３の下側）に流出させることができる。   As shown in FIG. 14, a step portion 19 is formed between the inner side surface 6c of the wheel mounting flange 6 and the shoulder portion 32a. The step portion 19 is formed into a smooth arcuate curved surface from the outermost diameter portion of the shoulder portion 32 a to the side surface 6 c of the wheel mounting flange 6, and is slightly between the inner edge of the bent portion 16 of the cap 13. The labyrinth 20 is configured to face each other with a small radial clearance C. Thereby, even if the grease or oil leaked from the seal 8 is scattered by the centrifugal force accompanying the rotation of the hub wheel 32, it can be collected by the cap 13 and discharged to the road surface side (lower side in FIG. 13).

本実施形態においても、前述した実施形態と同様、キャップ１３から流出してきたグリースあるいはオイルをポケット部１７で回収し、このポケット部１７から樋部１８を介して外部にスムーズに排出させることができ（図１３参照）、排出されたグリースあるいはオイルが遠心力によって飛散したとしてもブレーキ部品に付着することがなく、ブレーキ性能に悪影響を及ぼすのを確実に防止することができる。   Also in this embodiment, the grease or oil that has flowed out of the cap 13 can be collected in the pocket portion 17 and can be smoothly discharged from the pocket portion 17 to the outside through the flange portion 18 as in the above-described embodiment. (Refer to FIG. 13) Even if the discharged grease or oil is scattered by centrifugal force, it does not adhere to the brake parts, and it is possible to reliably prevent the brake performance from being adversely affected.

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、軸受部の構造に拘わらず、駆動軸と車軸管の開口部に車輪用軸受が装着された駆動輪側の車輪用軸受装置に適用できる。   The wheel bearing device according to the present invention can be applied to a wheel bearing device on the driving wheel side in which wheel bearings are mounted in openings of the drive shaft and the axle tube regardless of the structure of the bearing portion.

１、３８ 内方部材
２、２’、３４ 外方部材
２ａ、３４ａ 外側転走面
２ｂ 車体取付フランジ
２ｃ 外方部材のアウター側の端面
３ 転動体
４、２４、３２ ハブ輪
４ａ、５ａ、３５ａ 内側転走面
４ｂ 小径段部
４ｃ セレーション
４ｄ 加締部
５、３５、３５’ 内輪
６ 車輪取付フランジ
６ａ ハブボルト
６ｂ 車輪取付フランジのインナー側の基部
６ｃ 車輪取付フランジのインナー側の側面
７、３７ 保持器
８、９’ アウター側のシール
９ インナー側のシール
１０、１３、２１ キャップ
１０ａ、１１ 芯金
１０ｂ 弾性部材
１２ シール部材
１２ａ、１２ｂ サイドリップ
１２ｃ グリースリップ
１４、２８ａ 嵌合部
１５ 鍔部
１６、２１ａ 折曲部
１７ ポケット部
１７ａ 底部
１７ｂ 縁部
１８ 樋部
１８ａ 排出口
１９、２３ａ、２５ 段部
１９ａ 段部の側面
２０ ラビリンスシール
２２ 圧入治具
２３ 嵌合溝
２５ａ 環状溝
２６ 硬化層
２７ 面取り部
２８、３０ ディフレクタ
２８ｂ 湾曲部
２８ｃ、３０ａ 円板部
２９、３１ 弾性部材
３２ａ 肩部
３２ｂ 軸部
３３ 車輪用軸受
３５ｂ 大鍔部
３５ｃ 小鍔部
３６ 円錐ころ
５０ 車輪取付フランジ
５０ａ 基部
５０ｂ 側面
５１ 金属環
５１ａ 嵌合部
５１ｂ 湾曲部
５１ｃ 円板部
５１ｄ 傘部
５１ｅ 折曲部
５２ シール
５３ 外方部材
５４ 芯金
５５ シール部材
５５ａ、５５ｂ サイドリップ
５５ｃ グリースリップ
５６ ハブ輪
５６ａ 肩部
５７ 排水孔
５８ キャップ
５８ａ 円筒部
５８ｂ 立板部
Ａ 環状のすきま
Ｂ 軸方向すきま
Ｃ ラビリンスの径方向すきま
Ｌ キャップの折曲部の内径と外方部材の端部内径との径差
ｒ 基部の曲率半径
Ｒ 金属環の湾曲部の曲率半径 DESCRIPTION OF SYMBOLS 1,38 Inner member 2, 2 ', 34 Outer member 2a, 34a Outer rolling surface 2b Car body mounting flange 2c Outer member outer side end surface 3 Rolling elements 4, 24, 32 Hub wheel 4a, 5a, 35a Inner rolling surface 4b Small diameter step portion 4c Serration 4d Clamping portion 5, 35, 35 'Inner ring 6 Wheel mounting flange 6a Hub bolt 6b Inner side base 6c of wheel mounting flange Side surface 7, 37 of inner side of wheel mounting flange 8, 9 'Outer side seal 9 Inner side seal 10, 13, 21 Cap 10a, 11 Core metal 10b Elastic member 12 Seal member 12a, 12b Side lip 12c Grease lip 14, 28a Fitting part 15 Gutter part 16, 21a Folded portion 17 Pocket portion 17a Bottom portion 17b Edge portion 18 Gutter portion 18a Discharge port 19, 23a, 25 Step portion 19a Step portion side surface 20 Biling seal 22 Press fitting jig 23 Fitting groove 25a Annular groove 26 Hardened layer 27 Chamfered portion 28, 30 Deflector 28b Curved portion 28c, 30a Disk portion 29, 31 Elastic member 32a Shoulder portion 32b Shaft portion 33 Wheel bearing 35b Large collar portion 35c Small flange portion 36 Tapered roller 50 Wheel mounting flange 50a Base portion 50b Side surface 51 Metal ring 51a Fitting portion 51b Curved portion 51c Disk portion 51d Umbrella portion 51e Bending portion 52 Seal 53 Outer member 54 Core metal 55 Seal member 55a, 55b Side lip 55c Grease lip 56 Hub ring 56a Shoulder 57 Drainage hole 58 Cap 58a Cylindrical part 58b Standing plate A Annular clearance B Axial clearance C Labyrinth radial clearance L Inner diameter of cap and outer member The difference in diameter from the inner diameter of the end r of the base R of curvature R

Claims (12)

外周に車体取付フランジを一体に有し、内周に複列の外側転走面が一体に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所定のシメシロを介して圧入され、外周に前記複列の外側転走面に対向する内側転走面が形成された少なくとも一つの内輪からなる内方部材と、
この内方部材と前記外方部材の両転走面間に保持器を介して転動自在に収容された複列の転動体と、
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両側開口部に装着されたシールとを備え、
これらシールのうちアウター側のシールが、前記外方部材の端部内周に嵌合される芯金と、この芯金に一体に接合され、径方向外方に傾斜して延びるサイドリップと、軸受内方側に傾斜して延びるグリースリップとを有するシール部材からなる一体型のシールで構成された車輪用軸受装置において、
前記外方部材のアウター側の端部外周に円環状のキャップが装着され、このキャップが、前記外方部材の端部外周に圧入される円筒状の嵌合部と、この嵌合部の一端部から径方向内方に延びる折曲部を備え、この折曲部の路面側にポケット部が設けられ、このポケット部から軸方向に延びる樋部が一体に形成されていることを特徴とする車輪用軸受装置。 An outer member integrally including a vehicle body mounting flange on the outer periphery, and a double row outer rolling surface formed integrally on the inner periphery;
A hub wheel integrally having a wheel mounting flange for mounting a wheel at one end and a small-diameter step portion extending in the axial direction on the outer periphery, and a small-diameter step portion of this hub wheel are press-fitted through a predetermined shimoshiro An inner member composed of at least one inner ring formed with an inner rolling surface facing the outer rolling surface of the double row on the outer periphery;
A double row rolling element housed between the rolling surfaces of the inner member and the outer member so as to be freely rollable via a cage;
A seal mounted on both side openings of an annular space formed between the outer member and the inner member;
Outer seal among these seals is a core metal fitted to the inner periphery of the end of the outer member, a side lip that is integrally joined to the core metal and extends obliquely outward in the radial direction, and a bearing In the wheel bearing device constituted by an integral seal composed of a seal member having a grease lip extending inclinedly inwardly,
An annular cap is attached to the outer periphery of the outer side end of the outer member, and the cap is fitted into a cylindrical fitting portion that is press-fitted into the outer periphery of the outer member, and one end of the fitting portion. A bent portion extending radially inward from the portion, a pocket portion is provided on the road surface side of the bent portion, and a flange portion extending in the axial direction from the pocket portion is integrally formed. Wheel bearing device. 前記樋部の先端部が前記車体取付フランジよりもインナー側に開口するように設定されている請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein a distal end portion of the flange portion is set so as to open to an inner side of the vehicle body mounting flange. 前記ポケット部の底部が、前記嵌合部の一部が拡径し、インナー側に所定の傾斜角だけ広がるテーパ状に形成されている請求項１に記載の車輪用軸受装置。   2. The wheel bearing device according to claim 1, wherein a bottom portion of the pocket portion is formed in a tapered shape in which a part of the fitting portion is enlarged in diameter and widened by a predetermined inclination angle toward the inner side. 前記車輪取付フランジのインナー側の側面と基部との間には段部が形成され、この段部と前記キャップの折曲部の内縁が僅かな径方向すきまを介して対向し、ラビリンスが構成されている請求項１に記載の車輪用軸受装置。   A step portion is formed between the inner side surface of the wheel mounting flange and the base portion, and the inner edge of the step portion and the bent portion of the cap are opposed to each other through a slight radial clearance to form a labyrinth. The wheel bearing device according to claim 1. 前記ラビリンスの径方向すきまが直径で０．３〜３．０ｍｍの範囲に設定されている請求項４に記載の車輪用軸受装置。   The wheel bearing device according to claim 4, wherein a radial clearance of the labyrinth is set in a range of 0.3 to 3.0 mm in diameter. 前記キャップの折曲部の内径と前記外方部材の端部内径との径差が片側で０．３ｍｍ以上に設定されている請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein a diameter difference between an inner diameter of the bent portion of the cap and an inner diameter of the end portion of the outer member is set to 0.3 mm or more on one side. 前記ハブ輪の段部に環状溝が形成されている請求項１に記載の車輪用軸受装置。   The wheel bearing device according to claim 1, wherein an annular groove is formed in a step portion of the hub wheel. 前記ハブ輪の外周に、前記車輪取付フランジのインナー側の側面の根元部から前記小径段部に亙って高周波焼入れによって所定の硬化層が形成されている請求項７に記載の車輪用軸受装置。   The wheel bearing device according to claim 7, wherein a predetermined hardened layer is formed on the outer periphery of the hub wheel by induction hardening from a root portion on the inner side surface of the wheel mounting flange to the small diameter step portion. . 前記車輪取付フランジのインナー側の基部が所定の曲率半径ｒからなる円弧状に形成され、この基部に鋼板からプレス加工にて形成されたディフレクタが嵌着され、このディフレクタが、前記ハブ輪の肩部に外嵌される円筒状の嵌合部と、前記基部の形状に対応して円弧状に形成された湾曲部と、この湾曲部から径方向外方に延び、前記基部の側面に密着される円板部とを備え、前記シール部材の少なくともサイドリップが前記ディフレクタに摺接されると共に、前記ディフレクタの湾曲部が前記基部の円弧面に対応して所定の曲率半径Ｒからなる円弧面に形成され、それぞれの曲率半径Ｒ、ｒが、Ｒ＞ｒになるように設定されている請求項１に記載の車輪用軸受装置。   A base portion on the inner side of the wheel mounting flange is formed in an arc shape having a predetermined radius of curvature r, and a deflector formed by press working from a steel plate is fitted to the base portion, and this deflector is connected to the shoulder of the hub wheel. A cylindrical fitting portion that is externally fitted to the portion, a curved portion that is formed in an arc shape corresponding to the shape of the base portion, extends radially outward from the curved portion, and is in close contact with the side surface of the base portion And at least a side lip of the seal member is slidably contacted with the deflector, and a curved portion of the deflector has an arc surface having a predetermined radius of curvature R corresponding to the arc surface of the base portion. The wheel bearing device according to claim 1, wherein the wheel radii of curvature R and r are formed such that R> r. 前記ディフレクタの円板部が前記段部の最外径部よりも突出して形成されている請求項９に記載の車輪用軸受装置。   The wheel bearing device according to claim 9, wherein a disk portion of the deflector is formed so as to protrude from an outermost diameter portion of the stepped portion. 前記ディフレクタの円板部の先端部に加硫接着により弾性部材が一体に接合され、この弾性部材が前記基部の側面に弾性接触している請求項９または１０に記載の車輪用軸受装置。   11. The wheel bearing device according to claim 9, wherein an elastic member is integrally joined to a distal end portion of the disc portion of the deflector by vulcanization adhesion, and the elastic member is in elastic contact with a side surface of the base portion. 前記ディフレクタが、その表面にショットブラスト処理によって無数のディンプルが形成され、表面粗さがＲａ１．０〜５．０の範囲に粗面化処理されている請求項９乃至１１いずれかに記載の車輪用軸受装置。   The wheel according to any one of claims 9 to 11, wherein an infinite number of dimples are formed on the surface of the deflector by shot blasting, and the surface roughness is roughened in a range of Ra 1.0 to 5.0. Bearing device.
JP2012097833A 2012-04-23 2012-04-23 Bearing device for wheel Pending JP2013224718A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015119215A1 (en) * 2014-02-05 2015-08-13 Ntn株式会社 Bearing device for wheel
WO2018117102A1 (en) * 2016-12-21 2018-06-28 Nok株式会社 Sealing device

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015119215A1 (en) * 2014-02-05 2015-08-13 Ntn株式会社 Bearing device for wheel
WO2018117102A1 (en) * 2016-12-21 2018-06-28 Nok株式会社 Sealing device
CN110088492A (en) * 2016-12-21 2019-08-02 Nok株式会社 Sealing device
US10948017B2 (en) 2016-12-21 2021-03-16 Nok Corporation Sealing device

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