JP2012031937A - Wheel bearing device - Google Patents

Wheel bearing device Download PDF

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Publication number
JP2012031937A
JP2012031937A JP2010172019A JP2010172019A JP2012031937A JP 2012031937 A JP2012031937 A JP 2012031937A JP 2010172019 A JP2010172019 A JP 2010172019A JP 2010172019 A JP2010172019 A JP 2010172019A JP 2012031937 A JP2012031937 A JP 2012031937A
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Japan
Prior art keywords
ball
bearing device
pocket
wheel bearing
cage
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JP2010172019A
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Japanese (ja)
Inventor
Tomohisa Uozumi
朋久 魚住
Shinichi Hashimoto
眞一 橋本
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2010172019A priority Critical patent/JP2012031937A/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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3862—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together
    • F16C33/3875—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together made from plastic, e.g. two injection moulded parts joined by a snap fit
    • 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
    • F16C19/16—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 a single row of balls
    • F16C19/163—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 a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/52—Polyphenylene sulphide [PPS]
    • 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
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/60—Polyamides [PA]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/43—Clutches, e.g. disengaging bearing

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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 wheel bearing device that completely prevents a ball from running on a shoulder.SOLUTION: Two track grooves 3 are provided on the inner periphery of an outer member 1, and a shoulder 4 is formed between the two track grooves 3. Two track grooves 16, 18 are set on the outer periphery of an inner member 11, facing each of the two track grooves 3 of the outer member 1. Shoulders 17, 19 are each formed outside the two track grooves 16, 18. Balls 21 are inserted between the track grooves 3, 16, 18 facing each other. The ratio H/d of the height Hof the shoulders 4, 17, 19 to the diameter d of the ball 21, is set to be 0.25 or higher and lower than 0.50, to prevent the balls 21 from running on the shoulders 4, 17, 19, wherein Hindicates the height of the shoulder 4 of the outer member 1 and the shoulders 17, 19 of the inner member 11, and d indicates the diameter of the balls 21.

Description

この発明は、自動車のアクスルを支持する車輪軸受装置に関する。   The present invention relates to a wheel bearing device for supporting an axle of an automobile.

この種の車輪軸受装置として特許文献１に記載されたものが従来から知られている。この特許文献１に記載された車輪軸受装置においては、車体に取付けられる外方部材の内周に複列の軌道溝を形成し、その外方部材の内側に組込まれてアクスルを支持する内方部材の外周に、上記外方部材の複列の軌道溝のそれぞれと対向する複列の軌道溝を設け、上記外方部材の軌道溝とこれに対向する内方部材の軌道溝間のそれぞれにボールを組込んで内方部材を回転自在に支持している。   As this type of wheel bearing device, one described in Patent Document 1 has been conventionally known. In the wheel bearing device described in Patent Document 1, a double row raceway groove is formed on the inner periphery of an outer member attached to the vehicle body, and the inner member is incorporated inside the outer member to support the axle. Provided on the outer periphery of the member is a double row raceway groove facing each of the double row raceway grooves of the outer member, and between the raceway groove of the outer member and the raceway groove of the inner member facing this. A ball is incorporated to rotatably support the inner member.

上記のような車輪軸受装置においては、普通、外方部材の複列の軌道溝間に肩を形成し、一方、内方部材には、アウタ側軌道溝のアウタ側およびインナ側軌道溝のインナ側にそれぞれ肩を形成して、対向する軌道溝とボールを、転動体荷重の作用線の交点がピッチ円の外側に位置する外向きアンギュラコンタクトの接触としている。   In the wheel bearing device as described above, a shoulder is usually formed between the double row raceway grooves of the outer member, while the inner member has inner sides of the outer side raceway groove and the inner side raceway groove. A shoulder is formed on each side, and the facing raceway groove and the ball are in contact with the outward angular contact where the intersection of the lines of action of the rolling element load is located outside the pitch circle.

特開２０１０−５８７８９号公報JP 2010-58789 A

ところで、上記特許文献１に記載された車輪軸受装置においては、複列のボールのそれぞれを外向きアンギュラコンタクトとしているため、比較的大きなモーメント荷重やスラスト荷重を受けることができるものの、車輪が縁石に乗り上げた場合や車両が急旋回して、車輪軸受装置に大きなモーメント荷重やスラスト荷重が負荷された際にボールが外方部材や内方部材の肩に乗り上げて、肩を損傷させる可能性がある。   By the way, in the wheel bearing device described in the above-mentioned patent document 1, since each of the double-row balls is an outward angular contact, although the wheel can receive a relatively large moment load and thrust load, the wheel becomes a curb. When riding or when the vehicle turns sharply and a large moment load or thrust load is applied to the wheel bearing device, the ball may ride on the shoulder of the outer member or inner member and damage the shoulder. .

また、上記のような車輪軸受装置においては、複列のボールのそれぞれを合成樹脂からなる冠形保持器により保持するようにしているが、大きなモーメント荷重が負荷された際に、ボールの遅れ進みによって保持器が脱落するおそれがある。   In the wheel bearing device as described above, each of the double-row balls is held by a crown-shaped cage made of a synthetic resin. However, when a large moment load is applied, the balls are delayed. May cause the cage to fall off.

この発明の課題は、ボールの肩乗り上げを完全に防止することができるようにした車輪軸受装置を提供することである。   An object of the present invention is to provide a wheel bearing device capable of completely preventing a ball from climbing over the shoulder.

上記の課題を解決するために、この発明においては、複列の軌道溝を内周に有し、その複列の軌道溝間に肩が設けられた外方部材と、その外方部材の複列の軌道溝のそれぞれに対向する複列の軌道溝を外周に有し、その複列の軌道溝のアウタ側軌道溝のアウタ側およびインナ側軌道溝のインナ側のそれぞれに肩が形成された内方部材と、前記外方部材の複列の軌道溝とその軌道溝のそれぞれと対向する内方部材の複列の軌道溝とにアンギュラコンタクトするよう組込まれて内方部材を回転自在に支持する複列のボールと、その各列のボールをそれぞれ逆方向から単独に保持する一対の保持器とからなる車輪軸受装置において、前記外方部材の内周に設けられた肩および前記内方部材の外周に形成された肩の高さをＨ１、ボールの球径をｄとしたとき、ボールの球径ｄに対する肩の高さＨ１の比率Ｈ１／ｄを０．２５以上０．５０未満とした構成を採用したのである。 In order to solve the above problems, according to the present invention, an outer member having a double row raceway groove on the inner periphery, and a shoulder provided between the double row raceway grooves, and a double member of the outer member are provided. A double row raceway groove facing each of the raceway grooves in the row is provided on the outer periphery, and shoulders are formed on the outer side of the outer side raceway groove and the inner side of the inner side raceway groove of the double row raceway groove, respectively. The inner member is incorporated in angular contact with the double row raceway grooves of the outer member and the double row raceway grooves facing each of the raceway grooves, and the inner member is rotatably supported. In a wheel bearing device comprising a double row of balls and a pair of cages that hold the balls of each row independently from opposite directions, and a shoulder provided on the inner periphery of the outer member and the inner member H 1 height of the formed shoulder on the outer periphery, the spherical diameter of the ball and d of When in is the adopted a configuration in which the ratio H 1 / d of the shoulder height H 1 relative to the spherical diameter d of the ball and less than 0.25 to 0.50.

上記のように、ボールの球径ｄに対する外方部材および内方部材の肩の高さＨ１の比率Ｈ１／ｄを０．２５以上０．５０未満とすることによって、ボールに大きなスラスト荷重や大きなモーメント荷重が負荷された際に、その荷重を外方部材および内方部材の肩で受けることができ、ボールの肩乗り上げを完全に防止することができる。 As described above, by setting the ratio H 1 / d of the shoulder height H 1 of the outer member and the inner member to the ball diameter d of the ball to be 0.25 or more and less than 0.50, a large thrust load is applied to the ball. When a large moment load is applied, the load can be received by the shoulders of the outer member and the inner member, and it is possible to completely prevent the ball from climbing over the shoulder.

ここで、複列のボールのそれぞれを保持する保持器として、合成樹脂からなる円筒形の第１分割保持器と、その第１分割保持器の内側に嵌合された合成樹脂製の円筒形の第２分割保持器とからなり、第１分割保持器および第２分割保持器のそれぞれが、環状体を有し、その環状体の軸方向一側面に対向一対のポケット爪が等間隔に形成され、その各対向一対のポケット爪間に前記環状体を刳り抜く２分の１円を超える大きさのボール保持用ポケットが設けられた冠形とされ、その第１分割保持器と第２分割保持器はポケットの開口端が逆向きとされ、ポケットが径方向で対向する組立てとされ、前記第１分割保持器と前記第２分割保持器の相互間に、その両保持器の嵌合により係合して両保持器を軸方向に非分離とする連結手段を設けた構成のものを採用することができる。   Here, as a cage for holding each of the double-row balls, a cylindrical first divided cage made of synthetic resin, and a synthetic resin cylindrical shape fitted inside the first divided cage Each of the first divided holder and the second divided holder has an annular body, and a pair of opposing pocket claws are formed at equal intervals on one side surface in the axial direction of the annular body. The crown is provided with a ball-holding pocket having a size of more than a half circle that punches through the annular body between each pair of opposed pocket claws, and the first divided holder and the second divided holder. The cage is an assembly in which the open ends of the pockets are reversed and the pockets are opposed to each other in the radial direction. The cage is engaged between the first split cage and the second split cage by fitting the two cages. Combined with the connecting means to non-separate both cages in the axial direction It is possible to adopt things.

上記のような保持器の採用においては、ボールを保持するポケットが、第１分割保持器に形成された２分の１円を超える大きさのポケットと第２分割保持器に形成された２分の１円を超える大きさのポケットの２つのポケットにより形成されるため、ボール案内面は広く、強度の高い保持器を得ることができる。   In the adoption of the cage as described above, the pocket for holding the ball is a pocket having a size exceeding a half circle formed in the first divided cage and the two minutes formed in the second divided cage. Therefore, the ball guide surface is wide and a highly strong cage can be obtained.

また、第１分割保持器と第２分割保持器は、連結手段によって軸方向に非分離の結合状態とされるため、大きなモーメント荷重が負荷されてボールに遅れや進みが生じても、保持器は脱落するようなことはない。   Further, since the first split cage and the second split cage are in a non-separated coupled state in the axial direction by the connecting means, even if a large moment load is applied and the ball is delayed or advanced, the cage Will not fall off.

ここで、連結手段として、第１分割保持器の隣接するポケットのポケット爪間に内向きの係合爪を設け、第２分割保持器の隣接するポケットのポケット爪間に外向きの係合爪を設け、第１分割保持器の係合爪を第２分割保持器の外径面に形成された係合凹部に係合し、第２分割保持器の係合爪を第１分割保持器の内径面に形成された係合凹部に係合した構成から成るものを採用することができる。   Here, as the connecting means, an inward engagement claw is provided between the pocket claws of the adjacent pockets of the first divided holder, and an outward engagement claw is provided between the pocket claws of the adjacent pockets of the second divided holder. Engaging the engaging claw of the first split cage with the engaging recess formed in the outer diameter surface of the second split cage, and engaging the engaging claw of the second split cage with the first split cage. What consists of the structure engaged with the engagement recessed part formed in the internal-diameter surface is employable.

上記のような連結手段の採用において、係合爪と係合凹部の係合部の数を３つ以上とすることにより、第１分割保持器と第２分割保持器とをより確実に結合することができる。   In adopting the connecting means as described above, the number of the engagement portions of the engagement claw and the engagement recess is three or more, so that the first divided holder and the second divided holder are more reliably coupled. be able to.

また、係合爪と係合凹部間に形成される周方向すきまをボールとポケット間に形成される周方向のポケットすきまより大きくしておくことにより、大きなモーメント荷重が負荷されてボールに遅れ進みが生じ、第１分割保持器と第２分割保持器とが相対的に回転しても、係合爪が係合凹部の周方向で対向する側面に当接することはなく、係合爪の損傷防止に効果を挙げることができる。   In addition, by setting the circumferential clearance formed between the engaging claw and the engaging recess larger than the circumferential pocket clearance formed between the ball and the pocket, a large moment load is applied and the ball is delayed. Even if the first split cage and the second split cage rotate relative to each other, the engaging claws do not come into contact with the opposite side surfaces in the circumferential direction of the engaging recess, and the engaging claws are damaged. It can be effective for prevention.

さらに、係合爪と係合凹部間に形成される軸方向すきまをボールとポケット間に形成される軸方向のポケットすきまより大きくしておくことにより、第１分割保持器と第２分割保持器に離反する方向の軸方向力が作用した際に、対向一対のポケット爪の内面がボールの外周面に当接して、係合爪が係合凹部の軸方向端面に当接するというようなことはなく、係合爪の損傷防止に効果を挙げることができる。   Further, the first split retainer and the second split retainer are formed by making the axial clearance formed between the engaging claw and the engaging recess larger than the axial pocket clearance formed between the ball and the pocket. When the axial force in the direction separating from each other is applied, the inner surfaces of the pair of opposing pocket claws abut against the outer peripheral surface of the ball, and the engaging claws abut against the axial end surface of the engaging recess. The effect of preventing damage to the engaging claws can be obtained.

ここで、合成樹脂からなる第１分割保持器および第２分割保持器は、軌道溝とボールの接触部を潤滑する潤滑油と接触するため、耐油性に優れた合成樹脂で成形するのが好ましい。そのような樹脂として、ポリアミド４６（ＰＡ４６）、ポリアミド６６（ＰＡ６６）、ポリフェニレンスルファイド（ＰＰＳ）を挙げることができる。それらの樹脂のうち、ポリフェニレンスルファイド（ＰＰＳ）は、他の樹脂に比較して耐油性が優れているため、耐油性を考慮するならば、ポリフェニレンスルファイド（ＰＰＳ）を用いるのが最も好ましい。   Here, since the first split cage and the second split cage made of synthetic resin are in contact with a lubricating oil that lubricates the contact portion between the raceway groove and the ball, it is preferable to mold the synthetic resin with excellent oil resistance. . Examples of such a resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS). Among these resins, polyphenylene sulfide (PPS) has excellent oil resistance compared to other resins, and therefore, considering the oil resistance, it is most preferable to use polyphenylene sulfide (PPS).

また、樹脂材料の価格を考慮するならば、ポリアミド６６（ＰＡ６６）を用いるのが好ましく、潤滑油の種類に応じて適宜に決定すればよい。   In view of the price of the resin material, it is preferable to use polyamide 66 (PA66), which may be determined appropriately according to the type of the lubricating oil.

この発明に係る車輪軸受装置において、内方部材は、車輪取付フランジをアウタ側端部の外周に有し、インナ側端部に小径部が形成されたハブ輪と、そのハブ輪の前記小径部に圧入された軸受内輪とからなるものであってもよく、あるいは、車輪取付フランジをアウタ側端部の外周に有するハブ輪と、そのハブ輪のインナ側端部からハブ輪の外径面に圧入された正面組み合わせの一対の軸受内輪からなるものであってもよい。   In the wheel bearing device according to the present invention, the inner member has a wheel mounting flange on the outer periphery of the outer side end portion, a hub wheel having a small diameter portion formed at the inner side end portion, and the small diameter portion of the hub wheel. Or a hub ring having a wheel mounting flange on the outer periphery of the outer end, and an inner end of the hub ring from the inner end of the hub ring to the outer diameter surface of the hub ring. It may consist of a pair of bearing inner rings in a press-fitted front combination.

この発明においては、上記のように、ボールの球径ｄに対する外方部材および内方部材の肩の高さＨ１の比率Ｈ１／ｄを０．２５以上０．５０未満としたことによって、ボールに大きなスラスト荷重や大きなモーメント荷重が負荷された際に、その荷重を外方部材および内方部材の肩で受けることができ、ボールの肩乗り上げを完全に防止することができる。 In the present invention, as described above, by setting the ratio H 1 / d of the height H 1 of the shoulder of the outer member and the inner member to the ball diameter d of the ball to be 0.25 or more and less than 0.50, When a large thrust load or a large moment load is applied to the ball, the load can be received by the shoulders of the outer member and the inner member, and it is possible to completely prevent the ball from riding on the shoulder.

この発明に係る車輪軸受装置の実施の形態を示す縦断正面図A longitudinal front view showing an embodiment of a wheel bearing device according to the present invention 図１のボール組込み部を拡大して示す断面図Sectional drawing which expands and shows the ball installation part of FIG. 図２に示す右側保持器の一部分を示す右側面図The right view which shows a part of right holder shown in FIG. 図２に示す左側保持器の一部分を示す左側面図Left side view showing a part of the left cage shown in FIG. 図２の一部を拡大して示す断面図Sectional drawing which expands and shows a part of FIG. 第１分割保持器と第２分割保持器の一部分を示す平面図The top view which shows a part of a 1st division | segmentation holder | retainer and a 2nd division | segmentation holder | retainer 第１分割保持器のポケットにボールを組込んだ状態での周方向のポケットすきまを示す平面図The top view which shows the pocket clearance of the circumferential direction in the state which incorporated the ball in the pocket of the 1st division cage 第１分割保持器のポケットにボールを組込んだ状態での軸方向のポケットすきまを示す平面図The top view which shows the pocket clearance of the axial direction in the state which incorporated the ball in the pocket of the 1st division cage この発明に係る車輪軸受装置の他の実施の形態を示す縦断正面図Longitudinal front view showing another embodiment of the wheel bearing device according to the present invention この発明に係る車輪軸受装置のさらに他の実施の形態を示す縦断正面図Longitudinal front view showing still another embodiment of the wheel bearing device according to the present invention クラッチレリーズの深みぞ玉軸受を示す断面図Cross-sectional view of a clutch release deep groove ball bearing

以下、この発明の実施の形態を図面に基づいて説明する。図１に示すように、車輪軸受装置は、外方部材１と、その外方部材１の内側に組込まれた内方部材１１と、上記外方部材１と内方部材１１間に組込まれてその両部材を相対的に回転自在に支持する複列のボール２１およびその複列のボール２１の各列のボール２１を保持する一対の保持器３１とからなる。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. As shown in FIG. 1, the wheel bearing device is assembled between an outer member 1, an inner member 11 incorporated inside the outer member 1, and the outer member 1 and the inner member 11. It consists of a double row of balls 21 that rotatably support both members and a pair of cages 31 that hold the balls 21 of each row of the double row of balls 21.

外方部材１は、車体取付用フランジ２を外周に有している。外方部材１は、インナ側端部がナックルＡの嵌合孔ａ内に嵌合され、上記ナックルＡのアウタ側端面に衝合される上記車体取付用フランジ２がボルトの締め付けによってナックルＡに固定される。   The outer member 1 has a vehicle body mounting flange 2 on the outer periphery. The outer member 1 has an inner side end fitted into the fitting hole a of the knuckle A, and the vehicle body mounting flange 2 abutted on the outer side end surface of the knuckle A is attached to the knuckle A by tightening a bolt. Fixed.

ここで、インナ側端部とは、車体に対する車輪軸受装置の組付け状態で車体の幅方向中央側に位置する端部をいい、車体の幅方向外方に位置する側の端部はアウタ側端部という。   Here, the inner side end portion means an end portion located on the center side in the width direction of the vehicle body in the assembled state of the wheel bearing device with respect to the vehicle body, and the end portion located on the outer side in the width direction of the vehicle body is the outer side. It is called the end.

外方部材１の内周には複列の軌道溝３が設けられ、その複列の軌道溝３間に肩４が形成されている。   A double row raceway groove 3 is provided on the inner periphery of the outer member 1, and a shoulder 4 is formed between the double row raceway grooves 3.

内方部材１１は、インナ側端部に小径部１３を有するハブ輪１２と、そのハブ輪１２の上記小径部１３に圧入された軸受内輪１４とからなり、上記ハブ輪１２の外方部材１のアウタ側端面より外方に位置するアウタ側端部の外周には車輪取付フランジ１５が設けられている。   The inner member 11 includes a hub ring 12 having a small-diameter portion 13 at an inner side end portion and a bearing inner ring 14 press-fitted into the small-diameter portion 13 of the hub ring 12, and the outer member 1 of the hub ring 12. A wheel mounting flange 15 is provided on the outer periphery of the outer side end located outside the outer side end surface.

ハブ輪１２の外周には、外方部材１のアウタ側の軌道溝３と対向する軌道溝１６が設けられ、その軌道溝１６のアウタ側に肩１７が形成されている。一方、軸受内輪１４の外周には、外方部材１のインナ側の軌道溝３と対向する軌道溝１８が設けられ、その軌道溝１８のインナ側に肩１９が形成されている。   A raceway groove 16 is provided on the outer periphery of the hub wheel 12 so as to face the raceway groove 3 on the outer side of the outer member 1, and a shoulder 17 is formed on the outer side of the raceway groove 16. On the other hand, a raceway groove 18 is provided on the outer periphery of the bearing inner ring 14 so as to face the raceway groove 3 on the inner side of the outer member 1, and a shoulder 19 is formed on the inner side of the raceway groove 18.

外方部材１のアウタ側軌道溝３とハブ輪１２の軌道溝１６間には複数のボール２１が組込まれ、また、外方部材１のインナ側軌道溝３と軸受内輪１４の軌道溝１８間にもボール２１が組込まれ、これら複列のボール２１は軌道溝３、１６、１８と外向きアンギュラコンタクトの接触とされている。   A plurality of balls 21 are incorporated between the outer side raceway groove 3 of the outer member 1 and the raceway groove 16 of the hub ring 12, and between the inner side raceway groove 3 of the outer member 1 and the raceway groove 18 of the bearing inner ring 14. Also, balls 21 are incorporated, and these double-row balls 21 are in contact with the raceway grooves 3, 16, 18 and the outward angular contact.

ここで、図２に示すように、外方部材１の肩４および内方部材１１の二つの肩１７、１９の高さをＨ１、ボール２１の球径をｄとしたとき、ボール２１の球径ｄに対する肩の高さＨ１の比率Ｈ１／ｄは０．２５以上０．５０未満とされている。ここで、Ｈ１／ｄを０．２５以上としているため、ボール２１の乗り上げを確実に阻止することができる。また、加工性の面から比率Ｈ１／ｄを０．５０未満とした。 Here, as shown in FIG. 2, when the height of the shoulder 4 of the outer member 1 and the two shoulders 17 and 19 of the inner member 11 is H 1 and the ball diameter of the ball 21 is d, The ratio H 1 / d of the shoulder height H 1 to the spherical diameter d is set to 0.25 or more and less than 0.50. Here, since H 1 / d is set to 0.25 or more, it is possible to reliably prevent the ball 21 from climbing. Further, from the viewpoint of workability, the ratio H 1 / d was set to less than 0.50.

図２乃至図６に示すように、保持器３１は、第１分割保持器３２と、その第１分割保持器３２の内側に嵌合された第２分割保持器３３とからなる。   As shown in FIGS. 2 to 6, the retainer 31 includes a first split retainer 32 and a second split retainer 33 fitted inside the first split retainer 32.

図６に示すように、第１分割保持器３２は、環状体３４の軸方向一側面に対向一対のポケット爪３５を周方向に等間隔に形成し、各対向一対のポケット爪３５間に上記環状体３４を刳り抜く２分の１円を超える大きさのポケット３６を設けた合成樹脂の成形品からなり、上記環状体３４の内径は、図２に示すように、ボール２１のピッチ円径（ＰＣＤ）に略等しくされている。   As shown in FIG. 6, the first split holder 32 has a pair of opposed pocket claws 35 formed at equal intervals in the circumferential direction on one side surface in the axial direction of the annular body 34. It consists of a synthetic resin molded product provided with a pocket 36 having a size exceeding one-half circle that cuts through the annular body 34. The inner diameter of the annular body 34 is as shown in FIG. (PCD).

一方、第２分割保持器３３は、環状体３７の軸方向他側面に対向一対のポケット爪３８を周方向に等間隔に形成し、各対向一対のポケット爪３８間に上記環状体３７を刳り抜く２分の１円を超える大きさのポケット３９を設けた合成樹脂の成形品からなり、上記環状体３７の外径はボール２１のピッチ円径（ＰＣＤ）に略等しくされている。   On the other hand, the second split retainer 33 is formed with a pair of opposed pocket claws 38 formed at equal intervals in the circumferential direction on the other side surface in the axial direction of the annular body 37, and the annular body 37 is sandwiched between each pair of opposed pocket claws 38. The molded body is made of a synthetic resin provided with a pocket 39 having a size exceeding a half circle to be extracted. The outer diameter of the annular body 37 is substantially equal to the pitch circle diameter (PCD) of the ball 21.

第１分割保持器３２と第２分割保持器３３は、ポケット３６、３９の開口端が逆向きとなる嵌め合わせとされて、ポケット３６、３９が径方向で対向する組立てとされる。その第１分割保持器３２と第２分割保持器３３の相互間には、図５および図６に示すように、内外に嵌り合う嵌合状態において軸方向に非分離とする連結手段４０が設けられている。   The first split holder 32 and the second split holder 33 are assembled so that the open ends of the pockets 36 and 39 are opposite to each other, and the pockets 36 and 39 are opposed to each other in the radial direction. Between the first divided holder 32 and the second divided holder 33, as shown in FIGS. 5 and 6, there is provided a connecting means 40 that is non-separated in the axial direction in a fitted state that fits inside and outside. It has been.

連結手段４０は、第１分割保持器３２の隣接するポケット３６のポケット爪３５間に内向きの係合爪４１を設け、かつ、環状体３４の内径面に上記係合爪４１と同一軸線上に溝状の係合凹部４２を形成し、第２分割保持器３３の隣接するポケット３９のポケット爪３８間に外向きの係合爪４３を設け、かつ、環状体３７の外径面に上記係合爪４３と同一軸線上に係合凹部４４を形成し、第１分割保持器３２の係合爪４１と第２分割保持器３３の係合凹部４４の係合、および、第２分割保持器３３の係合爪４３と第１分割保持器３２の係合凹部４２の係合によって、第１分割保持器３２と第２分割保持器３３とを軸方向に非分離とする構成とされている。   The connecting means 40 is provided with an inward engagement claw 41 between the pocket claws 35 of the adjacent pockets 36 of the first divided holder 32, and on the inner surface of the annular body 34 on the same axis as the engagement claw 41. A groove-shaped engaging recess 42 is formed in the second split retainer 33 and an outward engaging claw 43 is provided between the pocket claws 38 of the adjacent pockets 39 of the second divided holder 33. An engagement recess 44 is formed on the same axis as the engagement claw 43, and the engagement claw 41 of the first divided holder 32 and the engagement recess 44 of the second divided holder 33 are engaged, and the second divided hold. The first split holder 32 and the second split holder 33 are not separated in the axial direction by the engagement of the engaging claw 43 of the holder 33 and the engaging recess 42 of the first split holder 32. Yes.

ここで、第１分割保持器３２および第２分割保持器３３は、軌道溝１６、１８とボール２１の接触部を潤滑する潤滑油に曝されるため、耐油性に優れた合成樹脂を用いるようにする。そのような合成樹脂として、ポリアミド４６（ＰＡ４６）、ポリアミド６６（ＰＡ６６）、ポリフェニレンスルファイド（ＰＰＳ）を挙げることができる。これらの樹脂は、潤滑油の種類に応じて適切なものを選択して使用すればよい。   Here, since the first split cage 32 and the second split cage 33 are exposed to the lubricating oil that lubricates the contact portions between the raceway grooves 16 and 18 and the balls 21, it is preferable to use a synthetic resin having excellent oil resistance. To. Examples of such a synthetic resin include polyamide 46 (PA46), polyamide 66 (PA66), and polyphenylene sulfide (PPS). These resins may be selected and used according to the type of lubricating oil.

実施の形態で示す車輪軸受装置は上記の構造からなり、その車輪軸受装置の組立てに際しては、第１分割保持器３２内に第２分割保持器３３を嵌合して保持器３１を組立てる。この場合、第１分割保持器３２と第２分割保持器３３はポケット３６、３９の開口端が逆を向く組立てとし、かつ、ポケット３６，３９が径方向で対向する組立てとし、その径方向で対向するポケット３６、３９内にボール２１を組込んで、２組のボールユニットを形成する。   The wheel bearing device shown in the embodiment has the above-described structure, and when assembling the wheel bearing device, the second divided holder 33 is fitted into the first divided holder 32 and the holder 31 is assembled. In this case, the first divided holder 32 and the second divided holder 33 are assembled so that the open ends of the pockets 36 and 39 are opposite to each other, and the pockets 36 and 39 are opposed to each other in the radial direction. The balls 21 are assembled into the opposing pockets 36 and 39 to form two sets of ball units.

２組のボールユニットの形成後、そのボールユニットを外方部材１の軸方向両端から外方部材１の内部に挿入する。このとき、ボールユニットは、第１分割保持器３２のポケット３６の開口端を先にして外方部材１の内部に挿入し、そのボールユニットのボール２１が軌道溝３内に嵌まり込む組付け後において、外方部材１のアウタ側端から内部にハブ輪１２を挿入する。   After the two sets of ball units are formed, the ball units are inserted into the outer member 1 from both axial ends of the outer member 1. At this time, the ball unit is inserted into the outer member 1 with the opening end of the pocket 36 of the first divided holder 32 first, and the ball 21 of the ball unit is fitted into the raceway groove 3. Later, the hub wheel 12 is inserted into the outer member 1 from the outer side end.

ハブ輪１２の軌道溝１６内にボール２１が嵌合するハブ輪１２の組付け後、外方部材１のインナ側端からハブ輪１２の小径部１３の外径面上に軸受内輪１４を圧入し、その軸受内輪１４の軌道溝１８内にボール２１が嵌合する位置まで軸受内輪１４を圧入することによって、車輪軸受装置の組立てが完了する。   After the assembly of the hub wheel 12 in which the ball 21 is fitted in the raceway groove 16 of the hub wheel 12, the bearing inner ring 14 is press-fitted onto the outer diameter surface of the small diameter portion 13 of the hub wheel 12 from the inner side end of the outer member 1. The assembly of the wheel bearing device is completed by press-fitting the bearing inner ring 14 to a position where the ball 21 is fitted into the raceway groove 18 of the bearing inner ring 14.

上記のような車輪軸受装置の組立て状態において、保持器３１は、第１分割保持器３２のポケット３６の開口端が外方部材１の肩４と軸方向で間隔をおいて対向し、また、アウタ側保持器３１の第１分割保持器３２の環状体３４の軸方向のアウタ側端部がハブ輪１２の肩１７と径方向で対向し、かつ、インナ側保持器３１の第１分割保持器３２のインナ側端部が軸受内輪１４の肩１９と径方向で対向する。   In the assembled state of the wheel bearing device as described above, the retainer 31 has the opening end of the pocket 36 of the first split retainer 32 facing the shoulder 4 of the outer member 1 at an interval in the axial direction, The outer side end in the axial direction of the annular body 34 of the first divided cage 32 of the outer side cage 31 faces the shoulder 17 of the hub wheel 12 in the radial direction, and the first divided cage of the inner side cage 31 is held. The inner side end of the vessel 32 faces the shoulder 19 of the bearing inner ring 14 in the radial direction.

このとき、外方部材１の肩４および内方部材１１の肩１７、１９においては、ボール２１の球径ｄに対する肩高さＨ１の比率Ｈ１／ｄが０．５を超えることのない高さとされているため、第１分割保持器３２の内径面と肩１７、１９との対向部間に間隔が確保されることになる。 At this time, in the shoulder 4 of the outer member 1 and the shoulders 17 and 19 of the inner member 11, the ratio H 1 / d of the shoulder height H 1 to the ball diameter d of the ball 21 does not exceed 0.5. Since the height is set, a space is secured between the opposed portions of the inner diameter surface of the first split cage 32 and the shoulders 17 and 19.

このため、内方部材１１が外方部材１に対して回転し、その内方部材１１の軌道溝１６、１８との接触によりボール２１が回転して、そのボール２１と共に保持器３１が回転しても、第１分割保持器３２の内径面は肩１７、１９の外径面と接触することなく回転することになり、内方部材１１は円滑に回転することになる。   For this reason, the inner member 11 rotates with respect to the outer member 1, the ball 21 rotates due to contact with the raceway grooves 16, 18 of the inner member 11, and the cage 31 rotates with the ball 21. Even so, the inner diameter surface of the first split cage 32 will rotate without contacting the outer diameter surfaces of the shoulders 17 and 19, and the inner member 11 will rotate smoothly.

車輪軸受装置においては、車輪が縁石に乗り上げた場合や車両が急旋回する場合にボール２１に大きなモーメント荷重やスラスト荷重が負荷される。このとき、ボール２１の球径ｄに対する外方部材１および内方部材１１の肩４、１７、１９の高さＨ１の比率Ｈ１／ｄを０．２５以上０．５０未満としているため、ボール２１に負荷される荷重を外方部材１および内方部材１１の肩４、１７、１９で受けることができる。このため、ボール２１が肩４、１７、１９に乗り上げて、肩４、１７、１９を損傷させるようなことはない。 In the wheel bearing device, a large moment load or thrust load is applied to the ball 21 when the wheel rides on the curb or when the vehicle turns sharply. At this time, the ratio H 1 / d of the height H 1 of the shoulders 4, 17, 19 of the outer member 1 and the inner member 11 with respect to the ball diameter d of the ball 21 is 0.25 or more and less than 0.50. A load applied to the ball 21 can be received by the shoulders 4, 17, and 19 of the outer member 1 and the inner member 11. Therefore, the ball 21 does not ride on the shoulders 4, 17, 19 and damage the shoulders 4, 17, 19.

実施の形態では、第１分割保持器３２のポケット３６および第２分割保持器３３のポケット３９の開口端にボール２１を抱き込む対向一対のポケット爪３５、３８を設け、上記第１分割保持器３２に形成された対向一対のポケット爪３５と第２分割保持器３３に設けられた対向一対のポケット爪３８を相反する方向に向く組み合わせとし、その組み合わせ状態において、係合爪４１、４３を係合凹部４２、４４に係合して、第１分割保持器３２と第２分割保持器３３を軸方向に非分離としているため、大きなモーメント荷重が負荷されてボール２１に遅れや進みが生じても、保持器３１は脱落するようなことはない。   In the embodiment, a pair of opposed pocket claws 35 and 38 for holding the ball 21 is provided at the open ends of the pocket 36 of the first divided holder 32 and the pocket 39 of the second divided holder 33, and the first divided holder The pair of opposed pawls 35 formed on 32 and the pair of opposed pawls 38 provided on the second split holder 33 are combined to face in opposite directions, and in this combined state, the engaging claws 41 and 43 are engaged. Since the first split cage 32 and the second split cage 33 are not separated in the axial direction by engaging with the mating recesses 42 and 44, a large moment load is applied and the ball 21 is delayed or advanced. However, the cage 31 does not fall off.

ここで、図６および図７に示すように、係合爪４１、４３と係合凹部４２、４４間に形成される周方向すきま５０のすきま量δ１をボール２１とポケット３６、３９間に形成される周方向のポケットすきま５１のすきま量δ２より大きくしておくことにより、大きなモーメント荷重が負荷されてボール２１に遅れ進みが生じ、第１分割保持器３２と第２分割保持器３３とが相対的に回転しても、係合爪４１、４３が係合凹部４２、４４の周方向で対向する側面に当接することはなく、係合爪４１、４３の損傷防止に効果を挙げることができる。 Here, as shown in FIGS. 6 and 7, the clearance δ 1 of the circumferential clearance 50 formed between the engaging claws 41, 43 and the engaging recesses 42, 44 is set between the ball 21 and the pockets 36, 39. By making it larger than the clearance amount δ 2 of the circumferential pocket clearance 51 to be formed, a large moment load is applied and the ball 21 is delayed and advanced, and the first split retainer 32 and the second split retainer 33. And the engagement claws 41 and 43 do not come into contact with the opposite sides of the engagement recesses 42 and 44 in the circumferential direction, and the engagement claws 41 and 43 are effectively prevented from being damaged. be able to.

また、図５および図８に示すように、係合爪４１、４３と係合凹部４２、４４間に形成される軸方向すきま５２のすきま量δ３をボール２１とポケット３６、３９間に形成される軸方向のポケットすきま５３のすきま量δ４より大きくしておくことにより、第１分割保持器３２と第２分割保持器３３に離反する方向の軸方向力が作用した際に、対向一対のポケット爪３５、３８の内面がボール２１の外周面に当接して、係合爪４１、４３が係合凹部４２、４４の軸方向端面に当接するというようなことがなくなり、係合爪４１、４３の損傷防止に効果を挙げることができる。 Further, as shown in FIGS. 5 and 8, a clearance amount δ 3 of the axial clearance 52 formed between the engaging claws 41 and 43 and the engaging recesses 42 and 44 is formed between the ball 21 and the pockets 36 and 39. When the axial force in the direction away from the first split cage 32 and the second split cage 33 is applied to the first split cage 32 and the second split cage 33 by making the clearance larger than the clearance amount δ 4 of the pocket clearance 53 in the axial direction. The inner surfaces of the pocket claws 35 and 38 abut against the outer peripheral surface of the ball 21, and the engagement claws 41 and 43 do not abut against the axial end surfaces of the engagement recesses 42 and 44. , 43 can be effectively prevented.

図１では、ハブ輪１２の内周にスプライン１２ａを形成した駆動輪支持用の車輪軸受装置を示したが、車輪軸受装置は駆動輪支持用に限定されるものではなく、ハブ輪１２の内周にスプラインが形成されていない被駆動輪支持用のものであってもよい。   Although FIG. 1 shows a wheel bearing device for driving wheel support in which a spline 12a is formed on the inner periphery of the hub wheel 12, the wheel bearing device is not limited to supporting the driving wheel. It may be for a driven wheel support in which no spline is formed around the circumference.

また、図１では、内方部材１１が、ハブ輪１２と軸受内輪１４とからなるものを示したが、内方部材１１はこれに限定されるものではない。例えば、図９および図１０に示すように、ハブ輪６０と、そのハブ輪６０の小径部６１の外径面に圧入された正面組み合わせの一対の軸受内輪６２とからなるものであってもよい。この場合、一対の軸受内輪６２のそれぞれに形成された軌道溝６３の一側の肩６４の高さＨ１とボール２１の球形ｄの比率Ｈ１／ｄを０．２５以上０．５０未満とする。 In FIG. 1, the inner member 11 includes the hub ring 12 and the bearing inner ring 14. However, the inner member 11 is not limited to this. For example, as shown in FIGS. 9 and 10, it may be composed of a hub wheel 60 and a pair of front bearing inner rings 62 that are press-fitted into the outer diameter surface of the small diameter portion 61 of the hub wheel 60. . This case, as less than 0.50 respectively formed ratio H 1 / d of the spherical d height H 1 and the ball 21 of the one side of the shoulder 64 of the raceway groove 63 0.25 more pair of bearing inner ring 62 To do.

内方部材１１が、ハブ輪６０と正面組み合わせの一対の軸受内輪６２からなる車輪軸受装置において、外方部材１は、図９に示すように、図１のナックルＡの嵌合孔ａ内に圧入嵌合されるようにしたものであってもよく、あるいは、図１０に示すように車体取付用のフランジ２を外周に有するものであってもよい。   In the wheel bearing device in which the inner member 11 is composed of a pair of bearing inner rings 62 in combination with the hub wheel 60 and the front surface, the outer member 1 is placed in the fitting hole a of the knuckle A in FIG. 1, as shown in FIG. It may be press-fitted or may have a flange 2 for mounting the vehicle body on the outer periphery as shown in FIG.

マニュアル車において、クラッチペダルの操作によってエンジンからトランスミッションへの動力の伝達と遮断を行なうクラッチレリーズ軸受装置においては、軸受を介してクラッチディスクをフライホイールに対して移動させるようにしている。   In a manual vehicle, in a clutch release bearing device that transmits and cuts power from an engine to a transmission by operating a clutch pedal, a clutch disk is moved with respect to the flywheel via the bearing.

この場合、軸受には比較的大きなスラスト荷重が負荷されることになり、その軸受として、標準型の深みぞ玉軸受が採用されていると、負荷されるスラスト荷重により、ボールが外輪および内輪の肩に乗り上げて、肩を損傷させる可能性がある。   In this case, a relatively large thrust load is applied to the bearing, and if a standard deep groove ball bearing is adopted as the bearing, the ball is moved to the outer ring and the inner ring by the applied thrust load. Riding on the shoulder can damage the shoulder.

そこで、図１１に示す参考例のクラッチレリーズ軸受においては、外輪７１の内周に形成された軌道溝７２と内輪７３の外周に形成された軌道溝７４間にボール７５を組込んだ深みぞ玉軸受からなるクラッチレリーズ軸受において、外輪７１のスラスト力を受ける肩７６および内輪７３のスラスト力を受ける肩７７の高さをＨ２、ボール７５の球径をｄとしたとき、ボール７５の球径ｄに対する肩の高さＨ２の比率Ｈ２／ｄを０．２５以上０．５０未満としている。 Therefore, in the clutch release bearing of the reference example shown in FIG. 11, a deep groove ball in which a ball 75 is incorporated between a raceway groove 72 formed on the inner periphery of the outer ring 71 and a raceway groove 74 formed on the outer periphery of the inner ring 73. In a clutch release bearing comprising a bearing, the height of the shoulder 76 that receives the thrust force of the outer ring 71 and the height of the shoulder 77 that receives the thrust force of the inner ring 73 is H 2 , and the ball diameter of the ball 75 is d. The ratio H 2 / d of the shoulder height H 2 to d is 0.25 or more and less than 0.50.

外輪７１のスラスト力を受ける肩７６および内輪７３のスラスト力を受ける肩７７の高さを上記のように規定することによって肩７６、７７に対するボール７５の乗り上げを防止することができる。   By defining the height of the shoulder 76 that receives the thrust force of the outer ring 71 and the height of the shoulder 77 that receives the thrust force of the inner ring 73 as described above, it is possible to prevent the ball 75 from riding on the shoulders 76 and 77.

なお、図１１に示すクラッチレリーズ軸受においては、ボール７５を保持する保持器７８として、図１に示す保持器３１と同一の構成からなる保持器を採用して、保持器７８の脱落を防止するようにしている。   In the clutch release bearing shown in FIG. 11, a cage having the same configuration as the cage 31 shown in FIG. 1 is adopted as the cage 78 that holds the ball 75 to prevent the cage 78 from falling off. I am doing so.

１ 外方部材
３ 軌道溝
４ 肩
１１ 内方部材
１２ ハブ輪
１３ 小径部
１４ 軸受内輪
１５ 車輪取付フランジ
１６ 軌道溝
１７ 肩
１８ 軌道溝
１９ 肩
２１ ボール
３１ 保持器
３２ 第１分割保持器
３３ 第２分割保持器
３４ 環状体
３５ ポケット爪
３６ ポケット
３７ 環状体
３８ ポケット爪
３９ ポケット
４０ 連結手段
４１ 係合爪
６０ ハブ輪
６１ 小径部
６２ 軸受内輪
６３ 軌道溝
６４ 肩 DESCRIPTION OF SYMBOLS 1 Outer member 3 Track groove 4 Shoulder 11 Inner member 12 Hub wheel 13 Small diameter part 14 Bearing inner ring 15 Wheel mounting flange 16 Track groove 17 Shoulder 18 Track groove 19 Shoulder 21 Ball 31 Cage 32 1st division cage 33 2nd Divided cage 34 Annular body 35 Pocket claw 36 Pocket 37 Annular body 38 Pocket claw 39 Pocket 40 Connecting means 41 Engaging claw 60 Hub wheel 61 Small diameter part 62 Bearing inner ring 63 Track groove 64 Shoulder

Claims (9)

複列の軌道溝を内周に有し、その複列の軌道溝間に肩が設けられた外方部材と、その外方部材の複列の軌道溝のそれぞれに対向する複列の軌道溝を外周に有し、その複列の軌道溝のアウタ側軌道溝のアウタ側およびインナ側軌道溝のインナ側のそれぞれに肩が形成された内方部材と、前記外方部材の複列の軌道溝とその軌道溝のそれぞれと対向する内方部材の複列の軌道溝とにアンギュラコンタクトするよう組込まれて内方部材を回転自在に支持する複列のボールと、その各列のボールをそれぞれ逆方向から単独に保持する一対の保持器とからなる車輪軸受装置において、
前記外方部材の内周に設けられた肩および前記内方部材の外周に形成された肩の高さをＨ１、ボールの球径をｄとしたとき、ボールの球径ｄに対する肩の高さＨ１の比率Ｈ１／ｄを０．２５以上０．５０未満としたことを特徴とする車輪軸受装置。 An outer member having a double row raceway groove on the inner periphery and a shoulder provided between the double row raceway grooves, and a double row raceway groove facing each of the double row raceway grooves of the outer member On the outer periphery, and an inner member having shoulders formed on the outer side of the outer side raceway groove and the inner side of the inner side raceway groove of the double row raceway groove, and the double row raceway of the outer member A double row of balls that are incorporated in angular contact with the groove and the double row raceway grooves of the inner member facing each of the raceway grooves and rotatably support the inner member, and each row of balls. In a wheel bearing device comprising a pair of cages that are independently held from opposite directions,
When the height of the shoulder provided on the inner periphery of the outer member and the shoulder formed on the outer periphery of the inner member is H 1 and the ball diameter of the ball is d, the height of the shoulder with respect to the ball diameter d of the ball wheel bearing apparatus being characterized in that a is 0.25 or more but less than 0.50 the ratio H 1 / d of the H 1. 前記保持器が、合成樹脂からなる円筒形の第１分割保持器と、その第１分割保持器の内側に嵌合された合成樹脂製の円筒形の第２分割保持器とからなり、第１分割保持器および第２分割保持器のそれぞれが、環状体を有し、その環状体の軸方向一側面に対向一対のポケット爪が等間隔に形成され、その各対向一対のポケット爪間に前記環状体を刳り抜く２分の１円を超える大きさのボール保持用ポケットが設けられた冠形とされ、その第１分割保持器と第２分割保持器はポケットの開口端が逆向きとされ、ポケットが径方向で対向する組立てとされ、前記第１分割保持器と前記第２分割保持器の相互間に、その両保持器の嵌合により係合して両保持器を軸方向に非分離とする連結手段を設けた請求項１に記載の車輪軸受装置。   The cage is composed of a cylindrical first split cage made of synthetic resin and a cylindrical second split cage made of synthetic resin fitted inside the first split cage. Each of the split cage and the second split cage has an annular body, and a pair of opposed pocket claws are formed at equal intervals on one side surface in the axial direction of the annular body. The crown is provided with a ball holding pocket with a size of more than a half circle that punches through the annular body, and the opening end of the pocket of the first divided holder and the second divided holder is reversed. The pockets are assembled so that the pockets are opposed to each other in the radial direction, and the first and second divided cages are engaged with each other by fitting the two cages so that the two cages are not axially engaged. The wheel bearing device according to claim 1, further comprising a connecting means for separation. 前記連結手段が、前記第１分割保持器の隣接するポケットのポケット爪間に内向きの係合爪を設け、前記第２分割保持器の隣接するポケットのポケット爪間に外向きの係合爪を設け、第１分割保持器の係合爪を第２分割保持器の外径面に形成された係合凹部に係合し、第２分割保持器の係合爪を第１分割保持器の内径面に形成された係合凹部に係合した構成から成る請求項２に記載の車輪軸受装置。   The connecting means has an inward engagement claw between the pocket claws of the adjacent pockets of the first divided holder, and an outward engagement claw between the pocket claws of the adjacent pockets of the second divided holder. Engaging the engaging claw of the first split cage with the engaging recess formed in the outer diameter surface of the second split cage, and engaging the engaging claw of the second split cage with the first split cage. The wheel bearing device according to claim 2, wherein the wheel bearing device is configured to engage with an engagement recess formed on an inner diameter surface. 前記係合爪と係合凹部の係合部の数を３つ以上とした請求項３に記載の車輪軸受装置。   The wheel bearing device according to claim 3, wherein the number of engagement portions of the engagement claw and the engagement recess is three or more. 前記係合爪と係合凹部間に形成される周方向すきまをボールとポケット間に形成される周方向のポケットすきまより大きくした請求項３又は４に記載の車輪軸受装置。   The wheel bearing device according to claim 3 or 4, wherein a circumferential clearance formed between the engaging claw and the engaging recess is larger than a circumferential pocket clearance formed between the ball and the pocket. 前記係合爪と係合凹部間に形成される軸方向すきまをボールとポケット間に形成される軸方向のポケットすきまより大きくした請求項３乃至５のいずれかの項に記載の車輪軸受装置。   The wheel bearing device according to any one of claims 3 to 5, wherein an axial clearance formed between the engaging claw and the engaging recess is larger than an axial pocket clearance formed between the ball and the pocket. 前記第１分割保持器および第２分割保持器が、ポリアミド４６、ポリアミド６６およびポリフェニレンスルファイドの一種からなる請求項２乃至６のいずれかの項に記載の車輪軸受装置。   The wheel bearing device according to any one of claims 2 to 6, wherein the first divided cage and the second divided cage are made of one of polyamide 46, polyamide 66, and polyphenylene sulfide. 前記内方部材が、車輪取付フランジをアウタ側端部の外周に有し、インナ側端部に小径部が形成されたハブ輪と、そのハブ輪の前記小径部に圧入された軸受内輪とからなる請求項１乃至７のいずれかの項に記載の車輪軸受装置。   The inner member has a wheel mounting flange on the outer periphery of the outer side end portion, a hub ring having a small diameter portion formed on the inner side end portion, and a bearing inner ring press-fitted into the small diameter portion of the hub ring. The wheel bearing device according to any one of claims 1 to 7. 前記内方部材が、車輪取付フランジをアウタ側端部の外周に有するハブ輪と、そのハブ輪のインナ側端部からハブ輪の外径面に圧入された正面組み合わせの一対の軸受内輪からなる請求項１乃至７のいずれかの項に記載の車輪軸受装置。   The inner member includes a hub ring having a wheel mounting flange on the outer periphery of the outer side end, and a pair of bearing inner rings in front combination that are press-fitted from the inner side end of the hub ring to the outer diameter surface of the hub ring. The wheel bearing device according to any one of claims 1 to 7.
JP2010172019A 2010-07-30 2010-07-30 Wheel bearing device Pending JP2012031937A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015041030A1 (en) * 2013-09-20 2015-03-26 Ntn株式会社 Crown retainer and ball bearing
JP2015059646A (en) * 2013-09-20 2015-03-30 Ntn株式会社 Sealing device of rolling bearing
DE102015104233A1 (en) 2014-03-24 2015-09-24 Jtekt Corporation Bearing device for a wheel

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015041030A1 (en) * 2013-09-20 2015-03-26 Ntn株式会社 Crown retainer and ball bearing
JP2015059646A (en) * 2013-09-20 2015-03-30 Ntn株式会社 Sealing device of rolling bearing
JP2015059647A (en) * 2013-09-20 2015-03-30 Ntn株式会社 Snap cage and ball bearing
DE102015104233A1 (en) 2014-03-24 2015-09-24 Jtekt Corporation Bearing device for a wheel

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