JP2003202033A - Bearing device for drive wheel - Google Patents

Bearing device for drive wheel

Info

Publication number
JP2003202033A
JP2003202033A JP2002000546A JP2002000546A JP2003202033A JP 2003202033 A JP2003202033 A JP 2003202033A JP 2002000546 A JP2002000546 A JP 2002000546A JP 2002000546 A JP2002000546 A JP 2002000546A JP 2003202033 A JP2003202033 A JP 2003202033A
Authority
JP
Japan
Prior art keywords
bearing
joint
diameter
hub wheel
wheel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2002000546A
Other languages
Japanese (ja)
Other versions
JP4071965B2 (en
Inventor
Hitohiro Ozawa
仁博 小澤
Original Assignee
Ntn Corp
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn Corp, Ntn株式会社 filed Critical Ntn Corp
Priority to JP2002000546A priority Critical patent/JP4071965B2/en
Priority claimed from DE60237669T external-priority patent/DE60237669D1/en
Publication of JP2003202033A publication Critical patent/JP2003202033A/en
Application granted granted Critical
Publication of JP4071965B2 publication Critical patent/JP4071965B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing device for drive wheel which reduces the weight and size thereof by plastic coupling and increasing durability. <P>SOLUTION: In this bearing device for drive wheel having both members 1 and 14 formed integrally with each other by plastic coupling, a hub wheel 1, a constant velocity universal joint 3, and a double row rolling bearing 2 are unitized, one 1a of the inside rolling surfaces of the double row rolling bearing 2 is formed on the outer peripheral surface of the hub wheel 1, and the other 14a is formed on the outer peripheral surface of an outer side joint member 14. The end face 19 of the hub wheel 1 is matched softly to the shoulder part 16 of the outer side joint member 14 and both members 1 and 14 are fitted to each other. In this fitted part, a cured irregularity part 5 is formed on the inner peripheral surface of the hub ring 1, and the fitted part 17b of the outer joint member 14 is increased in diameter crimped into the irregular part 5. Then a hard layer is formed at least on the inner side rolling surface 14a and the surface leading to the shaft part 17 leaving the fitted part 17b of the outer side joint member 14. <P>COPYRIGHT: (C)2003,JPO

Description

【発明の詳細な説明】Detailed Description of the Invention
【0001】[0001]
【発明の属する技術分野】本発明は、自動車等の駆動車
輪を支持する駆動車輪用軸受装置に関するもので、特
に、ハブ輪と等速自在継手と複列の転がり軸受とをユニ
ット化した駆動車輪用軸受装置に関する。
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive wheel bearing device for supporting a drive wheel of an automobile or the like, and more particularly to a drive wheel in which a hub wheel, a constant velocity universal joint, and a double row rolling bearing are unitized. Bearing device.
【0002】[0002]
【従来の技術】FR車の後輪、FF車の前輪、あるいは
4WD車の全輪といった自動車の駆動輪は、駆動車輪用
軸受装置により懸架装置に支持する。近年、駆動車輪用
軸受装置は軽量・コンパクト化を狙って、ハブ輪と等速
自在継手と軸受部とをユニット化する傾向にある。
2. Description of the Related Art Driving wheels of an automobile such as a rear wheel of an FR vehicle, a front wheel of an FF vehicle, or all wheels of a 4WD vehicle are supported by a suspension device by a bearing device for driving wheels. In recent years, a drive wheel bearing device tends to be unitized with a hub wheel, a constant velocity universal joint, and a bearing portion aiming at weight reduction and compactness.
【0003】図4は従来の駆動車輪用軸受装置を示す縦
断面図で、ハブ輪50と、軸受部60と、等速自在継手
70とをユニット化して構成している。ハブ輪50は車
輪(図示せず)を取り付けるための車輪取付フランジ5
1を一体に有し、この車輪取付フランジ51の円周等配
位置には車輪を固定するためのハブボルト52を植設し
ている。
FIG. 4 is a vertical sectional view showing a conventional bearing device for a drive wheel, which is constructed by uniting a hub wheel 50, a bearing portion 60, and a constant velocity universal joint 70. The hub wheel 50 is a wheel mounting flange 5 for mounting a wheel (not shown).
1 is integrally formed, and hub bolts 52 for fixing the wheels are planted at positions equidistantly arranged on the circumference of the wheel mounting flange 51.
【0004】軸受部60は外方部材61と内方部材62
と複列の転動体63、63とからなり、外方部材61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64を一体に有し、内周には複列の転走面61
a、61aを形成している。一方、内方部材62は、前
記した外方部材61の転走面61a、61aに対向する
複列の転走面50a、71aを形成している。この一方
の転走面50aはハブ輪50の外周に一体形成し、他方
の転走面71aは等速自在継手70の外側継手部材71
の外周に一体形成している。複列の転動体63、63を
これら転走面61a、50aと61a、71a間にそれ
ぞれ収容し、保持器65、65で転動自在に保持してい
る。この場合、内方部材62はハブ輪50と外側継手部
材71を指す。軸受部60の端部にはシール66、67
を装着し、軸受内部に封入した潤滑グリースの漏洩と、
外部からの雨水やダスト等の侵入を防止している。
The bearing 60 includes an outer member 61 and an inner member 62.
The outer member 61 integrally has a vehicle body mounting flange 64 for mounting on a vehicle body (not shown) on the outer periphery, and a double row rolling surface on the inner periphery. 61
a and 61a are formed. On the other hand, the inner member 62 forms the double-row rolling surfaces 50a and 71a facing the rolling surfaces 61a and 61a of the outer member 61. The one rolling surface 50a is integrally formed on the outer periphery of the hub wheel 50, and the other rolling surface 71a is the outer joint member 71 of the constant velocity universal joint 70.
Is integrally formed on the outer periphery of the. The double-row rolling elements 63, 63 are housed between the rolling surfaces 61a, 50a and 61a, 71a, respectively, and are rotatably held by the cages 65, 65. In this case, the inner member 62 refers to the hub wheel 50 and the outer joint member 71. Seals 66, 67 are provided at the ends of the bearing 60.
And the leakage of lubricating grease sealed inside the bearing,
Prevents rainwater and dust from entering from the outside.
【0005】等速自在継手70は外側継手部材71と図
示しない継手内輪、ケージ、およびトルク伝達ボールと
からなる。外側継手部材71はカップ状のマウス部72
と、このマウス部72から軸方向に延びる軸部73を有
し、マウス部72の内周には軸方向に延びる曲線状のト
ラック溝72aを形成している。
The constant velocity universal joint 70 comprises an outer joint member 71, a joint inner ring (not shown), a cage, and a torque transmission ball. The outer joint member 71 is a cup-shaped mouth portion 72.
The mouse portion 72 has a shaft portion 73 that extends in the axial direction, and a curved track groove 72a that extends in the axial direction is formed on the inner periphery of the mouse portion 72.
【0006】中空に形成した外側継手部材71の軸部7
3をハブ輪50に内嵌すると共に、ハブ輪50の内周面
に硬化させた凹凸部53と、端部に円筒状の小径段部5
4を形成し、軸部73を拡径してこの凹凸部53に食い
込ませ、その嵌合部を加締めてハブ輪50と外側継手部
材71とを塑性結合させている(特開2001−186
05号)。
The shaft portion 7 of the outer joint member 71 formed hollow
3 is fitted in the hub wheel 50, the uneven portion 53 is hardened on the inner peripheral surface of the hub wheel 50, and the cylindrical small-diameter step portion 5 is formed at the end portion.
4 is formed, the diameter of the shaft portion 73 is expanded to bite into the uneven portion 53, and the fitting portion is caulked to plastically couple the hub wheel 50 and the outer joint member 71 (Japanese Patent Laid-Open No. 2001-186).
No. 05).
【0007】前述の従来の駆動車輪用軸受装置では、セ
レーション等のトルク伝達手段に比べ嵌合部の緩みを防
止でき、かつ嵌合部の摩耗を抑制することができるた
め、装置の耐久性と操縦安定性を向上させることができ
る。また、この結合部はトルク伝達手段と、ハブ輪と外
側継手部材の結合手段とを併せ持つため、締結ナット等
の固定手段が不要となり装置の一層の軽量・コンパクト
化が達成できる。
In the above-described conventional bearing device for a drive wheel, loosening of the fitting portion can be prevented and wear of the fitting portion can be suppressed as compared with torque transmitting means such as serrations, so that durability of the device is improved. The steering stability can be improved. Further, since this connecting portion has both torque transmitting means and connecting means for connecting the hub wheel and the outer joint member, a fixing means such as a fastening nut is not required, and the device can be made further lightweight and compact.
【0008】[0008]
【発明が解決しようとする課題】しかしながら、駆動車
輪用軸受装置において、車両旋回時に過大な曲げモーメ
ント荷重が生じた時、ハブ輪と外側継手部材との突き合
せ部が節となって繰り返し曲げ荷重を受けることにな
る。この時、薄肉のハブ輪の小径段部に過大な応力が発
生し、強度、耐久性が低下する恐れがあった。
However, in the drive wheel bearing device, when an excessive bending moment load is generated when the vehicle turns, the abutting portion between the hub wheel and the outer joint member serves as a node to repeatedly bend the load. Will be received. At this time, excessive stress is generated in the small-diameter stepped portion of the thin-walled hub wheel, which may reduce strength and durability.
【0009】本発明は、このような事情に鑑みてなされ
たもので、塑性結合により、装置の軽量・コンパクト化
を図ると共に、装置の強度、耐久性を向上させた駆動車
輪用軸受装置を提供することを目的としている。
The present invention has been made in view of the above circumstances, and provides a drive wheel bearing device in which the device is made lighter and more compact by plastic coupling, and the device strength and durability are improved. The purpose is to do.
【0010】[0010]
【課題を解決するための手段】係る目的を達成すべく、
本発明のうち請求項1記載の発明は、ハブ輪と等速自在
継手と複列の転がり軸受とをユニット化し、この複列の
転がり軸受における内側転走面のうち一方の内側転走面
と、この内側転走面から軸方向に延びる円筒状の小径段
部を前記ハブ輪に形成し、このハブ輪と前記等速自在継
手の外側継手部材とを嵌合させ、この嵌合部で、前記ハ
ブ輪の内周面に硬化させた凹凸部を形成し、この凹凸部
に前記外側継手部材の嵌合部を拡径させて食い込ませる
ことにより、前記ハブ輪と前記外側継手部材とを一体に
塑性結合した駆動車輪用軸受装置において、前記凹凸部
を、互いに平行な複数列の交叉させた溝で形成すると共
に、少なくともこの溝の一方をブローチ加工によって形
成し、かつこの溝径を前記小径段部の内径よりも小径と
した構成を採用した。
[Means for Solving the Problems] In order to achieve the purpose,
According to a first aspect of the present invention, a hub wheel, a constant velocity universal joint, and a double row rolling bearing are unitized, and one of the inner rolling surfaces of the double row rolling bearing is an inner rolling surface. , A cylindrical small-diameter step portion extending in the axial direction from the inner raceway is formed on the hub wheel, and the hub wheel and the outer joint member of the constant velocity universal joint are fitted together, and at this fitting portion, By forming a hardened concavo-convex portion on the inner peripheral surface of the hub wheel and enlarging the fitting portion of the outer joint member to bite into the concavo-convex portion, the hub wheel and the outer joint member are integrated. In the bearing device for a drive wheel plastically coupled to each other, the concavo-convex portion is formed by a plurality of parallel rows of intersecting grooves, and at least one of the grooves is formed by broaching, and the groove diameter is the small diameter. We adopted a structure with a diameter smaller than the inner diameter of the step .
【0011】このように、交叉溝のうち、ブローチ加工
によって形成する溝の溝径を、ハブ輪の小径段部の内径
よりも小径としたため、ブローチの歯がこの小径段部の
内径を通過する際に生じる擦過傷を確実に防止すること
ができ、最弱部とされるハブ輪の小径段部の強度、耐久
性が低下する恐れがない。
Since the groove diameter of the cross groove formed by broaching is smaller than the inner diameter of the small diameter step portion of the hub wheel, the teeth of the broach pass through the inner diameter of the small diameter step portion. It is possible to reliably prevent scratches that occur at that time, and there is no fear that the strength and durability of the small-diameter stepped portion of the hub wheel, which is the weakest portion, will deteriorate.
【0012】好ましくは、請求項2に記載の発明のよう
に、前記凹凸部を、独立した環状溝と、この環状溝と直
交する軸方向溝とで形成すれば、この平行な複数列の軸
方向溝によって外側継手部材からハブ輪に効率良くトル
クを伝達することができ、また、平行な複数列の環状溝
によって両部材をガタなく軸方向に固着することができ
る。
[0012] Preferably, as in the invention described in claim 2, if the concavo-convex portion is formed by an independent annular groove and an axial groove orthogonal to the annular groove, the parallel rows of shafts are formed. Torque can be efficiently transmitted from the outer joint member to the hub wheel by the direction groove, and both members can be fixed axially without rattling by the parallel rows of annular grooves.
【0013】また、請求項3に記載の発明のように、前
記凹凸部を、螺旋状溝と、この螺旋状溝と交叉する軸方
向溝とで形成しても良い。螺旋状溝ならば、前記環状溝
と変わらぬ機能を有し、旋削等で容易に形成することが
できる。
Further, as in the invention described in claim 3, the concavo-convex portion may be formed by a spiral groove and an axial groove intersecting with the spiral groove. The spiral groove has the same function as the annular groove and can be easily formed by turning or the like.
【0014】また、請求項4に記載の発明のように、前
記凹凸部を、傾斜した第一の螺旋状溝と、この第一の螺
旋状溝と軸対称に第二の螺旋状溝で形成しても良い。こ
うした傾斜した螺旋状溝ならば、一方を旋削等で、他方
をヘリカルブローチ加工で形成することもできるし、両
方をヘリカルブローチ加工でアヤメローレット状に形成
することもできるため量産性が良い。
Further, as in the invention described in claim 4, the concavo-convex portion is formed by an inclined first spiral groove and a second spiral groove in axial symmetry with the first spiral groove. You may. In the case of such an inclined spiral groove, one can be formed by turning or the like and the other can be formed by helical broaching, or both can be formed in an iris knurled shape by helical broaching, and thus mass productivity is good.
【0015】また、請求項5に記載の発明は、前記複列
の転がり軸受における内側転走面のうち一方を前記ハブ
輪に、他方を前記外側継手部材にそれぞれ形成した、所
謂第4世代構造を採用することにより、軸受部とハブ輪
との嵌合等の嵌合部や部品点数を最小限にでき、嵌合部
のミスアライメント等がハブ輪の車輪取付フランジに累
積加算して、フランジ側面の面振れに悪影響を及ぼすの
を抑制することができるので、装置の一層の軽量・コン
パクト化を達成でき、かつ耐久性と操縦安定性を向上さ
せることができる。
The invention according to claim 5 is a so-called fourth generation structure in which one of the inner races of the double-row rolling bearing is formed on the hub wheel and the other is formed on the outer joint member. By adopting, it is possible to minimize the number of fitting parts such as the fitting of the bearing part and the hub wheel, and the number of parts. Since it is possible to prevent the side runout from being adversely affected, it is possible to further reduce the weight and size of the device and improve the durability and steering stability.
【0016】好ましくは、請求項6に記載の発明のよう
に、前記内側転走面から小径段部の端面、および端部内
径に至る表面に硬化層を形成すれば、この小径段部と円
筒面で嵌合する外側継手部材の軸部との摩耗が抑制され
る。
Preferably, when a hardened layer is formed on the surface extending from the inner raceway to the end face of the small-diameter step portion and the inner diameter of the end portion, the small-diameter step portion and the cylinder are formed. Wear of the shaft portion of the outer joint member fitted on the surface is suppressed.
【0017】また、請求項7に記載の発明は、前記ハブ
輪の小径段部と前記外側継手部材の軸部との径方向すき
まを0.5mm以下に設定した。このインロウ嵌合部の
径方向すきまは、小さい程ハブ輪の変形を抑制すること
ができるため有利であるが、ここでは嵌合のし易さを考
慮し、0.50〜−0.10mm、好ましくは0.35
〜−0.05mmに設定している。これにより、繰り返
し曲げ荷重に対し、小径段部の変形を抑制し、その荷重
を円筒面で確実に受けることができるので、装置の耐久
性を格段に向上させることができる。
Further, in the invention according to claim 7, the radial clearance between the small-diameter step portion of the hub wheel and the shaft portion of the outer joint member is set to 0.5 mm or less. The smaller the radial clearance of the inlay fitting portion is, the more the deformation of the hub wheel can be suppressed, which is advantageous, but here, considering ease of fitting, 0.50 to -0.10 mm, Preferably 0.35
It is set to ~ -0.05 mm. This makes it possible to suppress deformation of the small-diameter step portion against repeated bending loads and to reliably receive the load on the cylindrical surface, so that the durability of the device can be significantly improved.
【0018】[0018]
【発明の実施の形態】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、本発明に係る駆動
車輪用軸受の実施形態を示す縦断面図である。
BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an embodiment of a drive wheel bearing according to the present invention.
【0019】この駆動車輪用軸受装置は、ハブ輪1と、
複列の転がり軸受2と、等速自在継手3とをユニット化
して構成している。なお、以下の説明では、車両に組み
付けた状態で、車両の外側寄りとなる側をアウトボード
側(図面左側)、中央寄り側をインボード側(図面右
側)という。
This drive wheel bearing device comprises a hub wheel 1,
The double-row rolling bearing 2 and the constant velocity universal joint 3 are unitized. In the following description, the side closer to the outer side of the vehicle when assembled to the vehicle is referred to as the outboard side (left side in the drawing), and the side closer to the center is referred to as the inboard side (right side in the drawing).
【0020】ハブ輪1は、アウトボード側の端部に車輪
(図示せず)を取り付けるための車輪取付フランジ4を
一体に有している。ハブ輪1の内周面には凹凸部5を形
成し、熱処理によって表面硬さを54〜64HRCの範
囲に硬化層10を形成する(図中散点模様にて示す)。
熱処理としては、局部加熱ができ、硬化層深さの設定が
比較的容易にできる高周波誘導加熱による焼入れが好適
である。
The hub wheel 1 integrally has a wheel mounting flange 4 for mounting a wheel (not shown) on the end portion on the outboard side. The uneven portion 5 is formed on the inner peripheral surface of the hub wheel 1, and the hardened layer 10 is formed by heat treatment so as to have a surface hardness of 54 to 64 HRC (indicated by a dotted pattern in the figure).
As the heat treatment, quenching by high-frequency induction heating, which can locally heat and relatively easily set the depth of the hardened layer, is suitable.
【0021】なお、凹凸部5は、図2および図3に示す
ような複数列の溝を直交させた形状を例示することがで
きる。図2は、アヤメローレット状の凹凸部5を、ブロ
ーチ加工を含む工程で形成するもので、先ず(a)に示
すように、ハブ輪1の内周に旋削等の切削加工によって
平行な複数列の環状溝5aを形成し、次いで、同図
(b)に示すように、ブローチ加工によって環状溝5a
と直交する平行な複数列の軸方向溝5bを形成する。環
状溝5aと軸方向溝5bの形成順序は特に問わず、前記
とは逆に軸方向溝5bを先に形成しても良い。
The uneven portion 5 can be exemplified by a shape in which a plurality of rows of grooves are orthogonal to each other as shown in FIGS. FIG. 2 shows that the iris knurled irregularities 5 are formed in a process including broaching. First, as shown in FIG. To form an annular groove 5a, and then as shown in FIG.
A plurality of parallel rows of axial grooves 5b that are orthogonal to the above are formed. The order of forming the annular groove 5a and the axial groove 5b is not particularly limited, and the axial groove 5b may be formed first, contrary to the above.
【0022】ここで、ハブ輪1の端部に形成した小径段
部1bの内径をD1、環状溝5aの内接円径をD2、溝
底径をD4とし、一方、軸方向溝5bの溝底径をD3と
した時、D1>D3となるように設定することにより、
内径D1部にブローチ加工の際、ブローチの歯が通過す
ることによる発生する擦過傷を防止することができる。
なお、本実施形態ではD1とD2との寸法関係はD1>
D2とし、D4とD1との寸法関係はD4=D1に設定
している。しかし、D4とD1のどちらが大径になって
も良い。繰り返し曲げ応力に対して最弱部とされるハブ
輪1の小径段部1bは、こうした擦過傷だけでなく、後
述する外側継手部材14の軸部17とのインロウすきま
との関係が、微妙に強度、耐久性に影響することが本出
願人の実施した耐久試験等で判ってきた。
Here, the inner diameter of the small-diameter step portion 1b formed at the end of the hub wheel 1 is D1, the inscribed circle diameter of the annular groove 5a is D2, and the groove bottom diameter is D4, while the groove of the axial groove 5b is the groove. By setting D1> D3 when the bottom diameter is D3,
When broaching the inner diameter D1 portion, it is possible to prevent scratches caused by passage of teeth of the broach.
In the present embodiment, the dimensional relationship between D1 and D2 is D1>
D2 is set, and the dimensional relationship between D4 and D1 is set to D4 = D1. However, either D4 or D1 may have a larger diameter. The small-diameter stepped portion 1b of the hub wheel 1 which is the weakest portion against repeated bending stress not only has such scratches but also has a delicate strength in relation to the inlay clearance with the shaft portion 17 of the outer joint member 14 described later. It has been found that the durability test affects the durability test conducted by the applicant.
【0023】本実施例では、ハブ輪1の小径段部1bと
外側継手部材14の軸部17との径方向すきまを従来に
比べ抑制し、0.5mm以下に設定した。このインロウ
嵌合部の径方向すきまは、小さい程ハブ輪1の変形を抑
制することができるため有利であるが、ここでは嵌合の
し易さを考慮し、0.50〜−0.10mm、好ましく
は0.35〜−0.05mmに設定している。これによ
り、繰り返し曲げ荷重に対し、小径段部の変形を抑制
し、その荷重を円筒面で確実に受けることができるの
で、装置の耐久性を格段に向上させることができる。
In this embodiment, the radial clearance between the small-diameter step portion 1b of the hub wheel 1 and the shaft portion 17 of the outer joint member 14 is set to 0.5 mm or less in comparison with the conventional one. The smaller the radial clearance of the inlay fitting portion is, the more the deformation of the hub wheel 1 can be suppressed, which is advantageous, but here, considering ease of fitting, 0.50 to -0.10 mm. , Preferably 0.35 to −0.05 mm. This makes it possible to suppress deformation of the small-diameter step portion against repeated bending loads and to reliably receive the load on the cylindrical surface, so that the durability of the device can be significantly improved.
【0024】ここでは、凹凸部5は、環状溝5aと、こ
れに直交する軸方向溝5bとでアヤメローレット状の凹
凸部5を例示したが、環状溝5aに変えて一本の螺旋溝
であっても環状溝5aと変わらぬ機能を有し、旋削等で
容易に形成することができる。
Here, the uneven portion 5 is exemplified by the annular groove 5a and the axial groove 5b orthogonal to the annular groove 5a, which is an iris knurled uneven portion 5. However, instead of the annular groove 5a, one spiral groove is used. Even if it exists, it has the same function as the annular groove 5a and can be easily formed by turning or the like.
【0025】この他、図3に示すように、複数回のヘリ
カルブローチ加工によって第一の螺旋溝6aを形成し、
次いでこれとは軸対称に二回目のヘリカルブローチ加工
を行なって第二の螺旋溝6bを形成することによってア
ヤメローレット状の凹凸部6を形成することもできる。
ここで、第一の螺旋溝6aを旋削等の切削加工によって
形成しても良い。また、凹凸部5、6の凸部は良好な食
い込み性を確保するために、三角形状等の尖塔形状に形
成する。
In addition, as shown in FIG. 3, the first spiral groove 6a is formed by a plurality of helical broaching processes,
Next, the second helical groove 6b is formed axially symmetrically with respect to the second spiral groove 6b to form the iris knurled uneven portion 6.
Here, the first spiral groove 6a may be formed by cutting such as turning. Further, the convex portions of the concave-convex portions 5 and 6 are formed in a steeple shape such as a triangular shape in order to secure good biting property.
【0026】複列の転がり軸受2は、外方部材7と内方
部材8と複列の転動体9、9とを備え、外方部材7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7aを一体に有し、内周には複列の外側転走面7
b、7bを形成している。一方、内方部材8は、ハブ輪
1と後述する外側継手部材14を指し、外方部材7の外
側転走面7b、7bに対向するアウトボード側の内側転
走面1aをハブ輪1の外周に、またインボード側の内側
転走面14aを外側継手部材14の外周にそれぞれ形成
している。複列の転動体9、9をこれら転走面7b、1
aと7b、14a間にそれぞれ収容し、保持器11、1
1で転動自在に保持している。複列の転がり軸受2の端
部にはシール12、13を装着し、軸受内部に封入した
潤滑グリースの漏洩と、外部からの雨水やダスト等の侵
入を防止している。
The double-row rolling bearing 2 comprises an outer member 7, an inner member 8 and double-row rolling elements 9 and 9. The outer member 7 is mounted on the outer periphery of a vehicle body (not shown). It has a body mounting flange 7a integrally and has a double row of outer raceways 7 on the inner circumference.
b and 7b are formed. On the other hand, the inner member 8 refers to the hub wheel 1 and an outer joint member 14 to be described later, and the inner raceway surface 1a on the outboard side facing the outer raceway surfaces 7b and 7b of the outer member 7 is the hub wheel 1. The inner raceway surface 14 a on the inboard side is formed on the outer circumference and on the outer circumference of the outer joint member 14, respectively. The double-row rolling elements 9 and 9 are attached to these rolling surfaces 7b and 1b.
a and 7b, 14a, respectively, and retainers 11, 1
Holds at 1 for rolling freely. Seals 12 and 13 are attached to the ends of the double-row rolling bearing 2 to prevent leakage of lubricating grease sealed inside the bearing and invasion of rainwater or dust from the outside.
【0027】ハブ輪1の外周において、シール12のシ
ールリップが摺接するシールランド部、内側転走面1
a、および外側継手部材14の肩部16と当接しインロ
ウ部となる小径段部1bの表面に高周波焼入れによって
硬化層10’を形成している(図中散点模様にて示
す)。ここで複列の転がり軸受2は転動体9、9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。
On the outer periphery of the hub wheel 1, the seal land portion with which the seal lip of the seal 12 is in sliding contact, the inner raceway surface 1
A hardened layer 10 'is formed by induction hardening on the surface of the small-diameter stepped portion 1b which is in contact with the shoulder portion 16 of the outer joint member 14 and serves as the inlay portion (indicated by a dotted pattern in the figure). Here, the double row rolling bearing 2 is exemplified by a double row angular ball bearing in which the rolling elements 9 and 9 are balls, but the invention is not limited to this, and a double row tapered roller bearing in which tapered rollers are used for the rolling elements may be used. .
【0028】等速自在継手3は外側継手部材14と継手
内輪N、ケージC、およびトルク伝達ボールBとを備え
ている。外側継手部材14はカップ状のマウス部15
と、このマウス部15の底部をなす肩部16と、この肩
部16から軸方向に延びる軸部17を有し、マウス部1
5の内周には軸方向に延びる曲線状のトラック溝15a
を形成している。
The constant velocity universal joint 3 includes an outer joint member 14, a joint inner ring N, a cage C, and a torque transmitting ball B. The outer joint member 14 is a cup-shaped mouth portion 15
And a shoulder portion 16 forming a bottom portion of the mouse portion 15 and a shaft portion 17 axially extending from the shoulder portion 16.
A curved track groove 15a extending in the axial direction is formed on the inner periphery of the groove 5.
Is formed.
【0029】外側継手部材14を中空に形成し、この肩
部16の外周には前記した内側転走面14aを形成して
いる。また、外側継手部材14の軸部17は小径段部1
7aと嵌合部17bを有している。小径段部17aに圧
入したハブ輪1の小径段部1bを、外側継手部材14の
肩部16に突合せ、嵌合部17bをハブ輪1に内嵌す
る。その後この嵌合部17bの内径にマンドレルを挿入
・抜脱させる等、適宜な手段で嵌合部17bを拡径して
ハブ輪1の凹凸部5に食い込ませ、ハブ輪1と外側継手
部材14とを塑性結合させる。これにより、この結合部
はトルク伝達手段と、ハブ輪1と外側継手部材14の結
合手段とを併せ持つため、従来のセレーション等のトル
ク伝達手段をハブ輪1や外側継手部材14に形成する必
要はなく、また、締結ナット等の固定手段も不要となる
ため、装置の一層の軽量・コンパクト化を実現すること
ができる。
The outer joint member 14 is formed in a hollow shape, and the inner rolling surface 14a is formed on the outer circumference of the shoulder portion 16. Further, the shaft portion 17 of the outer joint member 14 is the small-diameter step portion 1
7a and a fitting portion 17b. The small-diameter step portion 1b of the hub wheel 1 press-fitted into the small-diameter step portion 17a is butted against the shoulder portion 16 of the outer joint member 14, and the fitting portion 17b is internally fitted to the hub wheel 1. After that, the fitting portion 17b is expanded in diameter by an appropriate means such as inserting / removing a mandrel into / from the fitting portion 17b so as to bite into the uneven portion 5 of the hub wheel 1 and the hub wheel 1 and the outer joint member 14 Plastically couple and. As a result, this connecting portion has both torque transmitting means and connecting means for the hub wheel 1 and the outer joint member 14, so that it is not necessary to form conventional torque transmitting means such as serrations on the hub wheel 1 and the outer joint member 14. In addition, since a fastening means such as a fastening nut is not necessary, further weight reduction and compactness of the device can be realized.
【0030】外側継手部材14において、マウス部15
の内周に形成したトラック溝15aとシール13が摺接
するシールランド部から転走面14a、および小径段部
17aに亙って表面に硬化層10”を施す。硬化処理と
して高周波誘導加熱による焼入れが好適である。また、
拡径する嵌合部17bは、鍛造後の素材表面硬さ24H
RC以下の未焼入れ部とし、前記したハブ輪1の凹凸部
5の表面硬さ54〜64HRCとの硬度差を30HRC
以上に設定するのが好ましい。これにより、嵌合部17
bが凹凸部5に容易に、かつ深く食い込み、凹凸部5の
先端が潰れることなく強固に両者を塑性結合することが
できる。
In the outer joint member 14, the mouth portion 15
A hardened layer 10 ″ is applied to the surface from the seal land portion where the track groove 15a formed on the inner periphery of the roller and the seal 13 are in sliding contact to the rolling surface 14a and the small-diameter stepped portion 17a. Is preferred.
The fitting portion 17b that expands in diameter has a material surface hardness of 24H after forging.
The hardness difference between the unhardened portion of RC or less and the surface hardness of the uneven portion 5 of the hub wheel 1 of 54 to 64 HRC is 30 HRC.
It is preferable to set the above. Thereby, the fitting portion 17
b can easily and deeply dig into the concave-convex portion 5, and the tip of the concave-convex portion 5 can be firmly plastically bonded without being crushed.
【0031】中空の外側継手部材14の内径には鋼鈑を
プレス加工によって成形したエンドキャップEを装着し
て、マウス部15に封入された潤滑グリースの外部への
漏洩と外部からのダスト侵入を防止している。
An end cap E formed by pressing a steel plate is attached to the inner diameter of the hollow outer joint member 14 to prevent leakage of the lubricating grease sealed in the mouth portion 15 and intrusion of dust from the outside. To prevent.
【0032】以上、本発明の実施の形態、すなわち、複
列の転がり軸受における内側転走面のうち一方をハブ輪
に、他方を外側継手部材にそれぞれ形成した、所謂第4
世代構造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。例えば、複列の転がり
軸受の内側転走面うち一方の転走面をハブ輪に、他方の
転走面を別体の内輪に形成し、この内輪をハブ輪の小径
段部に圧入した、所謂第3世代構造であっても良い。
As described above, the so-called fourth embodiment of the present invention, that is, one of the inner rolling surfaces of the double row rolling bearing is formed as the hub wheel and the other is formed as the outer joint member.
Although the generation structure has been described, the present invention is not limited to these embodiments at all, and is merely an example, within the scope not departing from the gist of the present invention.
It is needless to say that the present invention can be implemented in various forms, and the scope of the present invention is shown by the description of the claims, and further, the equivalent meanings described in the claims and all the scopes within the scope are provided. Including changes. For example, one of the inner rolling surfaces of the double-row rolling bearing is formed as a hub ring, the other rolling surface is formed as a separate inner ring, and this inner ring is press-fitted into a small diameter step portion of the hub ring. A so-called third generation structure may be used.
【0033】[0033]
【発明の効果】以上詳述したように、本発明に係る駆動
車輪用軸受装置は、ハブ輪と複列の転がり軸受と等速自
在継手をユニット化した駆動車輪用軸受装置において、
ハブ輪の内周に形成する凹凸部を、互いに平行な複数列
の交叉させた溝で構成すると共に、少なくともこの溝の
一方をブローチ加工によって形成し、かつこの溝径を小
径段部の内径よりも小径としたので、ブローチの歯がこ
の小径段部の内径を通過する際に生じる擦過傷を確実に
防止することができ、最弱部とされるハブ輪の小径段部
の強度、耐久性が低下する恐れがない。
As described in detail above, the drive wheel bearing device according to the present invention is a drive wheel bearing device in which a hub wheel, a double row rolling bearing, and a constant velocity universal joint are unitized.
The concavo-convex portion formed on the inner circumference of the hub wheel is composed of a plurality of parallel rows of intersecting grooves, and at least one of the grooves is formed by broaching, and the groove diameter is smaller than the inner diameter of the small diameter step Since the broach teeth have a small diameter, it is possible to reliably prevent scratches that occur when the teeth of the brooch pass through the inner diameter of this small diameter step, and the strength and durability of the small diameter step of the hub wheel, which is the weakest part, are improved. There is no fear of deterioration.
【0034】また、ハブ輪の小径段部と外側継手部材の
軸部とをインロウ部とし、その径方向すきまを、シメシ
ロを含む0.5mm以下に抑制したことにより、繰り返
し曲げ荷重に対し、小径段部の変形を抑制し、その荷重
を円筒面で確実に受けることができるので、装置の耐久
性を格段に向上させることができる。
Further, the small-diameter step portion of the hub wheel and the shaft portion of the outer joint member are made into the inlay portion, and the radial clearance thereof is suppressed to 0.5 mm or less including the interference, so that the small-diameter portion can withstand repeated bending loads. Since the deformation of the step portion can be suppressed and the load can be reliably received by the cylindrical surface, the durability of the device can be significantly improved.
【図面の簡単な説明】[Brief description of drawings]
【図1】本発明に係る駆動車輪用軸受装置の実施形態を
示す縦断面図である。
FIG. 1 is a vertical sectional view showing an embodiment of a drive wheel bearing device according to the present invention.
【図2】(a)は本発明に係るハブ輪の凹凸部形状を示
す縦断面図である。(b)は同上、軸方向溝を示す要部
側面図である。
FIG. 2 (a) is a vertical cross-sectional view showing the shape of the uneven portion of the hub wheel according to the present invention. FIG. 3B is a side view of the main part showing the axial groove.
【図3】本発明に係るハブ輪の凹凸部の形成工程を示す
縦断面図である。
FIG. 3 is a vertical cross-sectional view showing a step of forming an uneven portion of a hub wheel according to the present invention.
【図4】従来の駆動車輪用軸受装置を示す縦断面図であ
る。
FIG. 4 is a vertical cross-sectional view showing a conventional drive wheel bearing device.
【符号の説明】[Explanation of symbols]
1・・・・・・・・・・・・ハブ輪 1a、14a・・・・・・・内側転走面 1b、17a・・・・・・・小径段部 2・・・・・・・・・・・・複列の転がり軸受 3・・・・・・・・・・・・等速自在継手 4・・・・・・・・・・・・車輪取付フランジ 5、6・・・・・・・・・・凹凸部 5a・・・・・・・・・・・環状溝 5b・・・・・・・・・・・軸方向溝 6a・・・・・・・・・・・第一の螺旋溝 6b・・・・・・・・・・・第二の螺旋溝 7・・・・・・・・・・・・外方部材 7a・・・・・・・・・・・車体取付フランジ 7b・・・・・・・・・・・外側転走面 8・・・・・・・・・・・・内方部材 9・・・・・・・・・・・・転動体 10、10’、10”・・・・硬化層 11・・・・・・・・・・・保持器 12、13・・・・・・・・シール 14・・・・・・・・・・・外側継手部材 15・・・・・・・・・・・マウス部 15a・・・・・・・・・・トラック溝 16・・・・・・・・・・・肩部 17・・・・・・・・・・・軸部 17b・・・・・・・・・・嵌合部 50・・・・・・・・・・・ハブ輪 50a、61a、71a・・転走面 51・・・・・・・・・・・車輪取付フランジ 52・・・・・・・・・・・ハブボルト 53・・・・・・・・・・・凹凸部 54・・・・・・・・・・・小径段部 60・・・・・・・・・・・軸受部 61・・・・・・・・・・・外方部材 62・・・・・・・・・・・内方部材 63・・・・・・・・・・・転動体 64・・・・・・・・・・・車体取付フランジ 65・・・・・・・・・・・保持器 66、67・・・・・・・・シール 70・・・・・・・・・・・等速自在継手 71・・・・・・・・・・・外側継手部材 72・・・・・・・・・・・マウス部 72a・・・・・・・・・・トラック溝 73・・・・・・・・・・・軸部 B・・・・・・・・・・・・トルク伝達ボール C・・・・・・・・・・・・ケージ D1・・・・・・・・・・・小径段部の内径 D2・・・・・・・・・・・環状溝の内接円径 D3・・・・・・・・・・・軸方向溝の溝底径 D4・・・・・・・・・・・環状溝の溝底径 E・・・・・・・・・・・・エンドキャップ 1 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Hub wheel 1a, 14a ... Inside rolling surface 1b, 17a ... Small diameter step 2 ・ ・ ・ ・ ・ ・ ・ Double row rolling bearing 3 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Constant velocity universal joint 4 ... Wheel mounting flange 5, 6 ... 5a ..... annular groove 5b ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Axial groove 6a ... First spiral groove 6b ... Second spiral groove 7 ...... Outer member 7a ... ・ Vehicle mounting flange 7b ・ ・ ・ ・ ・ ・ ・ Outer rolling surface 8: Internal member 9 ......... Rolling elements 10, 10 ', 10 "... Hardened layer 11 --- Cage 12, 13 ... Seal 14 ···· Outside joint member 15: Mouse part 15a ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Track groove 16 ... ・ Shoulder 17 ・ ・ ・ ・ ・ ・ ・ Shaft 17b ... Mating part 50 ・ ・ ・ ・ ・ ・ ・ Hub wheel 50a, 61a, 71a ... Rolling surface 51 ・ ・ ・ ・ ・ ・ ・ Wheel mounting flange 52 ... Hub bolt 53 ... 54 ... Small diameter step 60 ・ ・ ・ ・ ・ ・ Bearing part 61 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Outer member 62 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inner member 63 ... Rolling elements 64 ・ ・ ・ ・ ・ ・ Vehicle mounting flange 65 ・ ・ ・ ・ Cage 66, 67 ... Seal 70 ・ ・ ・ ・ ・ ・ ・ Universal universal joint 71 ... Outside joint member 72 ... Mouse part 72a ... Track groove 73 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Shaft B ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Torque transmission ball C ... Cage D1 ・ ・ ・ ・ ・ ・ ・ Inner diameter of small diameter step D2 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Inscribed circle diameter of annular groove D3 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Groove bottom diameter of axial groove D4 ・ ・ ・ ・ ・ ・ ・ ・ ・ ・ Groove bottom diameter of annular groove E ..... End cap
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 FI テーマコート゛(参考) F16C 35/063 F16C 35/063 ─────────────────────────────────────────────────── ─── Continued Front Page (51) Int.Cl. 7 Identification Code FI Theme Coat (Reference) F16C 35/063 F16C 35/063

Claims (7)

    【特許請求の範囲】[Claims]
  1. 【請求項1】ハブ輪と等速自在継手と複列の転がり軸受
    とをユニット化し、この複列の転がり軸受における内側
    転走面のうち一方の内側転走面と、この内側転走面から
    軸方向に延びる円筒状の小径段部を前記ハブ輪に形成
    し、このハブ輪と前記等速自在継手の外側継手部材とを
    嵌合させ、この嵌合部で、前記ハブ輪の内周面に硬化さ
    せた凹凸部を形成し、この凹凸部に前記外側継手部材の
    嵌合部を拡径させて食い込ませることにより、前記ハブ
    輪と前記外側継手部材とを一体に塑性結合した駆動車輪
    用軸受装置において、 前記凹凸部を、互いに平行な複数列の交叉させた溝で形
    成すると共に、少なくともこの溝の一方をブローチ加工
    によって形成し、かつこの溝径を前記小径段部の内径よ
    りも小径としたことを特徴とする駆動車輪用軸受装置。
    Claim: What is claimed is: 1. A hub wheel, a constant velocity universal joint, and a double row rolling bearing are unitized, and one of the inner rolling surfaces of the double row rolling bearing and the inner rolling surface A cylindrical small-diameter step portion extending in the axial direction is formed on the hub wheel, and the hub wheel and the outer joint member of the constant velocity universal joint are fitted to each other, and at this fitting portion, the inner peripheral surface of the hub wheel is fitted. For a drive wheel in which the hub wheel and the outer joint member are integrally plastic-joined by forming a hardened concavo-convex portion and expanding the fitting portion of the outer joint member into the concavo-convex portion so as to bite In the bearing device, the concavo-convex portion is formed by a plurality of rows of intersecting parallel grooves, and at least one of the grooves is formed by broaching, and the diameter of the groove is smaller than the inner diameter of the small-diameter step portion. Drive wheel bearing device characterized by .
  2. 【請求項2】前記凹凸部を、独立した環状溝と、この環
    状溝と直交する軸方向溝とで形成した請求項1に記載の
    駆動車輪用軸受装置。
    2. The bearing device for a drive wheel according to claim 1, wherein the uneven portion is formed by an independent annular groove and an axial groove orthogonal to the annular groove.
  3. 【請求項3】前記凹凸部を、螺旋状溝と、この螺旋状溝
    と交叉する軸方向溝とで形成した請求項1に記載の駆動
    車輪用軸受装置。
    3. The bearing device for a drive wheel according to claim 1, wherein the uneven portion is formed by a spiral groove and an axial groove intersecting with the spiral groove.
  4. 【請求項4】前記凹凸部を、傾斜した第一の螺旋状溝
    と、この第一の螺旋状溝と軸対称に第二の螺旋状溝で形
    成した請求項1に記載の駆動車輪用軸受装置。
    4. The bearing for a drive wheel according to claim 1, wherein the uneven portion is formed by an inclined first spiral groove and a second spiral groove that is axially symmetrical to the first spiral groove. apparatus.
  5. 【請求項5】前記複列の転がり軸受における内側転走面
    のうち他方の内側転走面を前記外側継手部材に形成した
    請求項1乃至4いずれかに記載の駆動車輪用軸受装置。
    5. The drive wheel bearing device according to claim 1, wherein the other inner rolling surface of the inner rolling surfaces of the double-row rolling bearing is formed on the outer joint member.
  6. 【請求項6】前記内側転走面から小径段部の端面、およ
    び端部内径に至る表面に硬化層を形成した請求項1乃至
    5いずれかに記載の駆動車輪用軸受装置。
    6. The drive wheel bearing device according to claim 1, wherein a hardened layer is formed on the surface extending from the inner raceway surface to the end surface of the small-diameter step portion and the inner diameter of the end portion.
  7. 【請求項7】前記ハブ輪の小径段部と前記外側継手部材
    の軸部との径方向すきまを0.5mm以下に設定した請
    求項1乃至6いずれかに記載の駆動車輪用軸受装置。
    7. The bearing device for a drive wheel according to claim 1, wherein a radial clearance between the small-diameter step portion of the hub wheel and the shaft portion of the outer joint member is set to 0.5 mm or less.
JP2002000546A 2002-01-07 2002-01-07 Drive wheel bearing device Expired - Fee Related JP4071965B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2002000546A JP4071965B2 (en) 2002-01-07 2002-01-07 Drive wheel bearing device

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2002000546A JP4071965B2 (en) 2002-01-07 2002-01-07 Drive wheel bearing device
DE60237669T DE60237669D1 (en) 2001-12-21 2002-12-20 Bearing device for a drive wheel of a vehicle
CNB021578524A CN1315663C (en) 2001-12-21 2002-12-20 Bearing device for driving wheel
EP02258836A EP1321312B1 (en) 2001-12-21 2002-12-20 Bearing apparatus for a driving wheel of vehicle
US10/327,549 US7267490B2 (en) 2001-12-21 2002-12-20 Bearing apparatus for a driving wheel of vehicle
KR1020020081550A KR20030053032A (en) 2001-12-21 2002-12-20 A bearing device for driving wheel

Publications (2)

Publication Number Publication Date
JP2003202033A true JP2003202033A (en) 2003-07-18
JP4071965B2 JP4071965B2 (en) 2008-04-02

Family

ID=27640903

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2002000546A Expired - Fee Related JP4071965B2 (en) 2002-01-07 2002-01-07 Drive wheel bearing device

Country Status (1)

Country Link
JP (1) JP4071965B2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007145019A1 (en) * 2006-06-16 2007-12-21 Ntn Corporation Constant velocity universal joint
JP2007333155A (en) * 2006-06-16 2007-12-27 Ntn Corp Constant-velocity universal joint
GB2573633A (en) * 2018-03-21 2019-11-13 Zeiss Carl Industrielle Messtechnik Gmbh Roller bearing for rotary swivel joint

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007145019A1 (en) * 2006-06-16 2007-12-21 Ntn Corporation Constant velocity universal joint
JP2007333155A (en) * 2006-06-16 2007-12-27 Ntn Corp Constant-velocity universal joint
US8128504B2 (en) 2006-06-16 2012-03-06 Ntn Corporation Constant velocity universal joint
GB2573633A (en) * 2018-03-21 2019-11-13 Zeiss Carl Industrielle Messtechnik Gmbh Roller bearing for rotary swivel joint

Also Published As

Publication number Publication date
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