JP2010144923A - Inner ring of rolling bearing, and bearing device for wheel equipped with the same - Google Patents

Inner ring of rolling bearing, and bearing device for wheel equipped with the same Download PDF

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JP2010144923A
JP2010144923A JP2008326402A JP2008326402A JP2010144923A JP 2010144923 A JP2010144923 A JP 2010144923A JP 2008326402 A JP2008326402 A JP 2008326402A JP 2008326402 A JP2008326402 A JP 2008326402A JP 2010144923 A JP2010144923 A JP 2010144923A
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Prior art keywords
inner ring
end surface
large end
rolling
wheel
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JP2008326402A
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JP5227158B2 (en
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Takayuki Kowada
貴之 小和田
Takayasu Takubo
孝康 田窪
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • 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
    • 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)
  • Grinding Of Cylindrical And Plane Surfaces (AREA)
  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide an inner ring for a rolling bearing, improved in durability by preventing a grinding burn of the inner ring, and a bearing device for a wheel equipped with the inner ring for the rolling bearing. <P>SOLUTION: The bearing device for the wheel includes the inner ring 3 axially fixed to a hub wheel 2 with a caulking part 2c formed by plastically deforming a small-diameter step 2b of the hub wheel 2 radially outward. An annular recess 11 is formed at the large end face 3b of the inner ring 3. The radial dimensions of a chamfer part on the large end face 3b side and a chamfer part on the small end face 3c side are set to predetermined values, and the area of the large end face 3b and the area of the small end face 3c of the inner ring 3 are set to substantially the same. The depth of the recess 11 is larger than a grinding allowance and set in a range of 0.15-1.0 mm. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、自動車等の車輪を懸架装置に対して回転自在に支承する転がり軸受、特に、内輪の研削焼けを防止して耐久性の向上を図った転がり軸受の内輪およびそれを備えた車輪用軸受装置に関するものである。   The present invention relates to a rolling bearing that rotatably supports a wheel of an automobile or the like with respect to a suspension device, and more particularly to an inner ring of a rolling bearing that prevents grinding and burning of an inner ring and improves durability, and a wheel having the same. The present invention relates to a bearing device.

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、この転がり軸受には、一般的に、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. Generally, the rolling bearing has a desired bearing rigidity. A double-row angular contact ball bearing that exhibits durability against misalignment and has low rotational torque is often used from the viewpoint of improving fuel efficiency. 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.

例えば、複列アンギュラ玉軸受の内輪は、一般的に両頭平面研削盤等によって両端面が同時に研削加工されている。図１０に示すように、この内輪５０は、外周に円弧状の内側転走面５０ａが形成されると共に、この内側転走面５０ａの一方側に大径側となる肩部５１が形成され、他方側に小径側となるカウンタ部５２が形成されている。ここで、肩部５１側の大端面（背面側端面）５３とカウンタ部５２側の小端面（正面側端面）５４が同時に研削加工される場合、大端面５３と小端面５４の面積比Ａ１／Ａ２が大きく異なるため、加工時の研削抵抗も大きく異なることになる。加工条件によっては、強研削により研削焼けが発生する恐れがある。   For example, the inner ring of a double row angular contact ball bearing is generally ground at both ends at the same time by a double-head surface grinder or the like. As shown in FIG. 10, the inner ring 50 has an arcuate inner rolling surface 50a formed on the outer periphery thereof, and a shoulder 51 which is a large diameter side formed on one side of the inner rolling surface 50a. On the other side, a counter section 52 which is a small diameter side is formed. Here, when the large end surface (rear side end surface) 53 on the shoulder 51 side and the small end surface (front end surface) 54 on the counter unit 52 side are ground simultaneously, the area ratio A1 / of the large end surface 53 and the small end surface 54 is obtained. Since A2 is greatly different, the grinding resistance at the time of processing is also greatly different. Depending on the processing conditions, grinding burn may occur due to strong grinding.

この研削焼けが発生した場合、内輪５０には引張残留応力が発生している。こうした引張残留応力が発生した内輪５０を、例えば、図示しないが、ハブ輪の小径段部に圧入して、小径段部の端部を塑性変形させて形成した加締部によって内輪５０を固定した際、この揺動加締によって内輪５０にフープ応力が生じ、研削加工時の微小クラック等が内輪５０の割れや加工後の内輪割れ、所謂置き割れが発生する恐れがある。すなわち、研削加工時に内輪５０に発生した引張残留応力によって誘発された微小クラックを起点として割れに至る恐れがある。   When this grinding burn occurs, tensile residual stress is generated in the inner ring 50. For example, although not shown, the inner ring 50 in which such tensile residual stress is generated is press-fitted into a small-diameter step portion of the hub wheel, and the inner ring 50 is fixed by a crimping portion formed by plastic deformation of the end portion of the small-diameter step portion. At this time, the swing caulking causes a hoop stress in the inner ring 50, and there is a risk that micro cracks or the like at the time of grinding may crack the inner ring 50 or crack the inner ring after machining, so-called crack. That is, there is a risk of cracking starting from a microcrack induced by the tensile residual stress generated in the inner ring 50 during grinding.

こうした内輪５０の研削焼けを防止するために、研削条件を変更する等、種々の対策が講じられている。ここで、内輪５０の大端面５３と小端面５４の面積比Ａ１／Ａ２を小さく抑えることが考えられる。例えば、図１１に示す内輪５５には、その大端面５６に多数の窪み５７が形成されている。この窪み５７は、径方向と周方向に整列させて、それぞれ、所定間隔に分布されている。これらの窪み５７が吸音効果を発揮して、内輪５５の大端面５６と図示しない等速自在継手の外側継手部材との間から発生する異音を窪み５７により吸収することができるというものである（例えば、特許文献１参照。）。   In order to prevent such grinding burn of the inner ring 50, various countermeasures such as changing grinding conditions are taken. Here, it is conceivable to reduce the area ratio A1 / A2 between the large end surface 53 and the small end surface 54 of the inner ring 50. For example, the inner ring 55 shown in FIG. 11 has a number of depressions 57 formed on the large end surface 56 thereof. The dents 57 are aligned in the radial direction and the circumferential direction, and are distributed at predetermined intervals. These dents 57 exhibit a sound absorbing effect, and the dents 57 can absorb the noise generated between the large end surface 56 of the inner ring 55 and the outer joint member of the constant velocity universal joint (not shown). (For example, refer to Patent Document 1).

また、これらの窪み５７を内輪５５の大端面５６に形成することによって、目的が異なるものの、結果的にこの内輪５５の大端面５６と小端面５４の面積比Ａ３／Ａ２を小さく抑えることでき、研削加工時の研削抵抗が小さくなって研削焼けを防止することができる。
特開２００５−７５２２９号公報 Further, by forming these recesses 57 on the large end surface 56 of the inner ring 55, the purpose is different, but as a result, the area ratio A3 / A2 of the large end surface 56 and the small end surface 54 of the inner ring 55 can be kept small. Grinding resistance during grinding can be reduced and grinding burn can be prevented.
JP-A-2005-75229

然しながら、この従来の内輪５５では、大端面５６に形成された窪み５７が吸音効果を発揮させるためのものであって、単に径方向と周方向に整列して所定間隔に分布させるものであるから、研削加工時の内輪５５の研削焼けを防止するための解決手段や窪み５７自体の構成に関して記載もなければ規定もなく、無論示唆もない。   However, in this conventional inner ring 55, the depressions 57 formed in the large end face 56 are for exerting a sound absorbing effect, and are simply aligned in the radial direction and the circumferential direction and distributed at predetermined intervals. There is no description, no definition, and no suggestion regarding the means for preventing grinding burn of the inner ring 55 during grinding and the configuration of the recess 57 itself.

本発明は、このような従来の問題に鑑みてなされたもので、内輪の研削焼けを防止して耐久性の向上を図った転がり軸受の内輪およびそれを備えた車輪用軸受装置を提供することを目的とする。   The present invention has been made in view of such conventional problems, and provides an inner ring of a rolling bearing that prevents grinding and burning of the inner ring and improves durability, and a wheel bearing device including the same. With the goal.

係る目的を達成すべく、本発明のうち請求項１に記載の発明は、内周に外側転走面が形成された外輪に、複数の転動体を介して内嵌され、外周に前記外側転走面に対向する内側転走面が形成されると共に、この内側転走面の一方側に大径側となる肩部が形成され、他方側に小径側となるカウンタ部が形成された転がり軸受の内輪において、前記内輪の大端面と小端面が研削加工で仕上げられると共に、前記内輪の大端面に凹部が形成され、当該内輪の大端面の面積と小端面の面積が略同一に設定されている。   In order to achieve such an object, the invention according to claim 1 of the present invention is fitted into an outer ring having an outer rolling surface formed on the inner circumference via a plurality of rolling elements, and the outer rolling on the outer circumference. A rolling bearing in which an inner rolling surface facing the running surface is formed, a shoulder portion on the large diameter side is formed on one side of the inner rolling surface, and a counter portion on the small diameter side is formed on the other side In the inner ring, the large end surface and the small end surface of the inner ring are finished by grinding, and a recess is formed in the large end surface of the inner ring, and the area of the large end surface of the inner ring and the area of the small end surface are set substantially the same. Yes.

このように、転がり軸受の内輪において、内輪の大端面と小端面が研削加工で仕上げられると共に、内輪の大端面に凹部が形成され、当該内輪の大端面の面積と小端面の面積が略同一に設定されているので、両頭研削盤で内輪の両端面を研削加工する際、両端面の研削加工時に発生する研削抵抗を低減させることができ、研削焼けを防止して耐久性の向上を図った内輪を提供することができる。   As described above, in the inner ring of the rolling bearing, the large end surface and the small end surface of the inner ring are finished by grinding, and a recess is formed in the large end surface of the inner ring, and the area of the large end surface of the inner ring and the area of the small end surface are substantially the same. Therefore, when grinding both end faces of the inner ring with a double-head grinding machine, it is possible to reduce the grinding resistance that occurs during grinding of both end faces, thereby preventing grinding burn and improving durability. An inner ring can be provided.

好ましくは、請求項２に記載の発明のように、前記大端面側の面取り部と前記小端面側の面取り部の径方向寸法が所定値に設定され、当該大端面の面積と小端面の面積が略同一に設定されていれば、両頭研削盤で内輪の両端面を研削加工する際、加工時に発生する研削抵抗の差をなくすことができ、内輪の研削焼けを確実に防止することができる。   Preferably, as in the invention described in claim 2, the radial dimension of the chamfered portion on the large end surface side and the chamfered portion on the small end surface side is set to a predetermined value, and the area of the large end surface and the area of the small end surface Is set to be substantially the same, when grinding both end faces of the inner ring with a double-headed grinding machine, the difference in grinding resistance generated during machining can be eliminated, and grinding burn of the inner ring can be reliably prevented. .

また、請求項３に記載の発明のように、前記凹部が環状に形成されていても良い。   Moreover, like the invention of Claim 3, the said recessed part may be formed cyclically | annularly.

また、請求項４に記載の発明のように、前記凹部が、前記大端面の少なくとも外径側と内径側に形成されていれば、搬送中あるいは製造工程で内輪同士が衝突して角部にバリが発生することがあっても、直接そのバリが相手部品に接触するのを防止して組立精度を確保することができる。   Further, as in the invention described in claim 4, if the recesses are formed at least on the outer diameter side and the inner diameter side of the large end surface, the inner rings collide with each other during conveyance or in the manufacturing process to form a corner. Even if burrs may occur, assembly accuracy can be ensured by preventing the burrs from directly contacting the mating parts.

また、請求項５に記載の発明のように、前記凹部が、径方向に延び、周方向等配に複数形成されていれば、内輪の剛性を低下させることなく、大端面の面積を小端面の面積に近付けることができる。   Moreover, if the said recessed part is extended in radial direction and is formed in multiple numbers by the circumferential direction equality like invention of Claim 5, without reducing the rigidity of an inner ring | wheel, the area of a large end surface will be made small. The area can be approached.

また、請求項６に記載の発明のように、前記凹部の深さが研削取代よりも大きく、０．１５〜１．０ｍｍの範囲に設定されていれば、研削加工によって凹部が削り取られて研削抵抗が上昇することはなく、また、研削加工時のクーラントがこの凹部に溜まり、研削抵抗を抑制することができる。   Further, as in the invention described in claim 6, if the depth of the concave portion is larger than the grinding allowance and is set in a range of 0.15 to 1.0 mm, the concave portion is scraped off by grinding and ground. The resistance does not increase, and the coolant during the grinding process accumulates in this recess, and the grinding resistance can be suppressed.

また、請求項７に記載の発明のように、前記凹部が鍛造加工によって形成されていれば、旋削加工の手間が省け加工効率が向上する。   Moreover, if the said recessed part is formed by the forging process like invention of Claim 7, the effort of a turning process can be saved and process efficiency can improve.

また、本発明のうち請求項８に記載の発明は、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の開口部に装着されたシールとを備え、前記小径段部を径方向外方に塑性変形させて形成した加締部により前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記内輪が前記請求項１乃至７いずれかの内輪で構成されている。   Moreover, the invention according to claim 8 of the present invention has an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, a wheel mounting flange at one end, and an outer periphery. A hub wheel having a small-diameter step portion extending in the axial direction, and at least one inner rolling surface that is press-fitted into the small-diameter step portion of the hub wheel and that faces the outer rolling surface of the double row on the outer periphery. An inner member composed of an inner ring, a double row rolling element which is accommodated between the rolling surfaces of the inner member and the outer member via a cage, and the outer member and the inner member. And a seal mounted in an annular opening formed between the member and the inner ring with respect to the hub ring by a caulking part formed by plastically deforming the small diameter step part radially outward. In the wheel bearing device fixed in the axial direction, the inner ring is constituted by the inner ring according to any one of claims 1 to 7. To have.

これにより、両頭研削盤で内輪の両端面を研削加工する際、両端面の研削加工時に発生する研削抵抗を低減させることができ、研削焼けを防止することができる。したがって、研削焼けに伴い引張残留応力が発生するのを防止して、揺動加締によって発生する内輪のフープ応力を抑制し、耐久性の向上を図ることができる。   Thereby, when grinding both end faces of the inner ring with a double-head grinding machine, it is possible to reduce grinding resistance generated during grinding of both end faces and prevent grinding burn. Therefore, it is possible to prevent the occurrence of tensile residual stress due to grinding burn, suppress the hoop stress of the inner ring generated by swing caulking, and improve the durability.

また、請求項９に記載の発明のように、前記凹部が前記大端面の外径側に形成され、その深さが、前記シールの嵌合面を残して最大限に深く設定されていれば、実質的に内輪の外径を小さくすることができ、軸受のサイズや内輪の外径および肩部の幅を無駄にアップさせることなく、効果的に肩乗り上げを防止して耐久性を確保することができる。   Further, as in the invention according to claim 9, if the recess is formed on the outer diameter side of the large end surface, and the depth thereof is set to a maximum depth leaving the fitting surface of the seal. The outer diameter of the inner ring can be substantially reduced, effectively preventing shoulder riding and ensuring durability without increasing the bearing size, the outer diameter of the inner ring and the width of the shoulder. be able to.

また、請求項１０に記載の発明のように、前記内輪の大端面と肩部との角部に、所定の曲率半径からなる円弧状の面取り部が旋削加工によって形成され、この面取り部の軸方向寸法が、前記シールの嵌合面を残して最大限に大きく設定されると共に、前記面取り部の径方向寸法が所定値に設定されていれば、加締加工時に内輪の外径に発生するフープ応力を所定値以下に抑えることができると共に、軸受のサイズや内輪の外径および肩部の幅を無駄にアップさせることなく、効果的に肩乗り上げを防止して耐久性を確保することができる。   Further, as in the invention described in claim 10, an arc-shaped chamfered portion having a predetermined radius of curvature is formed by turning at a corner portion between the large end surface and the shoulder portion of the inner ring, and the shaft of the chamfered portion is formed. If the directional dimension is set to the maximum value, leaving the fitting surface of the seal, and the radial dimension of the chamfered portion is set to a predetermined value, it will occur at the outer diameter of the inner ring during caulking. The hoop stress can be kept below a predetermined value, and it effectively prevents shoulder climbing and ensures durability without unnecessarily increasing the bearing size, inner ring outer diameter and shoulder width. it can.

本発明に係る転がり軸受の内輪は、内周に外側転走面が形成された外輪に、複数の転動体を介して内嵌され、外周に前記外側転走面に対向する内側転走面が形成されると共に、この内側転走面の一方側に大径側となる肩部が形成され、他方側に小径側となるカウンタ部が形成された転がり軸受の内輪において、前記内輪の大端面と小端面が研削加工で仕上げられると共に、前記内輪の大端面に凹部が形成され、当該内輪の大端面の面積と小端面の面積が略同一に設定されているので、両頭研削盤で内輪の両端面を研削加工する際、両端面の研削加工時に発生する研削抵抗を低減させることができ、研削焼けを防止して耐久性の向上を図った内輪を提供することができる。   An inner ring of a rolling bearing according to the present invention is fitted into an outer ring having an outer rolling surface formed on the inner periphery via a plurality of rolling elements, and an inner rolling surface facing the outer rolling surface is disposed on the outer periphery. In the inner ring of the rolling bearing in which a shoulder portion which is a large diameter side is formed on one side of the inner rolling surface and a counter portion which is a small diameter side is formed on the other side, a large end surface of the inner ring The small end face is finished by grinding and a recess is formed in the large end face of the inner ring, and the area of the large end face of the inner ring and the area of the small end face are set to be approximately the same. When grinding a surface, it is possible to reduce the grinding resistance generated during grinding of both end faces, and to provide an inner ring that prevents grinding burn and improves durability.

また、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一体に形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に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開口部に装着されたシールとを備え、前記小径段部を径方向外方に塑性変形させて形成した加締部により前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記内輪が前記請求項１乃至７いずれかの内輪で構成されているので、両頭研削盤で内輪の両端面を研削加工する際、両端面の研削加工時に発生する研削抵抗を低減させることができ、研削焼けを防止することができる。したがって、研削焼けに伴い引張残留応力が発生するのを防止して、揺動加締によって発生する内輪のフープ応力を抑制し、耐久性の向上を図ることができる。   The wheel bearing device according to the present invention has an outer member in which a double row outer rolling surface is integrally formed on the inner periphery, a wheel mounting flange at one end, and an outer periphery in the axial direction. A hub ring formed with an extended small-diameter step portion, and at least one inner ring press-fitted into the small-diameter step portion of the hub ring and having an inner rolling surface facing the outer rolling surface of the double row on the outer periphery. An inner member, a double row rolling element housed between the rolling surfaces of the inner member and the outer member via a cage, and the outer member and the inner member. The inner ring is axially oriented with respect to the hub wheel by a crimped portion formed by plastically deforming the small-diameter stepped portion radially outward. In the wheel bearing device fixed to the inner ring, the inner ring is constituted by the inner ring according to any one of claims 1 to 7. Because there, when grinding the end faces of the inner ring in double-disc grinding machine, it is possible to reduce the grinding resistance generated during grinding of both end faces, it is possible to prevent grinding burn. Therefore, it is possible to prevent the occurrence of tensile residual stress due to grinding burn, suppress the hoop stress of the inner ring generated by swing caulking, and improve the durability.

外周に車体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一体に形成された外方部材と、一端部に車輪取付フランジを一体に有し、外周に前記複列の外側転走面に対向する一方の内側転走面と、この内側転走面から軸方向に延びる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開口部に装着されたシールとを備え、前記小径段部を径方向外方に塑性変形させて形成した加締部により前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、前記内輪の大端面に環状の凹部が形成され、前記大端面側の面取り部と前記小端面側の面取り部の径方向寸法が所定値に設定されると共に、当該内輪の大端面の面積と小端面の面積が略同一に設定され、前記凹部の深さが研削取代よりも大きく、０．１５〜１．０ｍｍの範囲に設定されている。   It has a vehicle body mounting flange to be attached to the vehicle body on the outer periphery, an outer member integrally formed with a double row outer rolling surface on the inner periphery, and a wheel mounting flange on one end. 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 step portion of the hub ring; An inner member made of an inner ring that is press-fitted and has the other inner rolling surface facing the outer rolling surface of the double row on the outer periphery, and between both rolling surfaces of the inner member and the outer member A double row rolling element housed in a rollable manner via a cage, and a seal attached to an opening of an annular space formed between the outer member and the inner member, the small diameter The inner ring is fixed in the axial direction with respect to the hub ring by a caulking part formed by plastically deforming the step part radially outward. In the wheel bearing device thus formed, an annular recess is formed in the large end surface of the inner ring, and the radial dimension of the chamfered portion on the large end surface side and the chamfered portion on the small end surface side is set to a predetermined value, and The area of the large end face and the area of the small end face of the inner ring are set to be substantially the same, and the depth of the recess is set in a range of 0.15 to 1.0 mm, which is larger than the grinding allowance.

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、本発明に係る内輪を備えた車輪用軸受装置の実施形態を示す縦断面図、図２（ａ）は、図１の内輪単体を示す正面図、（ｂ）は、（ａ）の断面図、図３〜図９は、図２の変形例である。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 an embodiment of a wheel bearing device having an inner ring according to the present invention, FIG. 2 (a) is a front view showing a single inner ring of FIG. 1, and FIG. FIG. 3 to FIG. 9 are cross-sectional views of 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).

この車輪用軸受装置は従動輪側の第３世代と称され、内方部材１と外方部材１０、および両部材１、１０間に転動自在に収容された複列の転動体（ボール）６、６とを備えている。内方部材１は、ハブ輪２と、このハブ輪２に所定のシメシロを介して圧入された内輪３とからなる。   This wheel bearing device is referred to as the third generation on the driven wheel side, and is a double row rolling element (ball) accommodated between the inner member 1 and the outer member 10 and between both members 1 and 10 so as to roll freely. 6 and 6. The inner member 1 includes a hub ring 2 and an inner ring 3 that is press-fitted into the hub ring 2 through a predetermined scissors.

ハブ輪２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４を一体に有し、この車輪取付フランジ４の円周等配位置に車輪を固定するためのハブボルト５が植設されている。このハブ輪２の外周には一方（アウター側）の内側転走面２ａと、この内側転走面２ａから肩部２ｄを介して軸方向に延びる軸状の小径段部２ｂが形成されている。そして、外周に他方（インナー側）の内側転走面３ａが形成された内輪３がこの小径段部２ｂに圧入されている。   The hub wheel 2 integrally has a wheel mounting flange 4 for mounting a wheel (not shown) at an end on the outer side, and a hub bolt for fixing the wheel at a circumferentially equidistant position of the wheel mounting flange 4. 5 is planted. On the outer periphery of the hub wheel 2, one (outer side) inner rolling surface 2a and an axial small-diameter step portion 2b extending in the axial direction from the inner rolling surface 2a via the shoulder portion 2d are formed. . And the inner ring | wheel 3 by which the inner side rolling surface 3a of the other (inner side) was formed in the outer periphery is press-fit in this small diameter step part 2b.

また、車輪取付フランジ４のハブボルト５間には円孔４ａが形成されている。この円孔４ａによってハブ輪２の軽量化を図ることができると共に、車輪用軸受装置の組立工程において、例えば、図示しないブレーキロータをハブ輪２に固定した状態で、ブレーキロータや車輪取付フランジ４に邪魔されることなく、工具にて容易にナックルボルト（図示せず）を締結することもでき、外方部材１０をナックル（図示せず）に簡便に固定することもでき、組立作業性を向上することができる。   A circular hole 4 a is formed between the hub bolts 5 of the wheel mounting flange 4. The hub wheel 2 can be reduced in weight by the circular hole 4a, and in the assembly process of the wheel bearing device, for example, with the brake rotor (not shown) fixed to the hub wheel 2, the brake rotor and the wheel mounting flange 4 The knuckle bolt (not shown) can be easily fastened with a tool without being obstructed by the tool, and the outer member 10 can be simply fixed to the knuckle (not shown). Can be improved.

そして、内輪３の小端面（正面側端面）３ｃをハブ輪２の肩部２ｄに突き当てた状態で、小径段部２ｂの端部を径方向外方に塑性変形させて加締部２ｃが形成されている。すなわち、この加締部２ｃとハブ輪２の肩部２ｄとで内輪３を挟持し、ハブ輪２に対して内輪３が軸方向に固定されている。加締部２ｃは内輪３のインナー側の外郭に沿って密着した状態で塑性変形させて形成され、内輪３の大端面（背面側端面）３ｂを押え付けて所望の軸力を確保することができる。   Then, with the small end face (front side end face) 3c of the inner ring 3 abutted against the shoulder 2d of the hub ring 2, the end of the small diameter step portion 2b is plastically deformed radially outward so that the caulking portion 2c is formed. Is formed. That is, the inner ring 3 is sandwiched between the caulking portion 2 c and the shoulder portion 2 d of the hub wheel 2, and the inner ring 3 is fixed to the hub wheel 2 in the axial direction. The caulking portion 2c is formed by plastic deformation in close contact with the inner side of the inner ring 3, and can hold the large end surface (back side end surface) 3b of the inner ring 3 to secure a desired axial force. it can.

外方部材１０は、外周に車体（図示せず）に取り付けるための車体取付フランジ１０ｂを一体に有し、内周に複列の外側転走面１０ａ、１０ａが一体に形成されている。そして、それぞれの転走面１０ａ、２ａと１０ａ、３ａ間に複列の転動体６、６が収容され、保持器７、７によりこれら複列の転動体６、６が転動自在に保持されている。また、外方部材１０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、軸受内部に封入された潤滑グリースの漏洩と、外部から雨水やダスト等が軸受内部に侵入するのを防止している。   The outer member 10 integrally has a vehicle body mounting flange 10b for mounting to the vehicle body (not shown) on the outer periphery, and double row outer rolling surfaces 10a, 10a are integrally formed on the inner periphery. And the double row rolling elements 6 and 6 are accommodated between each rolling surface 10a, 2a and 10a, 3a, and these double row rolling elements 6 and 6 are rollably hold | maintained by the holder | retainers 7 and 7. ing. Seals 8 and 9 are attached to the opening of the annular space formed between the outer member 10 and the inner member 1, and leakage of lubricating grease sealed inside the bearing and rainwater and dust from the outside. Etc. are prevented from entering the inside of the bearing.

なお、ここでは、ハブ輪２の外周に直接内側転走面２ａが形成された第３世代と呼称される車輪用軸受装置を例示したが、本発明に係る車輪用軸受装置はこうした構造に限定されず、例えば、ハブ輪の小径段部に一対の内輪を圧入した、第１世代あるいは第２世代構造であっても良い。また、転動体６、６をボールとした複列アンギュラ玉軸受を例示したが、これに限らず転動体に円すいころを使用した複列円すいころ軸受であっても良い。   Here, the wheel bearing device referred to as the third generation in which the inner raceway surface 2a is formed directly on the outer periphery of the hub wheel 2 is illustrated, but the wheel bearing device according to the present invention is limited to such a structure. For example, a first generation or second generation structure in which a pair of inner rings are press-fitted into a small-diameter step portion of the hub ring may be used. Moreover, although the double row angular contact ball bearing which used the rolling elements 6 and 6 as the ball | bowl was illustrated, it is not restricted to this, The double row tapered roller bearing which uses a tapered roller for a rolling element may be sufficient.

ハブ輪２はＳ５３Ｃ等の炭素０．４０〜０．８０重量％を含む中高炭素鋼で形成され、内側転走面２ａをはじめ、アウター側のシール８が摺接する車輪取付フランジ４の基部４ｂから小径段部２ｂに亙り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２ｃは、鍛造後の素材表面硬さの未焼入れ部とされている。   The hub wheel 2 is formed of medium and high carbon steel containing 0.40 to 0.80% by weight of carbon such as S53C, and the like from the base part 4b of the wheel mounting flange 4 to which the outer seal 8 comes into sliding contact, including the inner rolling surface 2a. The surface hardness is set to a range of 58 to 64 HRC by induction hardening over the small diameter step 2b. The caulking portion 2c is an unquenched portion of the material surface hardness after forging.

一方、内輪３および転動体６は、ＳＵＪ２等の高炭素クロム軸受鋼からなり、ズブ焼入れにより芯部まで５８〜６４ＨＲＣの範囲で硬化処理されている。また、外方部材１０は、前記ハブ輪２と同様、Ｓ５３Ｃ等の炭素０．４０〜０．８０重量％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１０ａ、１０ａ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。   On the other hand, the inner ring 3 and the rolling element 6 are made of high carbon chrome bearing steel such as SUJ2, and are hardened in the range of 58 to 64 HRC up to the core by quenching. Similarly to the hub wheel 2, the outer member 10 is made of medium and high carbon steel containing 0.40 to 0.80% by weight of carbon such as S53C, and at least the double row outer rolling surfaces 10a and 10a have high frequency. The surface hardness is hardened by quenching to a range of 58 to 64 HRC.

ここで、本出願人は、内輪３の両端面を両頭研削盤で研削した際、研削加工時に発生する研削抵抗を低減させるために、内輪３の大端面３ｂと小端面３ｃの面積比を小さくすることに着目した。本実施形態では、図２に示すように、内輪３の大端面３ｂに環状の凹部１１が旋削加工によって形成されている。この凹部１１の幅を所定値に設定することにより、大端面３ｂの面積Ａ０＝Ａ１−Ａ４を小端面３ｃの面積Ａ２に近付けることができ、大端面３ｂと小端面３ｃの面積比（Ａ０／Ａ２）が従来の面積比に比べ大幅に小さくなる。これにより、内輪３の両端面の研削加工時に発生する研削抵抗を低減させることができ、内輪３の研削焼けを防止して耐久性の向上を図った内輪３を提供することができる。なお、ここでは、大端面３ｂの面積Ａ１は、凹部１１を形成する前の面積（投影面積）を指す。   Here, the applicant reduces the area ratio of the large end surface 3b and the small end surface 3c of the inner ring 3 in order to reduce the grinding resistance generated during grinding when both end surfaces of the inner ring 3 are ground with a double-headed grinding machine. Focused on doing. In the present embodiment, as shown in FIG. 2, an annular recess 11 is formed on the large end surface 3 b of the inner ring 3 by turning. By setting the width of the recess 11 to a predetermined value, the area A0 = A1-A4 of the large end face 3b can be brought close to the area A2 of the small end face 3c, and the area ratio (A0 / A3) between the large end face 3b and the small end face 3c. A2) is significantly smaller than the conventional area ratio. As a result, it is possible to reduce the grinding resistance that occurs during grinding of both end faces of the inner ring 3, and it is possible to provide the inner ring 3 that is improved in durability by preventing grinding burn of the inner ring 3. Here, the area A1 of the large end surface 3b indicates the area (projected area) before the recess 11 is formed.

また、凹部１１の深さｔは、研削取代（０．０５〜０．１０ｍｍ）よりも大きく、０．１５〜１．０ｍｍの範囲に設定されている。これにより、研削加工によって凹部１１が削り取られて研削抵抗が上昇することはない。また、研削加工時のクーラントがこの凹部１１に溜まり、研削抵抗を抑制することができる。ここで、凹部１１の深さｔが１．０ｍｍを超えても良いが、加工量が増えることにより工程能力が低下すると共に、研削加工時に研削面にクーラントが滲み出難くなるので好ましくない。   Moreover, the depth t of the recessed part 11 is larger than the grinding allowance (0.05-0.10 mm), and is set to the range of 0.15-1.0 mm. Thereby, the concave portion 11 is not scraped off by the grinding process and the grinding resistance does not increase. Moreover, the coolant at the time of a grinding process accumulates in this recessed part 11, and grinding resistance can be suppressed. Here, the depth t of the recess 11 may exceed 1.0 mm, but this is not preferable because the processing capability is reduced due to an increase in the amount of processing, and the coolant is less likely to bleed onto the ground surface during grinding.

さらに、大端面３ｂ側の面取り部１２、１３と小端面３ｃ側の面取り部１４の径方向寸法を考慮することによって大端面３ｂの面積Ａ０と小端面３ｃの面積Ａ２が同一となるように設定することができる。これにより、両頭研削盤で内輪３の両端面３ｂ、３ｃを研削加工する際、加工時に発生する研削抵抗の差をなくすことができ、内輪３の研削焼けを確実に防止することができる。   Further, by considering the radial dimensions of the chamfered portions 12 and 13 on the large end surface 3b side and the chamfered portion 14 on the small end surface 3c side, the area A0 of the large end surface 3b and the area A2 of the small end surface 3c are set to be the same. can do. Thereby, when grinding the both end faces 3b, 3c of the inner ring 3 with a double-head grinding machine, the difference in grinding resistance generated during the machining can be eliminated, and grinding burn of the inner ring 3 can be reliably prevented.

図３〜図９に内輪３の変形例を示す。なお、前述した実施形態と同一部位あるいは同様の機能を有する部位には同じ符号を付して詳細な説明を省略する。図３に示す内輪１５の大端面３ｂには、径方向に延びる複数の凹部１５ａが周方向等配に鍛造加工によって形成されている。これにより、旋削加工の手間が省け加工効率が向上すると共に、研削加工時に研削面にクーラントが滲み出易くなり、大端面３ｂと小端面３ｃの面積比が小さくなることと相俟って大端面３ｂ側の研削抵抗を減少させることができる。   3 to 9 show modified examples of the inner ring 3. In addition, the same code | symbol is attached | subjected to the site | part which has the same site | part or the same function as embodiment mentioned above, and detailed description is abbreviate | omitted. On the large end surface 3b of the inner ring 15 shown in FIG. 3, a plurality of concave portions 15a extending in the radial direction are formed by forging in a circumferentially equal distribution. This saves the labor of turning and improves the machining efficiency, and also makes it easy for the coolant to ooze out to the grinding surface during grinding, and the large end surface combined with the reduction in the area ratio of the large end surface 3b to the small end surface 3c. The grinding resistance on the 3b side can be reduced.

図４に示す内輪１６の大端面３ｂには、外径側と内径側にそれぞれ環状の凹部１６ａ、１６ｂが鍛造加工によって形成されている。この凹部１６ａ、１６ｂのそれぞれの幅を所定値に設定することにより、大端面３ｂの面積Ａ０＝Ａ１−Ａ５−Ａ６を小端面３ｃの面積Ａ２に近付けることができ、大端面３ｂと小端面３ｃの面積比（Ａ０／Ａ２）を従来の面積比に比べ大幅に小さくすることができる。このように、大端面３ｂの外径側と内径側に環状の凹部１６ａ、１６ｂを形成することにより、搬送中あるいは製造工程で内輪１６同士が衝突して角部にバリが発生することがあっても、直接そのバリが相手部品に接触するのを防止して組立精度を確保することができる。なお、環状の凹部１６ａ、１６ｂを２本に限らず多数同心状に形成しても良い。   On the large end surface 3b of the inner ring 16 shown in FIG. 4, annular recesses 16a and 16b are formed by forging on the outer diameter side and the inner diameter side, respectively. By setting the respective widths of the recesses 16a and 16b to a predetermined value, the area A0 = A1-A5-A6 of the large end face 3b can be brought close to the area A2 of the small end face 3c, and the large end face 3b and the small end face 3c. The area ratio (A0 / A2) can be significantly reduced as compared with the conventional area ratio. As described above, by forming the annular recesses 16a and 16b on the outer diameter side and the inner diameter side of the large end surface 3b, the inner rings 16 may collide with each other during conveyance or in the manufacturing process, and burrs may be generated at the corners. However, the assembly accuracy can be ensured by preventing the burr from coming into direct contact with the mating part. The annular recesses 16a and 16b are not limited to two and may be formed concentrically.

図５に示す内輪１７の大端面３ｂには、外径側に複数の凹部１６ｃと内径側に環状の凹部１６ｂがそれぞれ鍛造加工によって形成されている。外径側の凹部１６ｃは周方向等配に形成されている。そして、この凹部１６ａ、１６ｂのそれぞれの幅を所定値に設定することにより、内輪１７の剛性を低下させることなく、大端面３ｂの面積Ａ０＝Ａ１−Ａ５−Ａ６を小端面３ｃの面積Ａ２に近付けることができる。   On the large end surface 3b of the inner ring 17 shown in FIG. 5, a plurality of recesses 16c are formed on the outer diameter side and an annular recess 16b is formed on the inner diameter side by forging. The recesses 16c on the outer diameter side are formed in a circumferentially uniform manner. Then, by setting the widths of the recesses 16a and 16b to predetermined values, the area A0 of the large end surface 3b is reduced to the area A2 of the small end surface 3c without reducing the rigidity of the inner ring 17. You can get closer.

図６に示す内輪１８の大端面３ｂには、外径側に環状の凹部１８ａが鍛造加工によって形成されている。この凹部１８ａの幅を所定値に設定することにより、大端面３ｂの面積Ａ０＝Ａ１−Ａ７を小端面３ｃの面積Ａ２に近付けることができる。なお、凹部１８ａの深さｔ１は、図示しないシールの嵌合面を残して最大限に深く設定されている。これにより、実質的に内輪１８の外径を小さくすることができ、軸受のサイズや内輪１８の外径および肩部の幅を無駄にアップさせることなく、効果的に肩乗り上げを防止して耐久性を確保することができる。ここで、肩乗り上げとは、例えば、軸受に大きなモーメント荷重が負荷された時に、転動体６と内側転走面３ａとの接触部に発生する接触楕円が肩部と内側転走面３ａの角部からはみ出し、所謂エッジロード（過大応力）が発生する現象を言う。   An annular recess 18a is formed on the outer diameter side of the large end surface 3b of the inner ring 18 shown in FIG. 6 by forging. By setting the width of the recess 18a to a predetermined value, the area A0 = A1-A7 of the large end face 3b can be brought close to the area A2 of the small end face 3c. The depth t1 of the recess 18a is set to the maximum depth, leaving a seal fitting surface (not shown). As a result, the outer diameter of the inner ring 18 can be substantially reduced, and the shoulder ride is effectively prevented and durable without increasing the bearing size, the outer diameter of the inner ring 18 and the width of the shoulder. Sex can be secured. Here, the shoulder climbing means that, for example, when a large moment load is applied to the bearing, a contact ellipse generated at the contact portion between the rolling element 6 and the inner rolling surface 3a is an angle between the shoulder portion and the inner rolling surface 3a. This is a phenomenon in which a so-called edge load (excessive stress) is generated.

図７に示す内輪１９の大端面３ｂには、外径側に複数の凹部１９ａが鍛造加工によって形成されている。この凹部１９ａは周方向等配に形成されている。そして、この凹部１９ａの幅を所定値に設定することにより、内輪１９の剛性を低下させることなく、大端面３ｂの面積Ａ０＝Ａ１−Ａ７を小端面３ｃの面積Ａ２に近付けることができる。   In the large end surface 3b of the inner ring 19 shown in FIG. 7, a plurality of recesses 19a are formed on the outer diameter side by forging. The recesses 19a are formed in a circumferentially equidistant manner. By setting the width of the recess 19a to a predetermined value, the area A0 = A1-A7 of the large end face 3b can be brought close to the area A2 of the small end face 3c without reducing the rigidity of the inner ring 19.

図８に示す内輪２０の大端面３ｂには、外径側に環状の凹部２０ａが旋削加工によって形成されている。ここで、大端面３ｂの面積Ａ２が小端面３ｃの面積Ａ２と略同一になるように、凹部２０ａの幅が所定値に設定されている（Ａ２＝Ａ１−Ａ８）。なお、凹部２０ａの深さｔ２は、内輪２０同士の衝突により発生するバリ等が大端面３よりも出っ張らない程度の深さ、例えば、０．５〜１．０ｍｍ程度に設定されている。   In the large end surface 3b of the inner ring 20 shown in FIG. 8, an annular recess 20a is formed on the outer diameter side by turning. Here, the width of the recess 20a is set to a predetermined value so that the area A2 of the large end face 3b is substantially the same as the area A2 of the small end face 3c (A2 = A1-A8). The depth t2 of the recess 20a is set to such a depth that a burr or the like generated by the collision between the inner rings 20 does not protrude from the large end surface 3, for example, about 0.5 to 1.0 mm.

図９に示す内輪２１の大端面３ｂと肩部２２との角部には、曲率半径Ｒからなる円弧状の面取り部２１ａが旋削加工によって形成されている。ここで、大端面３ｂの面積Ａ２が小端面３ｃの面積Ａ２と略同一になるように、面取り部２１ａの径方向の寸法が所定値に設定されている（Ａ２＝Ａ１−Ａ８）。これにより、応力集中を緩和でき、加締加工時に内輪２１の外径に発生するフープ応力を所定値以下に抑えることができると共に、軸受のサイズや内輪２１の外径および肩部２２の幅を無駄にアップさせることなく、効果的に肩乗り上げを防止して耐久性を確保することができる。   An arc-shaped chamfered portion 21a having a radius of curvature R is formed by turning at the corner between the large end surface 3b and the shoulder portion 22 of the inner ring 21 shown in FIG. Here, the radial dimension of the chamfered portion 21a is set to a predetermined value so that the area A2 of the large end surface 3b is substantially the same as the area A2 of the small end surface 3c (A2 = A1-A8). As a result, stress concentration can be alleviated, hoop stress generated on the outer diameter of the inner ring 21 during caulking can be suppressed to a predetermined value or less, and the bearing size, the outer diameter of the inner ring 21 and the width of the shoulder portion 22 can be reduced. Without raising wastefully, it is possible to effectively prevent shoulder climbing and ensure durability.

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、ハブ輪の小径段部に内輪を圧入し、小径段部の端部を塑性変形させて形成した加締部によって内輪を固定した第１世代乃至第３世代のセルフリテイン構造の車輪用軸受装置に適用できる。   In the wheel bearing device according to the present invention, the inner ring is fixed by a caulking portion formed by press-fitting an inner ring into a small-diameter step portion of a hub wheel and plastically deforming an end portion of the small-diameter step portion. It can be applied to a self-retained wheel bearing device.

本発明に係る内輪を備えた車輪用軸受装置の実施形態を示す縦断面図である。It is a longitudinal section showing an embodiment of a wheel bearing device provided with an inner ring concerning the present invention. （ａ）は、図１の内輪単体を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the inner ring single-piece | unit of FIG. (B) is sectional drawing of (a). （ａ）は、図２の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、図２の他の変形例を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the other modification of FIG. (B) is sectional drawing of (a). （ａ）は、一般的なアンギュラ玉軸受の内輪を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view showing an inner ring of a general angular contact ball bearing. (B) is sectional drawing of (a). （ａ）は、従来の内輪を示す正面図である。 （ｂ）は、（ａ）の断面図である。(A) is a front view which shows the conventional inner ring | wheel. (B) is sectional drawing of (a).

符号の説明Explanation of symbols

１・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・内方部材
２・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・ハブ輪
２ａ、３ａ・・・・・・・・・・・・・・・・・・・・・・・・・・・内側転走面
２ｂ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・小径段部
２ｃ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・加締部
２ｄ、２２・・・・・・・・・・・・・・・・・・・・・・・・・・・肩部
３、１５、１６、１７、１８、１９、２０、２１・・・・・・・・・・内輪
３ｂ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・大端面
３ｃ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・小端面
４・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・車輪取付フランジ
４ａ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・円孔
４ｂ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・基部
５・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・ハブボルト
６・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・転動体
７・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・保持器
８、９・・・・・・・・・・・・・・・・・・・・・・・・・・・・・シール
１０・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・外方部材
１０ａ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・外側転走面
１０ｂ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・車体取付フランジ
１１、１５ａ、１６ａ、１６ｂ、１６ｃ、１８ａ、１９ａ、２０ａ・・凹部
１２、１３、１４、２１ａ・・・・・・・・・・・・・・・・・・・・面取り部
５０、５５・・・・・・・・・・・・・・・・・・・・・・・・・・・内輪
５０ａ・・・・・・・・・・・・・・・・・・・・・・・・・・・・・内側転走面
５１・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・肩部
５２・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・カウンタ部
５３、５６・・・・・・・・・・・・・・・・・・・・・・・・・・・大端面
５４・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・小端面
５５・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・車輪取付フランジ
５７・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・窪み
Ａ０、Ａ３・・・・・・・・・・・・・・・・・・・・・・・・・・・大端面の面積
Ａ１・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・大端面の投影面積
Ａ２・・・・・・・・・・・・・・・・・・・・・・・・・・・・・・小端面の面積
Ａ４、Ａ５、Ａ６、Ａ７、Ａ８・・・・・・・・・・・・・・・・・・凹部の面積
ｔ、ｔ１、ｔ２・・・・・・・・・・・・・・・・・・・・・・・・・凹部の深さ 1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner member 2 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 2a, 3a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inside Rolling surface 2b ..... Small diameter step 2c ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Clamping part 2d, 22 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ Shoulder 3, 15, 16, 17, 18, 19, 20, 21 ... Inner ring 3b ... ………………………………………………………………………………………………………………………………………………………………………………………………………………………………………….・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 4a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Yen Hole 4b ... Base 5 ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub bolt 6 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Rolling element 7 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Retainer 8, 9 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Seal 10 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outside Member 10a ......... Outer rolling surface 10b ... ... Car body mounting flanges 11, 15a, 16a, 16b, 16c, 18a, 19a, 20a .... Recesses 12, 13, 14, 21a ... ... Chamfered portions 50, 55 ..... Inner ring 50a ...・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner rolling surface 51 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ Shoulder 52 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Counter 53, 56 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Large end face 54 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・End face 55 Ridge 57 .......... depressions A0, A3 ...・ ・ ・ ・ ・ ・ ・ ・ Area of large end face A1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ End face Projection area A2 of the small end surface area A4, A5, A6, A7, A8... ............ recess area t, t1, t2 depth

Claims (10)

内周に外側転走面が形成された外輪に、複数の転動体を介して内嵌され、外周に前記外側転走面に対向する内側転走面が形成されると共に、この内側転走面の一方側に大径側となる肩部が形成され、他方側に小径側となるカウンタ部が形成された転がり軸受の内輪において、
前記内輪の大端面と小端面が研削加工で仕上げられると共に、前記内輪の大端面に凹部が形成され、当該内輪の大端面の面積と小端面の面積が略同一に設定されていることを特徴とする転がり軸受の内輪。 An inner race surface is formed on the outer periphery of the outer ring having an outer race surface formed on the inner circumference through a plurality of rolling elements, and an inner race surface facing the outer race surface is formed on the outer circumference. In an inner ring of a rolling bearing in which a shoulder portion that is a large-diameter side is formed on one side and a counter portion that is a small-diameter side is formed on the other side,
The large end surface and the small end surface of the inner ring are finished by grinding, a recess is formed in the large end surface of the inner ring, and the area of the large end surface of the inner ring and the area of the small end surface are set to be substantially the same. The inner ring of the rolling bearing. 前記大端面側の面取り部と前記小端面側の面取り部の径方向寸法が所定値に設定され、当該大端面の面積と小端面の面積が略同一に設定されている請求項１に記載の転がり軸受の内輪。   The radial dimension of the chamfered portion on the large end surface side and the chamfered portion on the small end surface side is set to a predetermined value, and the area of the large end surface and the area of the small end surface are set to be substantially the same. Roller bearing inner ring. 前記凹部が環状に形成されている請求項１または２に記載の転がり軸受の内輪。   The inner ring of the rolling bearing according to claim 1 or 2, wherein the recess is formed in an annular shape. 前記凹部が、前記大端面の少なくとも外径側と内径側に形成されている請求項１乃至３いずれかに記載の転がり軸受の内輪。   The inner ring of the rolling bearing according to any one of claims 1 to 3, wherein the concave portion is formed at least on an outer diameter side and an inner diameter side of the large end surface. 前記凹部が、径方向に延び、周方向等配に複数形成されている請求項１乃至４いずれかに記載の転がり軸受の内輪。   The inner ring of a rolling bearing according to any one of claims 1 to 4, wherein a plurality of the recesses extend in the radial direction and are formed in a circumferentially equidistant manner. 前記凹部の深さが研削取代よりも大きく、０．１５〜１．０ｍｍの範囲に設定されている請求項１乃至５いずれかに記載の転がり軸受の内輪。   The inner ring of the rolling bearing according to any one of claims 1 to 5, wherein a depth of the recess is larger than a grinding allowance and is set in a range of 0.15 to 1.0 mm. 前記凹部が鍛造加工によって形成されている請求項１乃至６いずれかに記載の転がり軸受の内輪。   The inner ring of a rolling bearing according to any one of claims 1 to 6, wherein the recess is formed by forging. 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の開口部に装着されたシールとを備え、
前記小径段部を径方向外方に塑性変形させて形成した加締部により前記ハブ輪に対して前記内輪が軸方向に固定された車輪用軸受装置において、
前記内輪が前記請求項１乃至７いずれかの内輪で構成されていることを特徴とする車輪用軸受装置。 An outer member in which a double row outer rolling surface is integrally formed on the inner periphery;
A hub wheel having a wheel mounting flange integrally formed at one end and a small-diameter step portion extending in the axial direction on the outer periphery, and a press-fitted into the small-diameter step portion of the hub wheel, and the outer surface of the double row on the outer periphery. An inner member comprising at least one inner ring formed with an inner rolling surface opposed to
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 in an annular opening formed between the outer member and the inner member;
In the wheel bearing device in which the inner ring is fixed in the axial direction with respect to the hub wheel by a caulking part formed by plastically deforming the small diameter step part radially outwardly,
A bearing device for a wheel, wherein the inner ring comprises the inner ring according to any one of claims 1 to 7. 前記凹部が前記大端面の外径側に形成され、その深さが、前記シールの嵌合面を残して最大限に深く設定されている請求項８に記載の車輪用軸受装置。   The wheel bearing device according to claim 8, wherein the concave portion is formed on the outer diameter side of the large end surface, and the depth thereof is set to a maximum depth while leaving a fitting surface of the seal. 前記内輪の大端面と肩部との角部に、所定の曲率半径からなる円弧状の面取り部が旋削加工によって形成され、この面取り部の軸方向寸法が、前記シールの嵌合面を残して最大限に大きく設定されると共に、前記面取り部の径方向寸法が所定値に設定されている請求項８に記載の車輪用軸受装置。   An arc-shaped chamfered portion having a predetermined radius of curvature is formed by turning at the corner portion between the large end surface and the shoulder portion of the inner ring, and the axial dimension of the chamfered portion leaves the fitting surface of the seal. The wheel bearing device according to claim 8, wherein the wheel bearing device is set to a maximum size and a radial dimension of the chamfered portion is set to a predetermined value.
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