JP2000145805A - Constant velocity universal joint and automobile hub unit with constant velocity universal joint - Google Patents

Constant velocity universal joint and automobile hub unit with constant velocity universal joint

Info

Publication number
JP2000145805A
JP2000145805A JP10320932A JP32093298A JP2000145805A JP 2000145805 A JP2000145805 A JP 2000145805A JP 10320932 A JP10320932 A JP 10320932A JP 32093298 A JP32093298 A JP 32093298A JP 2000145805 A JP2000145805 A JP 2000145805A
Authority
JP
Japan
Prior art keywords
constant velocity
inner ring
velocity joint
ring
peripheral surface
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.)
Pending
Application number
JP10320932A
Other languages
Japanese (ja)
Other versions
JP2000145805A5 (en
Inventor
Yasumasa Mizukoshi
康允 水越
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
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 NSK Ltd filed Critical NSK Ltd
Priority to JP10320932A priority Critical patent/JP2000145805A/en
Publication of JP2000145805A publication Critical patent/JP2000145805A/en
Publication of JP2000145805A5 publication Critical patent/JP2000145805A5/ja
Pending legal-status Critical Current

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Classifications

    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Landscapes

  • Rolling Contact Bearings (AREA)

Abstract

PROBLEM TO BE SOLVED: To install an inner ring in the bore of a retainer without dropping the strength of a retainer in cases where a constant velocity universal joint is to be constructred small by increasing the number of balls constituting the joint while their diameter is made small. SOLUTION: A step 30 is formed at the end in axial direction of at least one of the shoulders 46 and 46a existing at the periphery of an inner ring 2A. Thereby the axial direction dimension of the shoulder 46a is made smaller than the length in the circumferential direction of either of the pockets 10 formed in this retainer. Installation of the inner ring 2A in the bore of the retainer 9 is made by inserting the shoulder 46a on the pocket 10.

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】この発明に係る等速ジョイン
ト及び等速ジョイント付自動車用ハブユニットは、トラ
ンスミッションから駆動輪に駆動力を伝達する為に利用
する。特に、本発明に係る等速ジョイント付自動車用ハ
ブユニットは、所謂第四世代のハブユニットと呼ばれる
もので、独立懸架式サスペンションに支持された駆動軸
｛ＦＦ車（前置エンジン前輪駆動車）の前輪、ＦＲ車
（前置エンジン後輪駆動車）及びＲＲ車（後置エンジン
後輪駆動車）の後輪、４ＷＤ車（四輪駆動車）の全輪｝
を、懸架装置に対して回転自在に支持する為に利用す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention A constant velocity joint and a hub unit for a vehicle with a constant velocity joint according to the present invention are used for transmitting a driving force from a transmission to driving wheels. In particular, the automotive hub unit with a constant velocity joint according to the present invention is a so-called fourth-generation hub unit, which is a drive shaft #FF vehicle (front engine front wheel drive vehicle) supported by an independent suspension type suspension. All wheels of front wheels, FR vehicles (front-engine rear-wheel drive vehicles) and RR vehicles (rear-engine rear-wheel drive vehicles), and 4WD vehicles (four-wheel drive vehicles).
Is used to rotatably support the suspension device.

【０００２】[0002]

【従来の技術】自動車のトランスミッションと、独立懸
架式サスペンションにより支持した駆動輪との間には等
速ジョイントを設けて、デファレンシャルギヤと駆動輪
との相対変位や車輪に付与された舵角に拘らず、エンジ
ンの駆動力を駆動輪に、全周に亙り同一角速度で伝達自
在としている。この様な部分に使用される等速ジョイン
トとして従来から、例えば実開昭５７−１４５８２４〜
５号公報、同５９−１８５４２５号公報、同６２−１２
０２１号公報等に記載されたものが知られている。2. Description of the Related Art A constant velocity joint is provided between a transmission of an automobile and a driving wheel supported by an independent suspension to control a relative displacement between a differential gear and the driving wheel and a steering angle given to the wheel. Instead, the driving force of the engine can be transmitted to the driving wheels at the same angular velocity over the entire circumference. Conventionally, as a constant velocity joint used for such a portion, for example, Japanese Utility Model Laid-Open No.
No. 5, No. 59-185425, No. 62-12
No. 021 is known.

【０００３】この様な従来から知られた等速ジョイント
１は、例えば図１０〜１１に示す様に、内輪２と外輪３
との間の回転力伝達を６個のボール４、４を介して行な
う様に構成している。上記内輪２は、トランスミッショ
ンにより回転駆動される一方の軸５の外端部に固定す
る。又、上記外輪３は、駆動輪を結合する他方の軸６の
内端部に固設する。上記内輪２の外周面２ａには、断面
円弧形の内側係合溝７、７を６本、円周方向に亙り間欠
的に且つ等間隔に、それぞれ円周方向に対し直角方向に
形成している。尚、これら各内側係合溝７、７を形成し
た事に伴い、上記内輪２の外径側部分でこれら各内側係
合溝７、７の間部分には、それぞれが直径方向外方に延
びる、肩部４６、４６が形成される。従って、これら各
肩部４６、４６の軸方向に亙る幅寸法Ｗ46は、上記内輪
２の軸方向寸法Ｌ2 と等しい（Ｗ46＝Ｌ2 ）。又、上記
外輪３の内周面３ａで、上記各内側係合溝７、７と対向
する位置には、やはり断面円弧形の外側係合溝８、８を
６本、円周方向に対し直角方向に形成している。[0003] Such a conventionally known constant velocity joint 1 comprises, for example, as shown in Figs.
Is transmitted through the six balls 4, 4. The inner ring 2 is fixed to the outer end of one shaft 5 driven to rotate by the transmission. Further, the outer wheel 3 is fixed to the inner end of the other shaft 6 for connecting the driving wheels. Six inner engagement grooves 7 having an arc-shaped cross section are formed on the outer peripheral surface 2a of the inner race 2 intermittently and at equal intervals in the circumferential direction, respectively, at right angles to the circumferential direction. ing. In addition, with the formation of these inner engagement grooves 7, 7, the outer diameter side portion of the inner ring 2 extends diametrically outward between the respective inner engagement grooves 7, 7. , Shoulders 46, 46 are formed. Accordingly, the width W 46 of each of the shoulders 46 in the axial direction is equal to the axial dimension L 2 of the inner ring 2 (W 46 = L 2 ). On the inner peripheral surface 3a of the outer race 3, six outer engaging grooves 8, 8 also having an arc-shaped cross section are provided at positions opposed to the inner engaging grooves 7, 7 in the circumferential direction. They are formed at right angles.

【０００４】又、上記内輪２の外周面２ａと外輪３の内
周面３ａとの間には、断面が円弧状で全体が円環状の保
持器９を挟持している。この保持器９の円周方向６箇所
位置で、上記内側、外側両係合溝７、８と整合する位置
には、それぞれポケット１０、１０を円周方向に亙り間
欠的に形成し、各ポケット１０、１０の内側にそれぞれ
１個ずつ、合計６個のボール４、４を保持している。こ
れら各ボール４、４は、それぞれ上記各ポケット１０、
１０に保持された状態で、上記内側、外側両係合溝７、
８に沿い転動自在である。[0004] A retainer 9 having an arc-shaped cross section and being entirely annular is held between the outer peripheral surface 2a of the inner race 2 and the inner peripheral surface 3a of the outer race 3. At six positions in the circumferential direction of the retainer 9, pockets 10, 10 are respectively formed intermittently in the circumferential direction at positions corresponding to the inner and outer engagement grooves 7, 8. A total of six balls 4, 4 are held, one each inside 10, 10. These balls 4 and 4 are respectively connected to the pockets 10 and
10, the inner and outer engagement grooves 7,
It can roll freely along 8.

【０００５】上記各ポケット１０、１０は図１２に示す
様に、円周方向に長い矩形とし、次述する軸交角αが１
８０度未満の状態で等速ジョイント１を運転する事に伴
い、円周方向に隣り合うボール４、４同士の間隔が変化
した場合でも、この変化を吸収できる様にしている。即
ち、上記内側係合溝７、７の底面７ａ、７ａ同士の位置
関係、並びに上記各外側係合溝８、８の底面８ａ、８ａ
同士の位置関係は、図１３に一点鎖線で示す様に、地球
儀の経線の如き関係になっている。上記内輪２の中心軸
と外輪３の中心軸とが一致している（軸交角α＝１８０
°）場合に上記各ボール４、４は、図１３に二点鎖線で
示した、地球儀の赤道に対応する位置の近傍に存在す
る。これに対して、上記内輪２の中心軸と外輪３の中心
軸とが不一致になる（軸交角α＜１８０°）と、等速ジ
ョイント１の回転に伴って上記各ボール４、４が、図１
３の上下方向に往復変位（地球儀の北極方向と南極方向
とに交互に変位）する。この結果、円周方向に隣り合う
ボール４、４同士の間隔が拡縮するので、上記各ポケッ
ト１０、１０を、それぞれ円周方向に長い矩形として、
上記間隔の拡縮を行なえる様にしている。尚、上記内側
係合溝７、７の底面７ａ、７ａと上記各外側係合溝８、
８の底面８ａ、８ａとは、前述の説明から明らかな通
り、互いに同心ではない。従って、上記経線に相当する
線は、これら各係合溝７、８毎に、互いに少しずれた位
置に存在する。As shown in FIG. 12, each of the pockets 10 and 10 has a rectangular shape which is long in the circumferential direction, and has an axis intersection angle α described below of one.
When the constant velocity joint 1 is operated in a state of less than 80 degrees, even if the interval between the balls 4 adjacent in the circumferential direction changes, the change can be absorbed. That is, the positional relationship between the bottom surfaces 7a, 7a of the inner engagement grooves 7, 7, and the bottom surfaces 8a, 8a of the outer engagement grooves 8, 8 are described.
The positional relationship between them is a relationship like a meridian of a globe as shown by a dashed line in FIG. The center axis of the inner ring 2 matches the center axis of the outer ring 3 (the axis intersection angle α = 180).
°), each of the balls 4 exists in the vicinity of the position corresponding to the equator of the globe as shown by the two-dot chain line in FIG. On the other hand, when the center axis of the inner ring 2 and the center axis of the outer ring 3 become inconsistent (axis intersection angle α <180 °), the balls 4, 4 are rotated as the constant velocity joint 1 rotates. 1
3 in the vertical direction (alternately in the north and south poles of the globe). As a result, the distance between the balls 4, 4 adjacent in the circumferential direction expands or contracts, so that each of the pockets 10, 10 is formed as a rectangle long in the circumferential direction.
The interval can be enlarged or reduced. The bottom surfaces 7a, 7a of the inner engaging grooves 7, 7 and the outer engaging grooves 8,
As is clear from the above description, the bottom surfaces 8a of the 8 are not concentric with each other. Therefore, the lines corresponding to the meridians are slightly offset from each other in each of the engagement grooves 7 and 8.

【０００６】更に、図１０に示す様に、前記一方の軸５
と他方の軸６との変位に拘らず、上記各ボール４、４
を、これら両軸５、６の軸交角α、即ち、上記一方の軸
５の中心線ａと他方の軸６の中心線ｂとの交点ｏで両線
ａ、ｂのなす角度αを二等分する、二等分面ｃ内に配置
している。この為に、上記内側係合溝７、７の底面７
ａ、７ａは、上記中心線ａ上で、上記交点ｏからｈだけ
離れた点ｄを中心とする球面上に位置させ、上記外側係
合溝８、８の底面８ａ、８ａは、上記中心線ｂ上で、上
記交点ｏからｈだけ離れた点ｅを中心とする球面上に位
置させている。但し、前記内輪２の外周面２ａ、外輪３
の内周面３ａ、並びに前記保持器９の内外両周面は、そ
れぞれ上記交点ｏを中心とする球面上に位置させて、上
記内輪２の外周面２ａと保持器９の内周面との摺動、並
びに外輪３の内周面３ａと保持器９の外周面との摺動を
自在としている。[0006] Further, as shown in FIG.
Irrespective of the displacement between the ball 4 and the other shaft 6,
Is the angle α between the two axes a and b at the intersection o between the center line a of the one axis 5 and the center line b of the other axis 6. It is arranged in the bisecting plane c. For this reason, the bottom surface 7 of the inner engagement grooves 7
a, 7a are located on the spherical surface centered on a point d, which is separated from the intersection point o by h, on the center line a, and the bottom surfaces 8a, 8a of the outer engaging grooves 8, 8 are located on the center line. On b, it is located on a spherical surface centered on a point e which is separated by h from the intersection o. However, the outer peripheral surface 2a of the inner ring 2 and the outer ring 3
Inner peripheral surface 3a and the inner and outer peripheral surfaces of the cage 9 are respectively positioned on a spherical surface centered at the intersection point o, and the outer peripheral surface 2a of the inner ring 2 and the inner peripheral surface of the cage 9 are Sliding and sliding between the inner peripheral surface 3a of the outer ring 3 and the outer peripheral surface of the retainer 9 are allowed.

【０００７】上述の様に構成する等速ジョイント１の場
合、上記一方の軸５により内輪２を回転させると、この
回転運動は６個のボール４、４を介して外輪３に伝達さ
れ、他方の軸６が回転する。両軸５、６同士の位置関係
（上記軸交角α）が変化した場合には、上記各ボール
４、４が内側、外側両係合溝７、８に沿って転動し、上
記一方の軸５と他方の軸６との変位を許容する。In the case of the constant velocity joint 1 constructed as described above, when the inner ring 2 is rotated by the one shaft 5, this rotational motion is transmitted to the outer ring 3 via the six balls 4, 4. Shaft 6 rotates. When the positional relationship between the two shafts 5 and 6 (the axis intersection angle α) changes, the balls 4 and 4 roll along the inner and outer engagement grooves 7 and 8, and the one shaft 5 and the other shaft 6 are allowed to displace.

【０００８】尚、上述の様な等速ジョイント１を構成す
る保持器９の内側に、同じく内輪２を組み込む作業は、
以下の様にして行なう。先ず、上記保持器９の中心軸方
向と上記内輪２の中心軸方向とを互いに直角方向とした
状態で、この保持器９の一端開口部に、この内輪２を対
向させる。次いで、図１４に示す様に、上記保持器９の
１個のポケット１０（図示の例では、上端部に存在する
ポケット１０）の内側に、上記内輪２の１本の肩部４６
を、直径方向内側から挿入しつつ、この内輪２を上記保
持器９の内径側に挿入する。この際、上記１本の肩部４
６を上記１個のポケット１０内に挿入した分だけ、上記
内輪２をこの挿入方向（図１４の上方）に片寄らせる事
ができる。従って、上述の様に内輪２を保持器９の内側
に挿入する際に、上記１本の肩部４６と直径方向反対側
（図１４の下端側）に存在する肩部４６の先端部（外周
縁部）が、上記保持器９の開口周縁部と干渉する事はな
い。上述の様にして内輪２を保持器９の内径側に挿入し
切ったならば、次いで、上記肩部４６を上記ポケット１
０から抜き出し、最後に上記内輪２を上記保持器９に対
して９０度回転させて、これら内輪２と保持器９との中
心軸同士を互いに一致させる。尚、上述の様に１本の肩
部４６を１個のポケット１０内に挿入できる様にすべ
く、上記保持器９に設ける複数個のポケット１０、１０
のうち、少なくとも１個（通常は直径方向反対側に対向
する２個）のポケット１０は、円周方向に亙る長さ寸法
Ｌ10（図１２）を、上記肩部４６の軸方向に亙る幅寸法
Ｗ46（＝内輪２の軸方向寸法Ｌ2 ）よりも大きく形成し
ておく。[0008] The work of similarly incorporating the inner ring 2 inside the retainer 9 constituting the constant velocity joint 1 as described above is as follows.
This is performed as follows. First, with the center axis direction of the cage 9 and the center axis direction of the inner ring 2 perpendicular to each other, the inner ring 2 is opposed to one end opening of the cage 9. Next, as shown in FIG. 14, one shoulder portion 46 of the inner ring 2 is provided inside one pocket 10 of the retainer 9 (in the illustrated example, the pocket 10 present at the upper end).
Is inserted from the inside in the diametrical direction, and the inner ring 2 is inserted into the inner diameter side of the retainer 9. At this time, the one shoulder 4
The inner ring 2 can be deviated in the insertion direction (upward in FIG. 14) by an amount corresponding to the insertion of the inner ring 6 into the one pocket 10. Therefore, when the inner ring 2 is inserted into the retainer 9 as described above, the distal end (outside) of the shoulder 46 present on the opposite side of the one shoulder 46 in the diametrical direction (the lower end in FIG. 14). The peripheral portion does not interfere with the peripheral portion of the opening of the retainer 9. After the inner ring 2 has been inserted into the inner diameter side of the retainer 9 as described above, the shoulder 46 is then connected to the pocket 1.
Then, the inner ring 2 is rotated by 90 degrees with respect to the retainer 9 so that the central axes of the inner ring 2 and the retainer 9 coincide with each other. In order to insert one shoulder 46 into one pocket 10 as described above, a plurality of pockets 10, 10, 10
At least one (usually two diametrically opposite sides) of the pockets 10 has a length L 10 (FIG. 12) extending in the circumferential direction and a width extending in the axial direction of the shoulder 46. It is formed larger than the dimension W 46 (= the axial dimension L 2 of the inner ring 2 ).

【０００９】等速ジョイントの基本的な構造及び作用は
上述の通りであるが、この様な等速ジョイントと、車輪
を懸架装置に対して回転自在に支持する為の車輪用転が
り軸受ユニットとを一体的に組み合わせる事が、近年研
究されている。即ち、自動車の車輪を懸架装置に回転自
在に支持する為には、外輪と内輪とを転動体を介して回
転自在に組み合わせた車輪用転がり軸受ユニットを使用
する。この様な車輪用転がり軸受ユニットと上述の様な
等速ジョイントとを一体的に組み合わせれば、これら車
輪用転がり軸受ユニットと等速ジョイントとを、全体と
して小型且つ軽量に構成できる。この様な車輪用転がり
軸受ユニットと等速ジョイントとを一体的に組み合わせ
た、本発明の対象となる等速ジョイント付自動車用ハブ
ユニットである、所謂第四世代のハブユニットと呼ばれ
る車輪用転がり軸受ユニットとして従来から、特開平７
−３１７７５４号公報に記載されたものが知られてい
る。Although the basic structure and operation of the constant velocity joint are as described above, such a constant velocity joint and a rolling bearing unit for a wheel for rotatably supporting the wheel with respect to a suspension device. Integral combination has been studied in recent years. That is, in order to rotatably support the wheels of the automobile on the suspension device, a rolling bearing unit for a wheel in which an outer ring and an inner ring are rotatably combined via a rolling element is used. If such a rolling bearing unit for a wheel and the above-described constant velocity joint are integrally combined, the rolling bearing unit for a wheel and the constant velocity joint can be configured to be small and lightweight as a whole. A so-called fourth generation hub unit, a so-called fourth-generation hub unit, which is an automobile hub unit with a constant velocity joint, which is an object of the present invention, in which such a rolling bearing unit for a wheel and a constant velocity joint are integrally combined. Conventionally, as a unit,
What is described in -317754 is known.

【００１０】図１５は、この公報に記載された従来構造
を示している。車両への組み付け状態で、懸架装置に支
持した状態で回転しない外輪１１は、外周面にこの懸架
装置に支持する為の第一の取付フランジ１２を、内周面
に複列の外輪軌道１３、１３を、それぞれ有する。上記
外輪１１の内側には、第一、第二の内輪部材１４、１５
を組み合わせて成るハブ１６を配置している。このうち
の第一の内輪部材１４は、外周面の一端寄り（図１５の
左寄り）部分に車輪を支持する為の第二の取付フランジ
１７を、同じく他端寄り（図１５の右寄り）部分に第一
の内輪軌道１８を、それぞれ設けた円筒状に形成してい
る。これに対して、上記第二の内輪部材１５は、一端部
（図１５の左端部）を、上記第一の内輪部材１４を外嵌
固定する為の円筒部１９とし、他端部（図１５の右端
部）を等速ジョイント１ａの外輪３Ａとし、中間部外周
面に第二の内輪軌道２０を設けている。そして、上記各
外輪軌道１３、１３と上記第一、第二の内輪軌道１８、
２０との間にそれぞれ複数個ずつの転動体２１、２１を
設ける事により、上記外輪１１の内側に上記ハブ１６
を、回転自在に支持している。FIG. 15 shows a conventional structure described in this publication. In an assembled state to a vehicle, the outer ring 11 which does not rotate while being supported by the suspension device has a first mounting flange 12 for supporting the suspension device on the outer peripheral surface, and a double-row outer ring raceway 13 on the inner peripheral surface. 13 respectively. Inside the outer ring 11, first and second inner ring members 14, 15 are provided.
Are arranged. The first inner ring member 14 has a second mounting flange 17 for supporting the wheel at one end (leftward in FIG. 15) of the outer peripheral surface, and a second mounting flange 17 at the other end (rightward in FIG. 15). The first inner raceway 18 is formed in a cylindrical shape provided for each. On the other hand, the second inner ring member 15 has one end (the left end in FIG. 15) as a cylindrical portion 19 for externally fixing the first inner ring member 14, and the other end (FIG. 15). (The right end) is the outer race 3A of the constant velocity joint 1a, and the second inner raceway 20 is provided on the outer peripheral surface of the intermediate part. Then, each of the outer raceways 13, 13 and the first and second inner raceways 18,
By providing a plurality of rolling elements 21, 21 respectively with the hub 16, the hub 16 is provided inside the outer race 11.
Is rotatably supported.

【００１１】又、上記第一の内輪部材１４の内周面と上
記第二の内輪部材１５の外周面との互いに整合する位置
には、それぞれ係止溝２２、２３を形成すると共に、止
め輪２４を、これら両係止溝２２、２３に掛け渡す状態
で設けて、上記第一の内輪部材１４が上記第二の内輪部
材１５から抜け出るのを防止している。更に、上記第二
の内輪部材１５の一端面（図１５の左端面）外周縁部
と、上記第一の内輪部材１４の内周面に形成した段部２
５の内周縁部との間に溶接２６を施して、上記第一、第
二の内輪部材１４、１５同士を結合固定している。Locking grooves 22 and 23 are formed at positions where the inner peripheral surface of the first inner race member 14 and the outer peripheral surface of the second inner race member 15 are aligned with each other. The first inner race member 14 is prevented from falling out of the second inner race member 15 by providing the first inner race member 14 in such a manner as to bridge the two engagement grooves 22 and 23. Further, the outer peripheral edge of one end face (left end face in FIG. 15) of the second inner race member 15 and the stepped portion 2 formed on the inner peripheral face of the first inner race member 14
The first and second inner ring members 14 and 15 are connected and fixed to each other by welding 26 between the inner ring members 5 and 5.

【００１２】更に、上記外輪１１の両端開口部と上記ハ
ブ１６の中間部外周面との間には、ステンレス鋼板等の
金属製で略円筒状のカバー２７ａ、２７ｂと、ゴムの如
きエラストマー等の弾性材製で円環状のシールリング２
８ａ、２８ｂとを設けている。これらカバー２７ａ、２
７ｂ及びシールリング２８ａ、２８ｂは、上記複数の転
動体２１、２１を設置した部分と外部とを遮断し、この
部分に存在するグリースが外部に漏出するのを防止する
と共に、この部分に雨水、塵芥等の異物が侵入する事を
防止する。又、上記第二の内輪部材１５の中間部内側に
は、この第二の内輪部材１５の内側を塞ぐ隔板部２９を
設けて、この第二の内輪部材１５の剛性を確保すると共
に、この第二の内輪部材１５の先端（図１５の左端）開
口からこの第二の内輪部材１５の内側に入り込んだ異物
が、前記等速ジョイント１ａ部分にまで達する事を防止
している。尚、この等速ジョイント１ａは、前述の図１
０〜１１に示した等速ジョイント１と同様に構成してい
る。A substantially cylindrical cover 27a, 27b made of a metal such as a stainless steel plate and an elastomer such as rubber are provided between the openings at both ends of the outer race 11 and the outer peripheral surface of the intermediate portion of the hub 16. Annular seal ring 2 made of elastic material
8a and 28b. These covers 27a, 2
7b and the seal rings 28a and 28b block the portion where the plurality of rolling elements 21 and 21 are installed from the outside, prevent the grease present in this portion from leaking to the outside, and provide rainwater, Prevents foreign matter such as dust from entering. Further, a partition plate portion 29 for closing the inside of the second inner ring member 15 is provided inside the intermediate portion of the second inner ring member 15 so as to secure the rigidity of the second inner ring member 15. Foreign matter that has entered the inside of the second inner ring member 15 from the opening (the left end in FIG. 15) of the second inner ring member 15 is prevented from reaching the constant velocity joint 1a. The constant velocity joint 1a is the same as that shown in FIG.
It has the same configuration as the constant velocity joint 1 shown in 0 to 11.

【００１３】上述の様に構成する車輪用転がり軸受ユニ
ットを車両に組み付ける際には、第一の取付フランジ１
２により外輪１１を懸架装置に支持し、第二の取付フラ
ンジ１７により駆動輪である車輪を第一の内輪部材１４
に固定する。又、エンジンによりトランスミッションを
介して回転駆動される、図示しない駆動軸の先端部を、
等速ジョイント１ａを構成する内輪２の内側にスプライ
ン係合させる。自動車の走行時には、この内輪２の回転
を、複数のボール４、４を介して第二の内輪部材１５を
含むハブ１６に伝達し、上記車輪を回転駆動する。When assembling the rolling bearing unit for a wheel configured as described above to a vehicle, the first mounting flange 1
2 supports the outer ring 11 on the suspension device, and the second mounting flange 17 allows the driving wheel to be connected to the first inner ring member 14.
Fixed to. Also, the tip of a drive shaft (not shown), which is rotationally driven by the engine via a transmission,
The spline is engaged with the inside of the inner ring 2 constituting the constant velocity joint 1a. When the automobile is running, the rotation of the inner ring 2 is transmitted to the hub 16 including the second inner ring member 15 via the plurality of balls 4, 4, and the wheels are rotationally driven.

【００１４】[0014]

【発明が解決しようとする課題】上述の様な第四世代の
ハブユニットをより小型化する為には、上記等速ジョイ
ント１ａを構成する複数個のボール４、４の外接円の直
径を小さくする事が有効である。そして、この外接円の
直径を小さくする為、上記各ボール４、４の直径を小さ
くし、しかも上記等速ジョイント１ａにより伝達可能な
トルクを確保する為には、上記ボール４、４の数を増や
す必要がある。In order to further reduce the size of the fourth-generation hub unit as described above, the diameter of the circumcircle of the plurality of balls 4 constituting the constant velocity joint 1a must be reduced. It is effective to do. In order to reduce the diameter of the circumscribed circle, to reduce the diameter of each of the balls 4, 4, and to secure the torque that can be transmitted by the constant velocity joint 1a, the number of the balls 4, 4 must be reduced. Need to increase.

【００１５】ところが、この様に各ボール４、４の直径
を小さくしてこれら各ボール４、４の外接円の直径を小
さくしつつ、これら各ボール４、４の数を増やす場合、
即ち、これら各ボール４、４を保持する保持器９の直径
寸法を小さくしつつ、この保持器９に形成するポケット
１０、１０の数を増やす場合には、これら各ポケット１
０、１０の円周方向に亙る長さ寸法Ｌ10を大きくできな
い。一方、前述した様に、上記保持器９の内側に内輪２
を挿入する際には、この内輪２の外周面に設けた何れか
の肩部４６を、上記各ポケット１０、１０のうちの何れ
かのポケット１０内に挿入する必要がある。この為、上
述の様な事情により、上記各ポケット１０、１０のうち
の少なくとも１個のポケット１０の円周方向に亙る長さ
寸法Ｌ10を、上記肩部４６の軸方向に亙る幅寸法Ｗ
46（＝内輪２の軸方向寸法Ｌ2 ）よりも大きくできなく
なった場合には、上記保持器９の内側に上記内輪２を挿
入できなくなる。However, when the number of the balls 4 and 4 is increased while the diameter of the balls 4 and 4 is reduced to reduce the diameter of the circumscribed circle of the balls 4 and 4,
That is, when increasing the number of pockets 10 and 10 formed in the retainer 9 while reducing the diameter of the retainer 9 that retains the balls 4 and 4,
Over the circumferential direction of the 0,10 it can not be increased length L 10. On the other hand, as described above, the inner ring 2 is
When inserting the inner ring 2, it is necessary to insert any one of the shoulders 46 provided on the outer peripheral surface of the inner ring 2 into any one of the pockets 10, 10. Therefore, the circumstances as described above, at least one of the length L 10 over the circumferential direction of the pocket 10, the width dimension W over the axial direction of the shoulder portion 46 of the pockets 10, 10
If it can not be larger than 46 (= axial dimension L 2 of the inner ring 2), it can not be inserted to the inner ring 2 on the inner side of the retainer 9.

【００１６】この様な事情に鑑みて、特開平９−１７７
８１０号公報には、等速ジョイントを構成するボールの
数を増やした場合でも、保持器の内側に内輪を挿入でき
る構造が記載されている。この公報に記載された構造の
場合には、上記内輪の外径寸法と上記保持器の一端開口
周縁部の内径寸法とを規制している為、保持器のポケッ
トに内輪の肩部を挿入する事なく、この保持器の内側に
内輪を挿入できる。ところが、この公報に記載された構
造の場合、上記保持器の一端開口周縁部の内径寸法を規
制した結果、この一端開口周縁部の肉厚が薄くなる。こ
れにより、上記保持器の強度が不足し、長期間に亙る使
用に伴い、上記一端開口周縁部から亀裂等の損傷が発生
する可能性が生じる為、好ましくない。本発明の等速ジ
ョイント及び等速ジョイント付自動車用ハブユニット
は、上述の様な事情に鑑み、等速ジョイントを構成する
ボールの直径を小さくしつつ、このボールの数を増やし
た場合でも、保持器の内側に内輪を挿入でき、且つ、こ
の保持器の強度を低下させない構造を実現すべく発明し
たものである。In view of such circumstances, Japanese Unexamined Patent Application Publication No. 9-177
No. 810 describes a structure in which an inner ring can be inserted inside a retainer even when the number of balls constituting a constant velocity joint is increased. In the case of the structure described in this publication, since the outer diameter of the inner ring and the inner diameter of the peripheral edge of one end opening of the retainer are regulated, the shoulder of the inner ring is inserted into the pocket of the retainer. The inner ring can be inserted inside the cage without any problem. However, in the case of the structure described in this publication, as a result of restricting the inner diameter of the peripheral edge of the one-end opening of the retainer, the thickness of the peripheral edge of the one-end opening is reduced. As a result, the strength of the retainer is insufficient, and there is a possibility that damage such as a crack may occur from the peripheral edge of the one end opening with use over a long period of time, which is not preferable. In view of the above-described circumstances, the constant velocity joint and the hub unit for a vehicle with the constant velocity joint according to the present invention reduce the diameter of the ball forming the constant velocity joint and maintain the ball even when the number of balls is increased. The present invention has been made to realize a structure in which the inner ring can be inserted into the inside of the container and the strength of the retainer is not reduced.

【００１７】[0017]

【課題を解決する為の手段】本発明の等速ジョイント及
び等速ジョイント付自動車用ハブユニットのうち、請求
項１に記載した等速ジョイントは、前述した従来の等速
ジョイントと同様に、内輪と、この内輪の外周面の円周
方向に亙り間欠的に存在する複数個所に、それぞれ円周
方向に対し直角方向に形成された断面円弧形の内側係合
溝と、上記内輪の周囲に設けられた外輪と、この外輪の
内周面で上記各内側係合溝と対向する位置に、円周方向
に対し直角方向に形成された断面円弧形の外側係合溝
と、上記内輪の外周面と上記外輪の内周面との間に挟持
され、上記内側、外側両係合溝に整合する位置にそれぞ
れ円周方向に亙り間欠的に複数個のポケットを形成した
保持器と、これら各ポケットの内側に１個ずつ保持され
た状態で内側、外側両係合溝に沿う転動を自在とされ
た、複数個のボールとから成り、これら各ボールを、上
記内輪の中心軸と上記外輪の中心軸との軸交角を二等分
し、これら両中心軸を含む平面に対し直交する二等分面
内に配置している。特に、本発明の等速ジョイントに於
いては、上記内輪の外径側部分でそれぞれ上記各内側係
合溝の間部分に形成された複数本の肩部のうち、少なく
とも１本の肩部の上記内輪の軸方向に亙る幅寸法を、こ
の内輪の軸方向寸法よりも小さくする事により、当該肩
部の軸方向に亙る幅寸法を、上記各ポケットのうちの少
なくとも１個のポケットの円周方向に亙る長さ寸法より
も短くしている。The constant velocity joint according to the first aspect of the present invention is the same as the above-mentioned conventional constant velocity joint. And an inner engaging groove having an arc-shaped cross section formed at a plurality of positions intermittently in the circumferential direction on the outer peripheral surface of the inner ring, each of which is formed in a direction perpendicular to the circumferential direction. An outer ring provided, an outer engaging groove having an arc-shaped cross section formed in a direction perpendicular to the circumferential direction at a position facing the inner engaging grooves on an inner peripheral surface of the outer ring; A retainer sandwiched between an outer peripheral surface and an inner peripheral surface of the outer ring and having a plurality of pockets formed intermittently in a circumferential direction at positions matching the inner and outer engagement grooves, respectively; Inside and outside with one inside each pocket It consists of a plurality of balls that are free to roll along the engagement groove, and divides each of these balls into two at the axis intersection angle between the center axis of the inner ring and the center axis of the outer ring. It is arranged in a bisector orthogonal to the plane containing the axis. In particular, in the constant velocity joint of the present invention, at least one of the plurality of shoulders formed at the outer diameter side portion of the inner race between the inner engagement grooves is formed. By making the width of the inner ring in the axial direction smaller than that of the inner ring, the width of the shoulder in the axial direction is reduced by the circumference of at least one of the pockets. It is shorter than the length dimension in the direction.

【００１８】又、請求項２に記載した等速ジョイント付
自動車用ハブユニットは、やはり前述した従来の等速ジ
ョイント付自動車用ハブユニットと同様に、外周面に懸
架装置に支持固定する為の第一の取付フランジを、内周
面に複列の外輪軌道を、それぞれ有するハブユニット用
の外輪と、中間部外周面に複列の内輪軌道を、一端部外
周面で上記ハブユニット用の外輪の一端開口部から突出
した部分に車輪を支持固定する為の第二の取付フランジ
を、それぞれ有するハブと、上記各外輪軌道と上記各内
輪軌道との間にそれぞれ複数個ずつ転動自在に設けた転
動体と、上記ハブの他端部に設けた等速ジョイントとを
備える。特に、本発明の等速ジョイント付自動車用ハブ
ユニットに於いては、この等速ジョイントが、請求項１
に記載した等速ジョイントである。The vehicle hub unit with a constant velocity joint according to a second aspect of the present invention is similar to the above-described conventional vehicle hub unit with a constant velocity joint, and is provided on the outer peripheral surface for supporting and fixing to a suspension device. One mounting flange, an outer ring for a hub unit having a double-row outer raceway on an inner peripheral surface, and an outer race for a hub unit having a double-row inner raceway on an intermediate outer peripheral surface, and an outer race for the hub unit at one end outer peripheral surface. A second mounting flange for supporting and fixing the wheel to a portion protruding from the one end opening is provided in a freely rotatable manner between the hub and the outer raceway and the inner raceway respectively. A rolling element; and a constant velocity joint provided at the other end of the hub. In particular, in a vehicle hub unit with a constant velocity joint according to the present invention, the constant velocity joint is provided in claim 1.
Is a constant velocity joint described in FIG.

【００１９】[0019]

【作用】上述の様に構成する本発明の等速ジョイント及
び等速ジョイント付自動車用ハブユニットによれば、各
ボールの直径を小さくしつつ、このボールの数を増やす
（例えば７個以上とする）事に伴い、保持器に形成する
各ポケットの円周方向に亙る長さ寸法を大きくできない
場合でも、前述の図１４を参照して説明した従来の組み
込み方法により、保持器の内径側に内輪を組み込める。
即ち、本発明の場合には、内輪の外径側部分に設けた各
肩部のうち、少なくとも１本の肩部の軸方向に亙る幅寸
法を、この内輪の軸方向寸法よりも小さくする事に基づ
き、当該肩部の幅寸法を、上記各ポケットのうちの少な
くとも１個のポケットの円周方向に亙る長さ寸法よりも
短くしている。この為、この様に軸方向に亙る幅寸法を
短くした少なくとも１本の肩部を、上記少なくとも１個
のポケット内に挿入する事ができ、上記従来の組み込み
方法により、保持器の内径側に内輪を組み込む事ができ
る。According to the constant velocity joint and the automobile hub unit with the constant velocity joint of the present invention configured as described above, the number of balls is increased while the diameter of each ball is reduced (for example, 7 or more). Therefore, even if the length of each pocket formed in the cage cannot be increased in the circumferential direction, the inner ring is formed on the inner diameter side of the cage by the conventional mounting method described with reference to FIG. Can be incorporated.
That is, in the case of the present invention, the width of at least one of the shoulders provided on the outer diameter side portion of the inner ring in the axial direction is made smaller than the axial dimension of the inner ring. , The width of the shoulder is made shorter than the length of at least one of the pockets in the circumferential direction. For this reason, at least one shoulder portion having such a reduced width in the axial direction can be inserted into the at least one pocket. Inner ring can be incorporated.

【００２０】従って、等速ジョイントを車輪支持用転が
り軸受ユニットと組み合わせた、所謂第四世代のハブユ
ニットである、本発明の等速ジョイント付自動車用ハブ
ユニットによれば、上記等速ジョイントにより伝達可能
なトルクを確保しつつ、更なる小型化を図る場合にも
（即ち、上記等速ジョイントを構成するボールの直径を
小さくすると共に、このボールの数を増やした場合に
も）、上記保持器に内輪を組み込めなくなると言った不
都合を生じる事はない。又、本発明の場合には、前記公
報に記載された従来構造の様に、保持器の一部分の肉厚
が薄くなる事はない為、この保持器の強度を十分に確保
できる。Therefore, according to the automotive hub unit with a constant velocity joint according to the present invention, which is a so-called fourth generation hub unit in which the constant velocity joint is combined with a wheel supporting rolling bearing unit, the transmission is performed by the constant velocity joint. In order to further reduce the size while securing a possible torque (ie, when reducing the diameter of the balls constituting the constant velocity joint and increasing the number of the balls), the retainer There will be no inconvenience that the inner ring cannot be assembled. Further, in the case of the present invention, since the thickness of a part of the cage is not reduced unlike the conventional structure described in the above-mentioned publication, the strength of the cage can be sufficiently secured.

【００２１】[0021]

【発明の実施の形態】図１〜６は、本発明の実施の形態
の第１例を示している。懸架装置に支持した状態で回転
しない外輪１１は、外周面にこの懸架装置に支持する為
の第一の取付フランジ１２を、内周面に複列の外輪軌道
１３、１３を、それぞれ有する。上記外輪１１の内径側
には、ハブ本体３１と内輪３２とから成るハブ３３を、
この外輪１１と同心に配置している。このハブ３３の外
周面で上記各外輪軌道１３、１３に対向する部分には、
それぞれ第一、第二の内輪軌道１８、２０を設けてい
る。これら両内輪軌道１８、２０のうち、第一の内輪軌
道１８は、上記ハブ本体３１の中間部外周面に直接形成
している。又、このハブ本体３１の中間部のうち、上記
第一の内輪軌道１８を形成した部分よりも内端寄り（図
１の右端寄り）部分に、上記内輪３２を外嵌している。
上記第二の内輪軌道２０は、この内輪３２の外周面に形
成している。そして、上記各外輪軌道１３、１３と上記
第一、第二の内輪軌道１８、２０との間に、それぞれ複
数個ずつの転動体２１、２１を転動自在に設ける事によ
り、上記外輪１１の内側に上記ハブ３３を、回転自在に
支持している。1 to 6 show a first embodiment of the present invention. The outer ring 11 that does not rotate while being supported by the suspension device has a first mounting flange 12 for supporting the suspension device on the outer peripheral surface, and double-row outer ring raceways 13 on the inner peripheral surface. On the inner diameter side of the outer ring 11, a hub 33 including a hub body 31 and an inner ring 32 is provided.
It is arranged concentrically with the outer ring 11. A portion of the outer peripheral surface of the hub 33 that faces the outer raceways 13, 13 includes:
First and second inner raceways 18 and 20, respectively, are provided. Of these two inner raceways 18, 20, the first inner raceway 18 is formed directly on the outer peripheral surface of the intermediate portion of the hub body 31. Further, the inner ring 32 is externally fitted to a portion of the intermediate portion of the hub main body 31 closer to the inner end (toward the right end in FIG. 1) than the portion where the first inner ring track 18 is formed.
The second inner raceway 20 is formed on the outer peripheral surface of the inner race 32. A plurality of rolling elements 21, 21 are provided between each of the outer raceways 13, 13 and the first and second inner raceways 18, 20 so as to be able to roll freely. The hub 33 is rotatably supported inside.

【００２２】図示の例の場合には、上述の様に、上記第
一の内輪軌道１８を上記ハブ本体３１の外周面に直接形
成する事により、この第一の内輪軌道１８の直径を、上
記内輪３２の外周面に形成した第二の内輪軌道２０の直
径よりも小さくしている。又、この様に第一の内輪軌道
１８の直径を第二の内輪軌道２０の直径よりも小さくし
た事に伴い、上記第一の内輪軌道１８と対向する外側
（自動車への組み付け状態で幅方向外側となる側を言
い、図１の左側）の外輪軌道１３の直径を、内側（自動
車への組み付け状態で幅方向中央側となる側を言い、図
１の右側）の外輪軌道１３の直径よりも小さくしてい
る。更に、この外側の外輪軌道１３を形成した、外輪１
１の外半部の外径を、上記内側の外輪軌道１３を形成し
た部分である、上記外輪１１の内半部の外径よりも小さ
くしている。又、図示の例では、この様に第一の内輪軌
道１８及び外側の外輪軌道１３の直径を小さくした事に
伴い、これら第一の内輪軌道１８と外側の外輪軌道１３
との間に設ける転動体２１、２１の数を、上記第二の内
輪軌道２０と内側の外輪軌道１３との間に設ける転動体
２１、２１の数よりも少なくしている。In the case of the illustrated example, as described above, by forming the first inner raceway 18 directly on the outer peripheral surface of the hub body 31, the diameter of the first inner raceway 18 can be reduced. The diameter is smaller than the diameter of the second inner raceway 20 formed on the outer peripheral surface of the inner race 32. In addition, as the diameter of the first inner raceway 18 is made smaller than the diameter of the second inner raceway 20 in this manner, the outer side facing the first inner raceway 18 (in the width direction when assembled to an automobile). The diameter of the outer raceway 13 on the outer side is referred to as the diameter of the outer raceway 13 on the inner side (the center side in the width direction when assembled to the vehicle, and the right side in FIG. 1). Is also small. Further, the outer race 1 having the outer race 13 formed thereon is formed.
The outer diameter of the outer half of the outer race 11 is smaller than the outer diameter of the inner half of the outer race 11, which is the portion where the inner outer raceway 13 is formed. In the illustrated example, the diameters of the first inner raceway 18 and the outer raceway 13 are reduced as described above.
Are smaller than the number of rolling elements 21 provided between the second inner raceway 20 and the inner outer raceway 13.

【００２３】又、上記ハブ本体３１の外端部外周面に
は、このハブ本体３１に車輪を支持固定する為の第二の
取付フランジ１７を、このハブ本体３１と一体に設けて
おり、この第二の取付フランジ１７に、上記車輪を結合
する為の複数本のスタッド３４の基端部を固定してい
る。図示の例の場合にこれら複数本のスタッド３４のピ
ッチ円直径は、上述の様に外輪１１の外半部の外径を、
同じく内半部の外径よりも小さくした分だけ（上記各ス
タッド３４の頭部３５が上記外輪１１の外端部外周面と
干渉しない程度に）小さくしている。尚、上記ハブ本体
３１の外周面のうちで、上記第一の内輪軌道１８を形成
した部分よりも軸方向内方に存在する部分の直径は、こ
の第一の内輪軌道１８に対応する転動体２１、２１の内
接円の直径よりも小さくしている。この理由は、車輪支
持用転がり軸受ユニットの組み立て時に、外輪１１の外
端部内周面に形成した外輪軌道１３の内径側に複数の転
動体２１、２１を組み付けると共に、上記外輪１１の外
端部内周面にシールリング３６を内嵌固定した状態で、
この外輪１１の内径側に上記ハブ本体３１を挿入自在と
する為である。又、上記ハブ本体３１の中間部外周面
で、上記第一の内輪軌道１８と上記内輪３２を外嵌した
部分との間部分には、全周に亙り凹溝状の肉盗み部３７
を形成して、上記ハブ本体３１の軽量化を図っている。A second mounting flange 17 for supporting and fixing a wheel to the hub body 31 is provided integrally with the hub body 31 on the outer peripheral surface of the outer end portion of the hub body 31. The base ends of a plurality of studs 34 for connecting the wheels are fixed to the second mounting flange 17. In the case of the illustrated example, the pitch circle diameter of the plurality of studs 34 is equal to the outer diameter of the outer half of the outer race 11 as described above.
Similarly, the outer diameter of the inner half is made smaller (by the extent that the head 35 of each stud 34 does not interfere with the outer peripheral surface of the outer end of the outer race 11). The diameter of a portion of the outer peripheral surface of the hub main body 31 which is located inward in the axial direction from the portion where the first inner raceway 18 is formed has a rolling element corresponding to the first inner raceway 18. 21 and 21 are smaller than the diameter of the inscribed circle. The reason for this is that, when assembling the rolling bearing unit for supporting the wheel, the plurality of rolling elements 21 are assembled on the inner diameter side of the outer raceway 13 formed on the inner peripheral surface of the outer race 11 and the outer race 11 In a state where the seal ring 36 is fitted and fixed on the peripheral surface,
This is because the hub main body 31 can be freely inserted into the inner diameter side of the outer ring 11. Further, on the outer peripheral surface of the intermediate portion of the hub main body 31, between the first inner raceway 18 and the portion where the inner race 32 is externally fitted, a groove-like thinning portion 37 is formed over the entire circumference.
Is formed to reduce the weight of the hub body 31.

【００２４】又、上記ハブ本体３１に外嵌した内輪３２
が軸方向内端側にずれ動くのを防止して、上記各外輪軌
道１３、１３と上記第一、第二の内輪軌道１８、２０と
の間にそれぞれ複数個ずつ転動自在に設けた、上記各転
動体２１、２１に付与した予圧を適正値に保持すべく、
上記ハブ本体３１の外周面内端寄り部分に全周に亙り形
成した係止凹溝３８に、止め輪３９を係止している。こ
の止め輪３９は、それぞれが半円弧状である、１対の止
め輪素子により構成している。この様な止め輪３９は、
上記各転動体２１、２１に適正な予圧を付与すべく、上
記内輪３２を上記ハブ本体３１に対して軸方向外方に押
圧しつつ、その内周縁部を上記係止凹溝３８に係合させ
る。上記内輪３２を軸方向外方に押圧している力を解除
した状態でも上記各転動体２１、２１に適正な予圧を付
与したままにすべく、上記止め輪３９として、適切な厚
さ寸法を有するものを選択使用する。即ち、上記止め輪
３９として、厚さ寸法が僅かずつ異なるものを複数種類
用意し、上記係止凹溝３８の溝幅等、転がり軸受ユニッ
トの構成各部材の寸法との関係で適切な厚さ寸法を有す
る止め輪３９を選択し、上記係止凹溝３８に係合させ
る。従って、この止め輪３９を係止凹溝３８に係止すれ
ば、上記押圧している力を解除しても、上記内輪３２が
軸方向内端側にずれ動くのを防止して、上記各転動体２
１、２１に適切な予圧を付与したままに保持できる。The inner race 32 externally fitted to the hub body 31
A plurality of rolls are provided between each of the outer raceways 13, 13 and the first and second inner raceways 18, 20 so as to be able to roll freely. In order to maintain the preload applied to each of the rolling elements 21 and 21 at an appropriate value,
A retaining ring 39 is locked in a locking groove 38 formed over the entire circumference in a portion near the inner end of the outer peripheral surface of the hub body 31. The retaining ring 39 is constituted by a pair of retaining ring elements each having a semicircular arc shape. Such a retaining ring 39
In order to apply an appropriate preload to each of the rolling elements 21, the inner peripheral edge thereof is engaged with the locking groove 38 while pressing the inner ring 32 axially outward with respect to the hub main body 31. Let it. The retaining ring 39 should have an appropriate thickness dimension so as to keep the rolling elements 21 and 21 properly preloaded even when the force pressing the inner ring 32 outward in the axial direction is released. Select what you have. That is, as the retaining ring 39, a plurality of types having slightly different thickness dimensions are prepared, and an appropriate thickness is set in relation to the dimensions of the components of the rolling bearing unit, such as the groove width of the locking concave groove 38. A retaining ring 39 having dimensions is selected and engaged with the locking groove 38. Therefore, if the retaining ring 39 is locked in the locking groove 38, even if the pressing force is released, the inner ring 32 is prevented from shifting toward the inner end in the axial direction. Rolling element 2
1, 21 can be maintained with an appropriate preload applied.

【００２５】又、上記止め輪３９を構成する１対の止め
輪素子が直径方向外方に変位し、この止め輪３９が上記
係止凹溝３８から不用意に抜け落ちる事を防止すべく、
この止め輪３９の周囲に、間座４０の一部を配置してい
る。この間座４０は、上記ハブ本体３１の内端部分に設
けた、等速ジョイント用の外輪４１により構成する、本
発明の対象である等速ジョイント１ｂ内に、雨水、塵芥
等の異物が入り込むのを防止する為のブーツ４２の外端
部を外嵌支持する為のものである。又、前記外輪１１の
外端部内周面と上記ハブ本体３１の中間部外周面との間
には前記シールリング３６を、上記外輪１１の内端部内
周面と前記内輪３２の内端部外周面との間には組み合わ
せシールリング４３を、それぞれ設けて、前記複数の転
動体２１、２１を設置した空間４４の両端開口部を塞い
でいる。Further, in order to prevent the pair of retaining ring elements constituting the retaining ring 39 from being displaced radially outward and to prevent the retaining ring 39 from accidentally falling out of the locking groove 38,
A part of the spacer 40 is arranged around the retaining ring 39. The spacer 40 is constituted by an outer ring 41 for a constant velocity joint provided at an inner end portion of the hub main body 31. Foreign matter such as rainwater and dust enters the constant velocity joint 1b which is an object of the present invention. This is for externally supporting the outer end portion of the boot 42 for preventing the above. The seal ring 36 is provided between the outer peripheral surface of the outer end of the outer ring 11 and the outer peripheral surface of the intermediate portion of the hub body 31. The inner peripheral surface of the inner end of the outer race 11 and the outer peripheral surface of the inner end of the inner race 32 are provided. A combination seal ring 43 is provided between the two surfaces to close the openings at both ends of a space 44 in which the plurality of rolling elements 21 are installed.

【００２６】更に、上記ハブ本体３１の内端部で、上記
内輪３２と上記ブーツ４２の外端部とを外嵌した部分
は、上述の様に、等速ジョイント１ｂの外輪となる外輪
４１としている。この外輪４１の内周面には、それぞれ
断面形状が円弧形である８本の外側係合溝８、８を、そ
れぞれ円周方向に対し直角方向（図１の左右方向）に形
成している。又、上記外輪４１の内側には、この外輪４
１と共にツェッパ型の上記等速ジョイント１ｂを構成す
る為の、内輪２Ａを配置している。そして、この内輪２
Ａの外周面に８本の内側係合溝７、７を、それぞれ円周
方向に対し直角方向に形成している。そして、これら各
内側係合溝７、７と上記各外側係合溝８、８との間に、
これら各係合溝７、８毎に１個ずつ、合計８個のボール
４を、保持器９のポケット１０、１０内に保持した状態
で転動自在に設けている。更に、上記内輪２Ａの中心部
には、スプライン孔４５を軸方向に亙り形成している。
自動車への組み付け状態でこのスプライン孔４５には、
図示しない駆動軸の端部をスプライン係合させ、上記内
輪２Ａ及び上記８個のボール４、４を介して、上記ハブ
本体３１を回転駆動自在とする。Further, the portion of the inner end of the hub body 31 where the inner ring 32 and the outer end of the boot 42 are fitted to each other is, as described above, an outer ring 41 serving as the outer ring of the constant velocity joint 1b. I have. Eight outer engagement grooves 8, 8 each having an arc-shaped cross section, are formed in the inner peripheral surface of the outer ring 41 in a direction perpendicular to the circumferential direction (the left-right direction in FIG. 1). I have. Also, the outer ring 4 is provided inside the outer ring 41.
1 and an inner ring 2A for constituting the Zeppa type constant velocity joint 1b. And this inner ring 2
The eight inner engaging grooves 7, 7 are formed on the outer peripheral surface of A at right angles to the circumferential direction. And, between each of these inner engagement grooves 7, 7 and each of the above outer engagement grooves 8, 8,
A total of eight balls 4, one for each of the engagement grooves 7, 8, are provided rotatably while being held in the pockets 10, 10 of the retainer 9. Further, a spline hole 45 is formed in the center of the inner ring 2A in the axial direction.
In the spline hole 45 when assembled to the car,
An end of a drive shaft (not shown) is spline-engaged, and the hub main body 31 is rotatably driven via the inner ring 2A and the eight balls 4,4.

【００２７】又、本例の場合、上記内輪２Ａの外径側部
分で上記各内側係合溝７、７の間部分に存在する、合計
８本の肩部４６、４６ａのうち、１本の肩部４６ａの軸
方向（図１、５の左右方向）に亙る幅寸法Ｗ46a を、上
記内輪２Ａの軸方向寸法Ｌ2Aよりも短く（Ｗ46a ＜
Ｌ2A）している。即ち、上記肩部４６ａの軸方向両端部
で、上記各内側係合溝７、７の底面７ａ、７ａの外接円
（これら各底面７ａ、７ａのうち、直径方向外方に最も
突出する部分の外接円）よりも直径方向外方部分に、こ
の肩部４６ａの長さ方向（図１、５左右方向）中央に向
け凹入する段部３０、３０を形成している。この様な段
部３０、３０は、上記内輪２Ａを鍛造加工により造る際
に形成する。本例の場合、この様な段部３０、３０を形
成する事により上記肩部４６ａの幅寸法Ｗ46a を、上記
各ポケット１０、１０のうちの少なくとも１個のポケッ
ト１０の円周方向に亙る長さ寸法Ｌ10（図１２）よりも
短く（Ｗ46a ＜Ｌ10）している。例えば、一部のポケッ
トの円周方向長さを、残部のポケットの円周方向長さよ
りも大きくした場合には、上記肩部４６ａの幅寸法Ｗ46
a を、少なくとも上記一部のポケットの円周方向に亙る
長さ寸法よりも短くする。In the case of the present embodiment, one of the eight shoulders 46, 46a present between the inner engagement grooves 7, 7 on the outer diameter side of the inner race 2A. the width W 46a over the axial direction of the shoulder portion 46a (the left-right direction in FIGS. 1 and 5), shorter than the axial dimension L 2A of the inner ring 2A (W 46a <
L2A ). That is, at both ends in the axial direction of the shoulder portion 46a, circumscribed circles of the bottom surfaces 7a, 7a of the inner engagement grooves 7, 7 (of the portions of the bottom surfaces 7a, 7a that protrude most outward in the diametric direction). Steps 30, 30 that are recessed toward the center of the shoulder 46 a in the longitudinal direction (left and right directions in FIGS. 1 and 5) are formed in a portion diametrically outward of the circumscribed circle). Such step portions 30, 30 are formed when the inner ring 2A is formed by forging. In the case of this example, by forming such steps 30, 30, the width dimension W 46a of the shoulder 46a extends in the circumferential direction of at least one of the pockets 10, 10. It is shorter (W 46a <L 10 ) than the length L 10 (FIG. 12). For example, when the circumferential length of some of the pockets is larger than the circumferential length of the remaining pockets, the width dimension W 46 of the shoulder 46a is set.
a is made shorter than at least the circumferential length of some of the pockets.

【００２８】尚、上述の様に一部のポケットの円周方向
長さを、残部のポケットの円周方向長さよりも大きくす
るケースとしては、例えば、以下の様な場合がある。即
ち、上記保持器９のポケット１０、１０にボール４を組
み込む作業を、この保持器９の内径側に内輪２Ａを組み
込み、更にこれら保持器９と内輪２Ａとを外輪４１の内
径側に挿入した後に行なう場合には、軸交角α（図１０
参照）を運転時の最小角度よりも更に小さくして、上記
各ポケット１０、１０内に、上記各ボール４を挿入でき
る様にする必要がある。この為、上記各ポケット１０、
１０内に上記ボール４を１個ずつ挿入しつつ、上記保持
器９を回転させる際、先に挿入した各ボール４の円周方
向に亙る変位量は、運転時よりも大きくなる。従って、
これら先に挿入したボール４を保持する各ポケット１
０、１０の円周方向長さは、これら各ボール４の円周方
向に亙る変位を可能にすべく、大きくする必要がある。
但し、最後に挿入するボール４は、その後、組み込み作
業に伴って円周方向に亙り変位する事はないので、この
最後に挿入するボール４を保持するポケット１０の円周
方向長さは、上記他のポケット１０、１０の様に大きく
する必要はない。この場合、通常は上記最後に挿入する
ボール４を保持するポケット１０の円周方向長さを小さ
くして、このポケット１０と円周方向に隣り合う各ポケ
ット１０、１０との間に存在する各柱部の幅寸法を大き
くし、その分上記保持器９の強度を確保する。The case where the circumferential length of some pockets is made larger than the circumferential length of the remaining pockets as described above is, for example, as follows. That is, the operation of incorporating the ball 4 into the pockets 10 and 10 of the retainer 9 is performed by incorporating the inner ring 2A into the inner diameter side of the retainer 9 and inserting the retainer 9 and the inner ring 2A into the inner diameter side of the outer ring 41. In the case of performing later, the axis intersection angle α (FIG. 10)
) Must be made smaller than the minimum angle during operation so that the balls 4 can be inserted into the pockets 10 and 10. Therefore, each of the pockets 10,
When the cage 9 is rotated while inserting the balls 4 one by one into the ball 10, the amount of displacement in the circumferential direction of each ball 4 inserted first becomes larger than that during operation. Therefore,
Each pocket 1 for holding the ball 4 inserted earlier
The circumferential lengths of 0 and 10 need to be increased in order to allow the circumferential displacement of each of these balls 4.
However, since the ball 4 to be inserted last is not displaced in the circumferential direction following the assembling work thereafter, the circumferential length of the pocket 10 for holding the ball 4 to be inserted last is as described above. It need not be as large as the other pockets 10,10. In this case, usually, the circumferential length of the pocket 10 for holding the ball 4 to be inserted last is reduced so that each pocket 10 between the pocket 10 and the adjacent pocket 10 in the circumferential direction is reduced. The width of the pillar portion is increased, and the strength of the retainer 9 is secured accordingly.

【００２９】上述の様な内輪２Ａを組み込んで構成す
る、本例の場合、上記保持器９の内径側に上記内輪２Ａ
を組み込む作業は、前述した従来の場合と同様に、図２
〜５に示す様にして行なう。先ず、上記保持器９の中心
軸の方向と上記内輪２Ａの中心軸の方向とを直角方向と
した状態で、この保持器９の一端（図２〜５の右端）開
口部に、この内輪２Ａを対向させる。次いで、図２〜３
に示す様に、上記保持器９の１個のポケット１０（円周
方向に亙る長さ寸法Ｌ10が、上述した肩部４６ａの幅寸
法Ｗ46a よりも大きなポケット１０。図示の例では、下
端部に存在するポケット１０。）の内側に、上記幅寸法
Ｗ46a を短くした肩部４６ａを、直径方向内側から挿入
しつつ、上記内輪２Ａを上記保持器９の内径側に挿入す
る。この際、上記肩部４６ａを上記１個のポケット１０
内に挿入した分だけ、上記内輪２Ａをこの挿入方向（図
２〜３の下方）に片寄らせる事ができる。従って、上述
の様に内輪２Ａを保持器９の内側に挿入する際に、上記
肩部４６ａと直径方向反対側（図２〜３の上端側）に存
在する肩部４６の先端部（外周縁部）が、上記保持器９
の開口周縁部と干渉する事はない。In the case of this embodiment in which the inner ring 2A as described above is incorporated, the inner ring 2A is provided on the inner diameter side of the retainer 9.
In the same manner as in the conventional case described above,
This is performed as shown in FIGS. First, in a state where the direction of the central axis of the retainer 9 and the direction of the central axis of the inner ring 2A are perpendicular to each other, the inner ring 2A is inserted into one end (the right end in FIGS. Face each other. Then, FIGS.
As shown in, one pocket 10 (length L 10 over the circumferential direction of the retainer 9, in the example of large pocket 10. shown than the width W 46a of the shoulder portion 46a as described above, the lower end The inner ring 2A is inserted into the inner side of the retainer 9 while the shoulder 46a having the reduced width dimension W46a is inserted from the inside in the diametrical direction into the inside of the pocket 10 existing in the portion.). At this time, the shoulder 46a is connected to the one pocket 10
The inner ring 2 </ b> A can be shifted in the insertion direction (downward in FIGS. 2 and 3) by an amount inserted into the inner ring. Therefore, when the inner ring 2A is inserted into the retainer 9 as described above, the distal end (outer peripheral edge) of the shoulder 46 present on the opposite side of the shoulder 46a in the diametrical direction (the upper end in FIGS. 2 and 3). Part) is the retainer 9
Does not interfere with the peripheral edge of the opening.

【００３０】上述の様にして内輪２Ａを保持器９の内径
側に完全に挿入し切ったならば、次いで、図４に示す様
に、上記肩部４６ａを上記ポケット１０から抜き出す。
そして最後に、上記内輪２Ａを上記保持器９に対し９０
度回転させて、図５に示す様に、これら内輪２Ａと保持
器９との中心軸を一致させる。本例の場合、上記肩部４
６ａの幅寸法Ｗ46a は、上述した様に上記１個のポケッ
ト１０の円周方向に亙る長さ寸法Ｌ10よりも短くしてい
る。この為、上記図２〜３に示した過程で、上記肩部４
６ａが上記１個のポケット１０内に挿入できなくなる事
はない。After the inner ring 2A has been completely inserted into the inner diameter side of the retainer 9 as described above, the shoulder 46a is then pulled out of the pocket 10, as shown in FIG.
Finally, the inner ring 2A is moved 90
5, the center axes of the inner ring 2A and the retainer 9 coincide with each other as shown in FIG. In the case of this example, the shoulder 4
Width W 46a of 6a are shorter than the length L 10 over the circumferential direction of the one pocket 10 as described above. For this reason, in the process shown in FIGS.
6a cannot be inserted into the one pocket 10.

【００３１】尚、本例の場合、上述の様に１本の肩部４
６ａの軸方向両端部に段部３０、３０を形成した事に伴
い、等速ジョイント１ｂのジョイント角（内輪２Ａの中
心軸と外輪４１の中心軸との位置関係が直線状態からず
れた角度。図１０に示した軸交角αの補角。）が大きく
なった場合には、上記肩部４６ａにより動力を伝達され
るボール４が、この肩部４６ａの片側に設けた内側係合
溝７の端縁から上記段部３０側に外れる場合も想定され
る。但し、この様な場合でも、残りの肩部４６、４６に
より残りのボール４に動力を伝達できる。従って、上記
肩部４６ａの軸方向両端部に上記段部３０、３０を形成
する事に伴い、上記等速ジョイント１ｂの許容ジョイン
ト角（使用状態でのジョイント角の最大値）が制限され
る事はない。大きなジョイント角を付与したまま、上記
等速ジョイントが大きなトルクの伝達を行なう事は、一
般的ではない。従って、大きなジョイント角を付与した
状態で、トルク伝達に寄与するボール４の数が１個少な
くなる事は、特に問題とはならない。In the case of this example, as described above, one shoulder 4
The joint angle of the constant velocity joint 1b (the angle at which the positional relationship between the central axis of the inner ring 2A and the central axis of the outer ring 41 is shifted from the linear state due to the formation of the step portions 30 at both ends in the axial direction of 6a. When the supplementary angle of the axis intersecting angle α shown in FIG. 10 is increased, the ball 4 to which power is transmitted by the shoulder 46a is disengaged from the inner engaging groove 7 provided on one side of the shoulder 46a. It is also conceivable that the edge part is displaced toward the step 30 side. However, even in such a case, power can be transmitted to the remaining balls 4 by the remaining shoulders 46,46. Therefore, by forming the steps 30, 30 at both ends in the axial direction of the shoulder 46a, the allowable joint angle of the constant velocity joint 1b (the maximum value of the joint angle in use) is limited. There is no. It is not common that the constant velocity joint transmits a large torque while giving a large joint angle. Therefore, it does not matter that the number of the balls 4 contributing to the torque transmission is reduced by one when the large joint angle is provided.

【００３２】又、本例の場合、前述したハブ３３を構成
するハブ本体３１は、例えば図６（ａ）〜（ｄ）に示す
様にして製造する事ができる。先ず、図６（ａ）の右側
に示す様な、Ｓ５３Ｃ〜Ｓ５５Ｃ相当の炭素鋼製の棒状
素材４７を適当な長さに切断して、同図（ａ）の左側に
示す様な短円筒状の前加工素材４８を得る。次いで、こ
の前加工素材４８を軸方向に圧縮する事により、この前
加工素材４８の軸方向中間部を直径方向外方に膨出させ
て、同図（ｂ）に拡大して示す様な、ビヤ樽型の第一中
間素材４９とする。次いで、この第一中間素材４９に鍛
造加工を施し、同図（ｃ）に示す様な第二中間素材５０
とする。この様に第一中間素材４９に鍛造加工を施した
結果、この第一中間素材４９の軸方向中間部で直径方向
外方に膨出した肉の一部が、上記第二中間素材５０の一
端部（図６の左端部）外周面に形成された第二の取付フ
ランジ１７となる。又、上記第二中間素材５０の一端部
内径側部分に上記ハブ本体３１の外端面に開口する凹部
の概略形状が、同じくこの第二中間素材５０の中間部外
周面に第一の内輪軌道１８が、それぞれ形成される。更
に、上記第二中間素材５０に鍛造加工を施し、同図
（ｄ）に示す様な第三中間素材５１とする。この鍛造加
工により、上記第三中間素材５１の他端部（図６の右端
部）内径側部分に、外側係合溝８、８が形成される。そ
の後、上記第三中間素材５１に切削等を施す事により、
各部に必要な形状を与え、続いて必要な個所に高周波焼
き入れ、研磨、超仕上げを施す事で、上記ハブ本体３１
を完成させる。尚、等速ジョイントの外側係合溝８、８
を精密な鍛造仕上げのままとし、研磨、超仕上げを行な
わない加工にする事も可能である。In the case of the present embodiment, the hub main body 31 constituting the hub 33 described above can be manufactured, for example, as shown in FIGS. First, a rod-shaped material 47 made of carbon steel corresponding to S53C to S55C as shown on the right side of FIG. 6A is cut into an appropriate length, and a short cylindrical shape as shown on the left side of FIG. To obtain a pre-processed material 48. Next, by compressing the pre-processed material 48 in the axial direction, the axially intermediate portion of the pre-processed material 48 is bulged outward in the diametrical direction, and as shown in FIG. The first intermediate material 49 is a beer barrel type. Next, the first intermediate material 49 is forged, and a second intermediate material 50 as shown in FIG.
And As a result of forging the first intermediate material 49 in this manner, a portion of the meat that has swelled diametrically outward at the axially intermediate portion of the first intermediate material 49 becomes one end of the second intermediate material 50. The second mounting flange 17 is formed on the outer peripheral surface of the portion (the left end in FIG. 6). Also, the approximate shape of the concave portion that opens at the outer end surface of the hub main body 31 at one end inner diameter side portion of the second intermediate material 50 is the same as that of the first inner ring raceway 18 at the intermediate portion outer peripheral surface of the second intermediate material 50. Are formed respectively. Further, forging is performed on the second intermediate material 50 to obtain a third intermediate material 51 as shown in FIG. By this forging process, outer engagement grooves 8, 8 are formed in the other end (the right end in FIG. 6) inner diameter side portion of the third intermediate material 51. Then, by performing cutting or the like on the third intermediate material 51,
By giving each part a required shape, and then performing high-frequency quenching, polishing, and super-finishing on the required portions, the hub body 31 is formed.
To complete. The outer engagement grooves 8, 8 of the constant velocity joint
It is also possible to use a process that does not perform polishing or super-finishing while leaving a precise forged finish.

【００３３】上述の様に構成する本例の等速ジョイント
付自動車用ハブユニットにより、車輪を懸架装置に対し
て回転自在に支持する作用は、前述した従来の等速ジョ
イント付自動車用ハブユニットの場合と同様である。
又、本発明の等速ジョイント付自動車用ハブユニットの
場合には、上記等速ジョイント１ｂを構成する内側、外
側両係合溝７、８の数を８本とし、上記ボール４、４の
数を８個としているので、使用に伴うハブ３３と内輪２
Ａとの間でのトルク伝達時に、上記等速ジョイント１ｂ
を構成する各ボール４、４毎に加わる負荷の大きさを、
前述の図１０〜１１に示した従来構造の場合よりも小さ
くできる。従って、その分だけ、上記各ボール４、４の
外径を小さくして、環状に配置したこれら各ボール４、
４の外接円の直径、並びに上記複数の外側係合溝８、８
の外接円の直径を小さくできる。そして、この様に外側
係合溝８、８の外接円の直径を小さくした分、車輪支持
用転がり軸受ユニットの外径寸法を小さくして、装置全
体の小型・軽量化を図れる。The function of rotatably supporting the wheels with respect to the suspension device by the vehicle hub unit with the constant velocity joint of the present embodiment configured as described above is the same as that of the conventional vehicle hub unit with the constant velocity joint described above. Same as in the case.
In the case of the hub unit for a vehicle with a constant velocity joint according to the present invention, the number of the inner and outer engagement grooves 7 and 8 constituting the constant velocity joint 1b is set to eight, and the number of the balls 4 and 4 is increased. And the inner ring 2
A at the time of torque transmission between the
The magnitude of the load applied to each of the balls 4 constituting the
It can be smaller than in the case of the conventional structure shown in FIGS. Accordingly, the outer diameter of each of the balls 4, 4 is reduced by that much, and each of the balls 4,
4 and the outer engagement grooves 8, 8
The diameter of the circumscribed circle can be reduced. The outer diameter of the wheel-supporting rolling bearing unit can be reduced by the reduced diameter of the circumcircle of the outer engagement grooves 8, 8, thereby reducing the size and weight of the entire device.

【００３４】特に、本発明の等速ジョイント付自動車用
ハブユニットの場合には、上述の様に各ボール４、４の
直径を小さくしつつ、このボール４、４の数を増やす事
に伴い、上記保持器９に形成する各ポケット１０、１０
の円周方向に亙る長さ寸法Ｌ10を大きくしなくても、上
記保持器９の内径側に上記内輪２Ａを組み込める。更
に、本発明の場合には、前述した特開平９−１７７８１
０号公報に記載された従来構造の様に、保持器９の一部
分の肉厚が薄くなる事はない。この為、この保持器９の
強度を十分に確保できる。この結果、等速ジョイント１
ｂを小型化して、この等速ジョイント１ｂの外輪４１と
車輪支持用転がり軸受ユニットを構成するハブ本体３１
とを一体化した、所謂第四世代のハブユニットの実用化
に寄与できる。In particular, in the case of the automotive hub unit with a constant velocity joint according to the present invention, the number of the balls 4, 4 is increased while the diameter of each of the balls 4, 4 is reduced as described above. Each pocket 10, 10 formed in the retainer 9
Without increasing the length L 10 over the circumferential, incorporate the inner ring 2A on the inner diameter side of the retainer 9. Furthermore, in the case of the present invention, the above-mentioned Japanese Patent Application Laid-Open No.
The thickness of a part of the retainer 9 does not become thin unlike the conventional structure described in Japanese Patent Application Publication No. 0-205. Therefore, the strength of the cage 9 can be sufficiently ensured. As a result, the constant velocity joint 1
b, the outer ring 41 of the constant velocity joint 1b and the hub body 31 forming the wheel supporting rolling bearing unit.
And a so-called fourth generation hub unit.

【００３５】又、図示の例の様に、上記各外側係合溝
８、８の外半部を前記第二の内輪軌道２０の内径側に配
置すれば、車輪支持用転がり軸受ユニットの外径寸法だ
けでなく軸方向寸法も小さくして、装置全体の小型・軽
量化をより有効に図れる。この様な本例の構造は、転が
り軸受ユニット本体を構成する第二の内輪軌道２０を、
上記各外側係合溝８、８よりも大径にせざるを得ず、上
記転がり軸受ユニット本体の外径寸法が大きくなる。こ
の様な本例の構造では、上記ボール４、４の数を６個か
ら７個以上に増やして、その分ボール４、４の外径を小
さくし、上記転がり軸受ユニットの外径寸法を小さくで
きる本発明の効果が、特に大きくなる。If the outer halves of the outer engagement grooves 8, 8 are arranged on the inner diameter side of the second inner raceway 20, as in the example shown in the figure, the outer diameter of the rolling bearing unit for wheel support can be improved. By reducing not only the dimensions but also the axial dimensions, the overall size and weight of the apparatus can be more effectively reduced. Such a structure of the present example is such that the second inner raceway 20 constituting the rolling bearing unit main body is
The outer engagement grooves 8 must be larger in diameter than the outer engagement grooves 8, and the outer diameter of the rolling bearing unit body becomes larger. In such a structure of the present example, the number of the balls 4, 4 is increased from six to seven or more, the outer diameter of the balls 4, 4 is reduced accordingly, and the outer diameter of the rolling bearing unit is reduced. The effect of the present invention that can be achieved is particularly large.

【００３６】更に、図示の例の場合には、前述した様
に、外側の転動体列を構成する各転動体２１、２１のピ
ッチ円直径を小さくする事により、外輪１１の外半部の
外径を小さくできる。そして、この外輪１１の外半部の
外径を小さくした分だけ、ハブ本体３１の外周面に設け
た第二の取付フランジ１７に固定した複数のスタッド３
４のピッチ円直径を小さくできる。従って、上記ハブ本
体３１の軸方向寸法を大きくする事なく、上記スタッド
３４を支持固定する上記第二の取付フランジ１７の外径
を小さくして、車輪支持用転がり軸受ユニットの小型・
軽量化を、更に有効に図れる。Further, in the case of the illustrated example, as described above, by reducing the pitch circle diameter of each of the rolling elements 21 constituting the outer row of rolling elements, the outer half of the outer ring 11 can be formed. The diameter can be reduced. The plurality of studs 3 fixed to the second mounting flange 17 provided on the outer peripheral surface of the hub body 31 by an amount corresponding to the reduced outer diameter of the outer half of the outer ring 11.
4 can be reduced in pitch circle diameter. Therefore, the outer diameter of the second mounting flange 17 for supporting and fixing the stud 34 is reduced without increasing the axial dimension of the hub main body 31, thereby reducing the size of the wheel supporting rolling bearing unit.
Weight reduction can be achieved more effectively.

【００３７】尚、上述の様に、外側の転動体列を構成す
る各転動体２１、２１のピッチ円直径を内側の転動体列
を構成する各転動体２１、２１のピッチ円直径よりも小
さくする事に伴い、外側の転動体列部分の基本動定格荷
重が内側の転動体列部分の基本動定格荷重よりも小さく
なる。従って、両列に加わる荷重が同じであれば、外側
の転動体列部分の寿命が内側の転動体列部分の寿命より
も短くなる。これに対して、一般的な自動車では、外側
の転動体列部分に加わる荷重は内側の転動体列部分に加
わる荷重よりも小さい。この為、上記両列部分の寿命を
ほぼ同じにする設計が容易になって、無駄のない設計が
可能になる。尚、図示の例では、転動体２１、２１とし
て玉を使用しているが、重量の嵩む自動車用の転がり軸
受ユニットの場合には、転動体としてテーパころを使用
する場合もある。本発明は、勿論、この様に転動体とし
てテーパころを使用する転がり軸受ユニットと一体の等
速ジョイントにも適用可能である。As described above, the pitch circle diameter of each of the rolling elements 21 and 21 constituting the outer rolling element row is smaller than the pitch circle diameter of each of the rolling elements 21 and 21 forming the inner rolling element row. Accordingly, the basic dynamic load rating of the outer rolling element row portion becomes smaller than the basic dynamic load rating of the inner rolling element row portion. Therefore, if the load applied to both rows is the same, the life of the outer rolling element row is shorter than the life of the inner rolling element row. On the other hand, in a general automobile, the load applied to the outer rolling element row portion is smaller than the load applied to the inner rolling element row portion. For this reason, it is easy to design the two rows so that the lifespans thereof are almost the same, and it is possible to design without waste. Although balls are used as the rolling elements 21 in the illustrated example, tapered rollers may be used as the rolling elements in the case of a heavy-duty rolling bearing unit for an automobile. The present invention is, of course, applicable to a constant velocity joint integrated with a rolling bearing unit using a tapered roller as a rolling element.

【００３８】次に、図７は、本発明の実施の形態の第２
例を示している。本例の場合、内輪２Ｂを構成する総て
の肩部４６ａ、４６ａの軸方向両端部に、段部３０、３
０を形成している。これにより、総ての肩部４６ａ、４
６ａの軸方向に亙る幅寸法Ｗ46a を、保持器９に形成し
た各ポケット１０、１０（図１〜５）のうちの少なくと
も１個のポケット１０の円周方向に亙る長さ寸法Ｌ
10（図１２）よりも短く（Ｗ46a ＜Ｌ10）している。本
例の場合、上記段部３０、３０は、総ての肩部４６ａ、
４６ａの軸方向両端部に形成している為、これら各段部
３０、３０を、旋削加工により形成する事もできる。こ
の様に構成する本例の場合には、上記肩部４６ａ、４６
ａの何れをも上記１個のポケット１０に挿入できる為、
上記保持器９に内径側に上記内輪２Ｂを組み込む作業の
容易化を図れる。FIG. 7 shows a second embodiment of the present invention.
An example is shown. In the case of the present example, the shoulders 46a, 46a constituting the inner ring 2B are provided with step portions 30, 3 at both ends in the axial direction.
0 is formed. Thereby, all the shoulders 46a, 4
The width dimension W 46a extending in the axial direction of 6a is set to the length dimension L extending in the circumferential direction of at least one of the pockets 10, 10 (FIGS. 1 to 5) formed in the retainer 9.
10 (FIG. 12) (W 46a <L 10 ). In the case of this example, the steps 30, 30 are all shoulders 46a,
Since these steps are formed at both ends in the axial direction of 46a, these steps 30 can be formed by turning. In the case of the present example having such a configuration, the shoulders 46a, 46
a can be inserted into the one pocket 10,
The work of assembling the inner ring 2B on the inner diameter side of the retainer 9 can be facilitated.

【００３９】尚、本例の場合、上記総ての肩部４６ａ、
４６ａの軸方向に亙る幅寸法Ｗ46aを小さくした為、上
記内輪２Ｂの外周面に形成した総ての内側係合溝７、７
の長さが短くなる。従って、これら総ての内側係合溝
７、７の長さを短くした分、等速ジョイントの許容ジョ
イント角が小さくなる事も想定される。一方、この等速
ジョイントの許容ジョイント角は、上記内輪２Ｂに結合
する図示しない駆動軸の外周面と外輪４１（図１）の開
口周縁部とが干渉する際のジョイント角αと、各ボール
４（図１）が、上記内側係合溝７、７と外側係合溝８、
８（図１）との少なくとも一方の係合溝から外れる際の
ジョイント角βとの、角度が小さい方のジョイント角に
より決定される。この為、上記ジョイント角βが上記ジ
ョイント角αよりも大きい（β＜α）場合には、上記ジ
ョイント角βが上記ジョイント角αと等しくなるまでこ
のジョイント角βを小さくしても、即ち、上記内側係合
溝７、７と外側係合溝８、８との少なくとも一方の係合
溝の長さを短くしても、上記許容ジョイント角の大きさ
に影響を与えない。従って、本例の構造を、上記ジョイ
ント角βが上記ジョイント角αよりも大きい（β＜α）
等速ジョイントに採用すれば、この等速ジョイントの許
容ジョイント角の大きさに影響を与える事なく、上記保
持器９の内径側に内輪２Ｂを組み込む作業の容易化を図
れる。その他の構成及び作用は、上述した第１例の場合
と同様である。In the case of this embodiment, all the shoulders 46a,
Since the width dimension W 46a of the inner ring 2B in the axial direction is reduced, all the inner engaging grooves 7, 7 formed on the outer peripheral surface of the inner ring 2B are formed.
Becomes shorter. Therefore, it is assumed that the allowable joint angle of the constant velocity joint is reduced by the reduction of the length of all the inner engagement grooves 7. On the other hand, the allowable joint angle of this constant velocity joint is determined by the joint angle α when the outer peripheral surface of the drive shaft (not shown) connected to the inner ring 2B interferes with the peripheral edge of the opening of the outer ring 41 (FIG. 1). (FIG. 1) shows the inner engagement grooves 7, 7 and the outer engagement grooves 8,
8 (FIG. 1) and the joint angle β at the time of disengaging from at least one of the engagement grooves is determined by the smaller joint angle. Therefore, if the joint angle β is larger than the joint angle α (β <α), the joint angle β may be reduced until the joint angle β becomes equal to the joint angle α, Even if the length of at least one of the inner engagement grooves 7, 7 and the outer engagement grooves 8, 8 is reduced, the magnitude of the allowable joint angle is not affected. Therefore, the structure of the present example is modified such that the joint angle β is larger than the joint angle α (β <α).
By adopting the constant velocity joint, the work of assembling the inner ring 2B on the inner diameter side of the retainer 9 can be facilitated without affecting the allowable joint angle of the constant velocity joint. Other configurations and operations are the same as those of the above-described first example.

【００４０】次に、図８は、本発明の実施の形態の第３
例を示している。上述した第１〜２例の場合が、肩部４
６ａの軸方向両端部に段部３０を形成していたのに対
し、本例の場合には、この段部３０を、肩部４６ｂの軸
方向一端部（図８の右端部）にのみ形成する事により、
加工工数の低減を図っている。又、本例の場合、上記段
部３０は、上記肩部４６ｂの軸方向両端部のうち、この
肩部４６ｂの高さ寸法（この肩部４６ｂの基端縁である
内輪係合溝７の底面７ａから、この肩部４６ｂの先端面
である内輪２Ｃの外周面２ａまでの直径方向に亙る寸
法）が大きい側の端部（図８の右端部）に形成してい
る。本例の場合、上記段部３０を上記肩部４６ｂの高さ
寸法が大きい側の端部に形成する事とした理由は、以下
の通りである。FIG. 8 shows a third embodiment of the present invention.
An example is shown. In the first and second examples described above, the shoulder 4
Steps 30 are formed at both ends in the axial direction of 6a, but in the case of this example, the steps 30 are formed only at one axial end (right end in FIG. 8) of the shoulder 46b. By doing
The number of processing steps is reduced. In the case of the present example, the stepped portion 30 has a height dimension of the shoulder portion 46b (of the inner ring engaging groove 7 which is a base end edge of the shoulder portion 46b) among both axial end portions of the shoulder portion 46b. It is formed at the end (the right end in FIG. 8) on the side where the diameter (dimension in the diameter direction) from the bottom surface 7a to the outer peripheral surface 2a of the inner ring 2C, which is the distal end surface of the shoulder 46b, is large. In the case of this example, the reason that the step portion 30 is formed at the end portion on the side where the height dimension of the shoulder portion 46b is large is as follows.

【００４１】即ち、等速ジョイントのジョイント角が最
大となり、この等速ジョイントを構成する各ボール４
が、図８の仮想平面γ上に配置される場合、これら各ボ
ール４は、この仮想平面γ上に配置された状態で、上記
内側係合溝７の最も浅い部分（肩部４６、４６ｂの高さ
寸法が最も小さい部分で、図８の左端部分）と、同じく
最も深い部分（肩部４６、４６ｂの高さ寸法が最も大き
い部分で、図８の右端部分）との間を往復移動しつつ、
上記肩部４６、４６ｂから駆動力の伝達を受ける。一
方、この様な駆動力の伝達時、上記各肩部４６、４６ｂ
の先端部は、上記各ボール４から円周方向に向く反力を
受け、同方向に弾性変形する。又、この様な円周方向に
亙る弾性変形量は、上記各肩部４６、４６ｂの各部分
（高さ寸法の異なる各部分）で等しい。従って、上記駆
動力の伝達時、上記各ボール４から上記各肩部４６、４
６ｂの各部分（高さ寸法の異なる各部分）に加わる反力
は、これら各肩部４６、４６ｂの高さ寸法が最も大きい
部分で最も小さくなる。That is, the joint angle of the constant velocity joint is maximized, and each ball 4 constituting this constant velocity joint is
Are arranged on the imaginary plane γ in FIG. 8, these balls 4 are arranged on the imaginary plane γ, and the balls 4 are arranged on the imaginary plane γ. It reciprocates between the portion having the smallest height dimension (left end portion in FIG. 8) and the deepest portion (the portion having the largest height dimension of the shoulders 46 and 46b and the right end portion in FIG. 8). While
The driving force is transmitted from the shoulders 46 and 46b. On the other hand, when such a driving force is transmitted, each of the shoulders 46, 46b
Receives a reaction force in the circumferential direction from each of the balls 4 and elastically deforms in the same direction. Further, the amount of elastic deformation in the circumferential direction is equal at each portion (each portion having a different height) of each of the shoulders 46 and 46b. Therefore, at the time of transmitting the driving force, each of the balls 4 and the shoulders 46, 4
The reaction force applied to each portion (each portion having a different height) of the portion 6b is smallest at the portion where the height of each of the shoulders 46, 46b is the largest.

【００４２】この理由は、図９に示す様に、同図（ａ）
に示す肩部４６、４６ｂの高さ寸法が大きい部分（高さ
寸法ｈ1 ）の先端部と、同図（ｂ）に示す肩部４６、４
６ｂの高さ寸法が小さい部分（高さ寸法ｈ2 、但しｈ1
＜ｈ2 ）の先端部とに、上記ボール４から同じ大きさの
反力Ｆが加わる場合には、上記高さ寸法が大きい部分に
作用するモーメント荷重（Ｆ・ｈ1 ）の方が、上記高さ
寸法が小さい部分に作用するモーメント荷重（Ｆ・ｈ
2 ）よりも大きく（Ｆ・ｈ1 ＞Ｆ・ｈ2 ）なり、それぞ
れ同図に鎖線で示す様に、上記高さ寸法が大きい部分の
円周方向に亙る弾性変形量δ1 の方が、上記高さ寸法が
小さい部分の円周方向に亙る弾性変形量δ2 よりも大き
く（δ1 ＞δ2 ）なる為である。即ち、上記高さ寸法が
大きい部分と、上記高さ寸法が小さい部分との円周方向
に亙る弾性変形量が等しい場合には、上記高さ寸法が大
きい部分に加わる反力の方が、上記高さ寸法が小さい部
分に加わる反力よりも小さくなる為である。The reason for this is as shown in FIG.
And the distal end portion of the height dimension is larger portion of the shoulder portion 46,46B (height h 1) shown in, shoulder 46,4 shown in FIG. (B)
6b where the height dimension is small (height dimension h 2 , but h 1
When a reaction force F of the same magnitude is applied from the ball 4 to the tip of <h 2 ), the moment load (F · h 1 ) acting on the portion where the height dimension is large is greater than the above-mentioned moment load (F · h 1 ). Moment load (Fh
2) increased (F · h 1> F · h 2) than, as respectively shown by the chain line in the figure, the direction of elastic deformation [delta] 1 over the circumferential direction of a portion the height is large, This is because the elastic deformation amount δ 2 in the circumferential direction of the portion having the small height dimension is larger (δ 1 > δ 2 ). That is, when the elastic deformation amount in the circumferential direction of the portion having the large height dimension is equal to the elastic deformation amount in the circumferential direction of the portion having the small height dimension, the reaction force applied to the portion having the large height dimension is smaller than the above-described reaction force. This is because the reaction force is smaller than the reaction force applied to the portion where the height is small.

【００４３】ところで、上記等速ジョイントの運転時
に、この等速ジョイントのジョイント角が大きくなり、
しかも大きなトルクを伝達する事に伴い、この等速ジョ
イントを構成する各ボール４（図１）が上記肩部４６ｂ
の端部に形成した上記段部３０の端縁に乗り上げた場合
には、前記内輪係合溝７に対する上記各ボール４の接触
楕円が上記段部３０の端縁部分で途切れ、これら各ボー
ル４の転動面に所謂エッジロードが加わる。これら各ボ
ール４の転動面にこの様なエッジロードが加わると、こ
れら各ボール４の転がり疲れ寿命が著しく低下する。但
し、この場合に、上記各ボール４の転動面と上記段部３
０の端縁との接触圧を小さくできれば、上記エッジロー
ドによる転がり疲れ寿命の低下を抑える事ができる。こ
の為、本例の場合には、上記エッジロードによる上記各
ボール４の転がり疲れ寿命の低下を抑えるべく、これら
各ボール４の転動面と上記段部３０の端縁との接触圧が
最も小さくなる部分である、上記肩部４６ｂの高さ寸法
が最大となる側の端縁（図８の右端縁）に、前記段部３
０を形成する事とした。その他の構成及び作用は、前述
した第１例の場合と同様である。During the operation of the constant velocity joint, the joint angle of the constant velocity joint increases.
In addition, with transmission of a large torque, each ball 4 (FIG. 1) constituting this constant velocity joint is attached to the shoulder 46b.
When the ball rides on the edge of the step 30 formed at the end of the ball, the contact ellipse of each ball 4 with the inner ring engaging groove 7 is interrupted at the edge of the step 30 and A so-called edge load is added to the rolling surface of the roller. When such an edge load is applied to the rolling surface of each of the balls 4, the rolling fatigue life of each of the balls 4 is significantly reduced. However, in this case, the rolling surface of each ball 4 and the step 3
If the contact pressure with the zero edge can be reduced, the reduction of the rolling fatigue life due to the edge load can be suppressed. For this reason, in the case of the present example, the contact pressure between the rolling surface of each of the balls 4 and the edge of the step 30 is minimized in order to suppress a decrease in the rolling fatigue life of each of the balls 4 due to the edge load. The step portion 3 is provided at the edge (the right edge in FIG. 8) on the side where the height of the shoulder portion 46b is the largest, which is the portion to be reduced.
0 is to be formed. Other configurations and operations are the same as in the case of the above-described first example.

【００４４】尚、図示は省略するが、本発明を通常の
（単体の）等速ジョイントとして実施する場合も、この
等速ジョイントの外径を小さくしつつ、保持器の耐久性
を十分に向上させて、信頼性の高い製品の実現に寄与で
きる。Although not shown, when the present invention is embodied as a normal (single) constant velocity joint, the durability of the cage is sufficiently improved while reducing the outer diameter of the constant velocity joint. This can contribute to the realization of a highly reliable product.

【００４５】[0045]

【発明の効果】本発明の等速ジョイント及び等速ジョイ
ント付自動車用ハブユニットは、以上に述べた通り構成
され作用するので、回転力伝達用のボールの数を多くす
る（例えば７個以上とする）事により外径を小さくでき
る構造で、しかもこれら各ボールを保持する為の保持器
の耐久性確保を図れる。従って、第四世代のハブユニッ
トと呼ばれる、等速ジョイントを一体的に組み込んだ車
輪支持用転がり軸受ユニットの小型・軽量化を、十分な
耐久性を確保しつつ実現できる。The constant velocity joint and the hub unit for a vehicle with the constant velocity joint according to the present invention are constructed and operated as described above, so that the number of balls for transmitting the rotational force is increased (for example, seven or more). S), the outer diameter can be reduced, and the durability of the cage for holding these balls can be ensured. Therefore, it is possible to reduce the size and weight of the rolling bearing unit for wheel support, which is called a fourth-generation hub unit and integrally incorporates a constant velocity joint, while securing sufficient durability.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の等速ジョイント付自動車用ハブユニッ
トの１例を示す断面図。FIG. 1 is a cross-sectional view showing an example of a vehicle hub unit with a constant velocity joint according to the present invention.

【図２】等速ジョイントの保持器と内輪とを取り出し
て、この保持器の内径側にこの内輪を組み込む作業の初
期段階を示す断面図。FIG. 2 is a sectional view showing an initial stage of an operation of taking out a retainer and an inner ring of the constant velocity joint and assembling the inner ring on an inner diameter side of the retainer.

【図３】同じく保持器の内径側に内輪を組み込む作業の
途中段階を、この保持器の内径側にこの内輪の一部を挿
入した状態で示す断面図。FIG. 3 is a cross-sectional view showing a state in which a part of the inner ring is inserted into the inner diameter side of the retainer during the operation of assembling the inner ring on the inner diameter side of the retainer.

【図４】同じく保持器の内径側に内輪を組み込む作業の
途中段階を、この保持器の内径側にこの内輪を挿入し切
った状態で示す断面図。FIG. 4 is a cross-sectional view showing an intermediate stage of the work of installing the inner ring on the inner diameter side of the retainer in a state where the inner ring is completely inserted into the inner diameter side of the retainer.

【図５】同じく保持器の内径側に内輪を組み込む作業を
完了した状態で示す断面図。FIG. 5 is a cross-sectional view showing a state where the operation of installing the inner ring on the inner diameter side of the retainer is completed.

【図６】ハブ本体の製造工程を示す図。FIG. 6 is a diagram showing a manufacturing process of the hub body.

【図７】本発明の実施の形態の第２例を示す、等速ジョ
イントの内輪の断面図。FIG. 7 is a sectional view of an inner race of a constant velocity joint, showing a second example of the embodiment of the present invention.

【図８】同第３例を示す、等速ジョイントの内輪の断面
図。FIG. 8 is a cross-sectional view of the inner race of the constant velocity joint, showing the third example.

【図９】等速ジョイントの内輪の部分端面図。FIG. 9 is a partial end view of the inner race of the constant velocity joint.

【図１０】従来の等速ジョイントの１例を、ジョイント
角を付与した状態で示す断面図。FIG. 10 is a sectional view showing an example of a conventional constant velocity joint in a state where a joint angle is given.

【図１１】同じくジョイント角を付与しない状態で示
す、図１０のＡ−Ａ断面に相当する図。FIG. 11 is a view corresponding to a cross section taken along the line AA of FIG. 10, which is also shown without a joint angle.

【図１２】保持器の一部を外周側から見た図。FIG. 12 is a view of a part of the retainer as viewed from an outer peripheral side.

【図１３】内側、外側両係合溝の底面の位置関係を示す
模式図。FIG. 13 is a schematic diagram showing the positional relationship between the bottom surfaces of the inner and outer engagement grooves.

【図１４】保持器の内径側に内輪を組み込む作業の途中
段階を示す断面図。FIG. 14 is a cross-sectional view showing an intermediate stage of an operation of installing the inner ring on the inner diameter side of the retainer.

【図１５】等速ジョイントを一体的に組み込んだ車輪支
持用転がり軸受ユニットの従来構造の１例を示す断面
図。FIG. 15 is a cross-sectional view showing an example of a conventional structure of a wheel supporting rolling bearing unit integrally incorporating a constant velocity joint.

【符号の説明】[Explanation of symbols]

１、１ａ、１ｂ 等速ジョイント ２、２Ａ、２Ｂ、２Ｃ 内輪 ２ａ 外周面 ３、３Ａ 外輪 ３ａ 内周面 ４ ボール ５ 軸 ６ 軸 ７ 内側係合溝 ７ａ 底面 ８ 外側係合溝 ８ａ 底面 ９ 保持器 １０ ポケット １１ 外輪 １２ 第一の取付フランジ １３ 外輪軌道 １４ 第一の内輪部材 １５ 第二の内輪部材 １６ ハブ １７ 第二の取付フランジ １８ 第一の内輪軌道 １９ 円筒部 ２０ 第二の内輪軌道 ２１ 転動体 ２２ 係止溝 ２３ 係止溝 ２４ 止め輪 ２５ 段部 ２６ 溶接 ２７ａ、２７ｂ カバー ２８ａ、２８ｂ シールリング ２９ 隔板部 ３０ 段部 ３１ ハブ本体 ３２ 内輪 ３３ ハブ ３４ スタッド ３５ 頭部 ３６ シールリング ３７ 肉盗み部 ３８ 係止凹溝 ３９ 止め輪 ４０ 間座 ４１ 外輪 ４２ ブーツ ４３ 組み合わせシールリング ４４ 空間 ４５ スプライン孔 ４６、４６ａ、４６ｂ 肩部 ４７ 棒状素材 ４８ 前加工素材 ４９ 第一中間素材 ５０ 第二中間素材 ５１ 第三中間素材 DESCRIPTION OF SYMBOLS 1, 1a, 1b Constant velocity joint 2, 2A, 2B, 2C Inner ring 2a Outer peripheral surface 3, 3A Outer ring 3a Inner peripheral surface 4 Ball 5 Shaft 6 Shaft 7 Inner engaging groove 7a Bottom 8 Outer engaging groove 8a Bottom 9 Cage DESCRIPTION OF SYMBOLS 10 Pocket 11 Outer ring 12 First mounting flange 13 Outer ring track 14 First inner ring member 15 Second inner ring member 16 Hub 17 Second mounting flange 18 First inner ring track 19 Cylindrical part 20 Second inner ring track 21 Rolling Moving body 22 Locking groove 23 Locking groove 24 Retaining ring 25 Step 26 Welding 27a, 27b Cover 28a, 28b Seal ring 29 Partition plate 30 Step 31 Hub body 32 Inner ring 33 Hub 34 Stud 35 Head 36 Seal ring 37 Meat Stealing part 38 Locking concave groove 39 Retaining ring 40 Spacer 41 Outer ring 42 Boot 43 Combination seal ring 44 Space 45 Splat Inner holes 46, 46a, 46b Shoulder 47 Rod material 48 Pre-processed material 49 First intermediate material 50 Second intermediate material 51 Third intermediate material

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 内輪と、この内輪の外周面の円周方向に
亙り間欠的に存在する複数個所に、それぞれ円周方向に
対し直角方向に形成された断面円弧形の内側係合溝と、
上記内輪の周囲に設けられた外輪と、この外輪の内周面
で上記各内側係合溝と対向する位置に、円周方向に対し
直角方向に形成された断面円弧形の外側係合溝と、上記
内輪の外周面と上記外輪の内周面との間に挟持され、上
記内側、外側両係合溝に整合する位置にそれぞれ円周方
向に亙り間欠的に複数個のポケットを形成した保持器
と、これら各ポケットの内側に１個ずつ保持された状態
で上記内側、外側両係合溝に沿う転動を自在とされた、
複数個のボールとから成り、これら各ボールを、上記内
輪の中心軸と上記外輪の中心軸との軸交角を二等分し、
これら両中心軸を含む平面に対し直交する二等分面内に
配置した等速ジョイントに於いて、上記内輪の外径側部
分でそれぞれ上記各内側係合溝の間部分に形成された複
数本の肩部のうち、少なくとも１本の肩部の上記内輪の
軸方向に亙る幅寸法を、この内輪の軸方向寸法よりも小
さくする事により、当該肩部の軸方向に亙る幅寸法を、
上記各ポケットのうちの少なくとも１個のポケットの円
周方向に亙る長さ寸法よりも短くした事を特徴とする等
速ジョイント。1. An inner ring, and an inner engaging groove having an arc-shaped cross section formed at a plurality of positions intermittently in the circumferential direction on the outer peripheral surface of the inner ring, each being formed in a direction perpendicular to the circumferential direction. ,
An outer ring provided around the inner ring, and an outer engaging groove having an arc-shaped cross section formed in a direction perpendicular to the circumferential direction at a position facing the inner engaging grooves on the inner peripheral surface of the outer ring. And a plurality of pockets formed between the outer peripheral surface of the inner race and the inner peripheral surface of the outer race, and intermittently formed in the circumferential direction at positions matching the inner and outer engagement grooves. The retainer and the inner and outer engagement grooves are allowed to freely roll while being held one by one inside each of these pockets.
Consisting of a plurality of balls, each of these balls, bisecting the axis intersection angle of the center axis of the inner ring and the center axis of the outer ring,
In a constant velocity joint arranged in a bisecting plane orthogonal to a plane including both central axes, a plurality of joints formed on the outer diameter side portion of the inner ring and between the inner engagement grooves respectively. By making the width of at least one shoulder in the axial direction of the inner ring smaller than that of the inner ring, the width of the shoulder in the axial direction can be reduced.
A constant velocity joint, wherein at least one of the pockets has a length shorter than a circumferential length of the pocket. 【請求項２】 外周面に懸架装置に支持固定する為の第
一の取付フランジを、内周面に複列の外輪軌道を、それ
ぞれ有するハブユニット用の外輪と、中間部外周面に複
列の内輪軌道を、一端部外周面で上記ハブユニット用の
外輪の一端開口部から突出した部分に車輪を支持固定す
る為の第二の取付フランジを、それぞれ有するハブと、
上記各外輪軌道と上記各内輪軌道との間にそれぞれ複数
個ずつ転動自在に設けた転動体と、上記ハブの他端部に
設けた等速ジョイントとを備えた等速ジョイント付自動
車用ハブユニットに於いて、この等速ジョイントが請求
項１に記載した等速ジョイントである事を特徴とする等
速ジョイント付自動車用ハブユニット。2. An outer ring for a hub unit having a first mounting flange for supporting and fixing to a suspension device on an outer peripheral surface, an outer ring for a hub unit having a plurality of rows of outer raceways on an inner peripheral surface, and a plurality of rows on an intermediate portion outer peripheral surface. Hubs each having a second mounting flange for supporting and fixing the wheel to a portion protruding from the one end opening of the outer ring for the hub unit on one end outer peripheral surface,
A vehicle hub with a constant velocity joint, comprising a plurality of rolling elements rotatably provided between the respective outer raceways and the inner raceways, and a constant velocity joint provided at the other end of the hub. 2. A hub unit for a vehicle having a constant velocity joint, wherein the constant velocity joint is the constant velocity joint according to claim 1.
JP10320932A 1998-11-11 1998-11-11 Constant velocity universal joint and automobile hub unit with constant velocity universal joint Pending JP2000145805A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP10320932A JP2000145805A (en) 1998-11-11 1998-11-11 Constant velocity universal joint and automobile hub unit with constant velocity universal joint

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP10320932A JP2000145805A (en) 1998-11-11 1998-11-11 Constant velocity universal joint and automobile hub unit with constant velocity universal joint

Publications (2)

Publication Number Publication Date
JP2000145805A true JP2000145805A (en) 2000-05-26
JP2000145805A5 JP2000145805A5 (en) 2006-01-12

Family

ID=18126901

Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10032853C2 (en) * 2000-07-06 2003-02-20 Gkn Loebro Gmbh Constant velocity joint
US6579384B2 (en) 2000-10-13 2003-06-17 Honda Giken Kogyo Kabushiki Kaisha Ball for constant-velocity joint and method of manufacturing such ball
WO2009054216A1 (en) * 2007-10-24 2009-04-30 Ntn Corporation Constant velocity universal joint
EP2093444A1 (en) * 2006-12-05 2009-08-26 NTN Corporation Joint assembly, and total assembly of bearing device having the joint assembly and adapted for use for drive wheel
US7632190B2 (en) 2004-01-15 2009-12-15 Honda Motor Co., Ltd. Constant velocity joint
WO2010052985A1 (en) * 2008-11-06 2010-05-14 Ntn株式会社 Fixed constant velocity universal joint, method of manufacturing fixed constant velocity universal joint, and bearing device adapted for use in driving wheel and using fixed constant velocity universal joint
WO2012005206A1 (en) * 2010-07-07 2012-01-12 株式会社ジェイテクト Ball type constant velocity joint
JP2015057574A (en) * 2014-12-25 2015-03-26 株式会社ジェイテクト Ball type constant velocity joint

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6893352B2 (en) 2000-07-06 2005-05-17 Gkn Lobro Gmbh Homocinetic joint
DE10032853C2 (en) * 2000-07-06 2003-02-20 Gkn Loebro Gmbh Constant velocity joint
US6579384B2 (en) 2000-10-13 2003-06-17 Honda Giken Kogyo Kabushiki Kaisha Ball for constant-velocity joint and method of manufacturing such ball
US7632190B2 (en) 2004-01-15 2009-12-15 Honda Motor Co., Ltd. Constant velocity joint
EP2093444A4 (en) * 2006-12-05 2011-05-25 Ntn Toyo Bearing Co Ltd Joint assembly, and total assembly of bearing device having the joint assembly and adapted for use for drive wheel
EP2093444A1 (en) * 2006-12-05 2009-08-26 NTN Corporation Joint assembly, and total assembly of bearing device having the joint assembly and adapted for use for drive wheel
WO2009054216A1 (en) * 2007-10-24 2009-04-30 Ntn Corporation Constant velocity universal joint
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WO2010052985A1 (en) * 2008-11-06 2010-05-14 Ntn株式会社 Fixed constant velocity universal joint, method of manufacturing fixed constant velocity universal joint, and bearing device adapted for use in driving wheel and using fixed constant velocity universal joint
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