JPH06193642A - Fitting structure of inner race to shaft portion of constant speed universal joint - Google Patents

Fitting structure of inner race to shaft portion of constant speed universal joint

Info

Publication number
JPH06193642A
JPH06193642A JP4345738A JP34573892A JPH06193642A JP H06193642 A JPH06193642 A JP H06193642A JP 4345738 A JP4345738 A JP 4345738A JP 34573892 A JP34573892 A JP 34573892A JP H06193642 A JPH06193642 A JP H06193642A
Authority
JP
Japan
Prior art keywords
chamfer
inner ring
shaft
shaft portion
fitting structure
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
JP4345738A
Other languages
Japanese (ja)
Other versions
JP3188001B2 (en
Inventor
Hiroaki Hamaguchi
宏晃 浜口
Kazuharu Kato
一治 加藤
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.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co 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 NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Priority to JP34573892A priority Critical patent/JP3188001B2/en
Publication of JPH06193642A publication Critical patent/JPH06193642A/en
Application granted granted Critical
Publication of JP3188001B2 publication Critical patent/JP3188001B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22313—Details of the inner part of the core or means for attachment of the core on the shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/12—Mounting or assembling

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Steering Controls (AREA)

Abstract

PURPOSE:To embody a constant speed universal joint miniaturized and lightened, having high operating angle, and also improved in its assemblage. CONSTITUTION:The inner side chamfer 1dy of the serration 1d of an inner race 1 touches a circular circlip 2c, and an inlet side chamfer 1dz touches a shoulder portion 2e, thereby the inner race 1 and a shaft portion 2 are axially and mutually bound. The chamfer angle thetaz of the inlet side chamfer 1dz is set to 32.5 deg. or less, which is preferably set to 15 deg. or more and 32.5 deg. or less.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、自動車や各種産業機械
に使用される等速自在継手において、その内輪と軸部と
の嵌合構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fitting structure for an inner ring and a shaft of a constant velocity universal joint used in automobiles and various industrial machines.

【０００２】[0002]

【従来の技術】等速自在継手は、内周面に軸方向に延び
た複数の案内溝を形成した外輪と、内周面に軸方向に延
びた複数の案内溝を形成した内輪と、内・外輪の案内溝
が協働して形成するボールトラックに配されたトルク伝
達ボールと、トルク伝達ボールを作動角の角度２等分面
内に保持する保持器とで構成されるものであるが、通
常、外輪に従動軸（又は駆動軸）を接合し、内輪に駆動
軸（又は従動軸）あるいは中間軸といった軸部をセレー
ション又はスプライン嵌合して使用する。そして、駆動
軸と従動軸との間に角度変位が生じると、トルク伝達ボ
ールが内・外輪の案内溝に案内されてボールトラック内
を移動することにより、内輪と外輪とが作動角を取りこ
の角度変位に対応する。公知のように、セレーションと
スプラインとは歯型形状により区別されるもので、スプ
ラインは軸線に平行なキー状の歯を軸部の外周面に等間
隔に形成したもの、セレーションはスプラインの歯を細
かい三角形の山形にしたものである。セレーションは歯
たけが低く歯数が多いので、スプラインよりもさらに大
きなトルクを伝達することができ、スプラインが一般に
大径の軸部に用いられるのに対し、セレーションは小径
の軸部に用いられることが多い。2. Description of the Related Art A constant velocity universal joint includes an outer ring having a plurality of axially extending guide grooves formed on its inner peripheral surface, and an inner ring having a plurality of axially extending guide grooves formed on its inner peripheral surface.・ A torque transmitting ball arranged on a ball track formed by the guide groove of the outer ring in cooperation with each other, and a cage for holding the torque transmitting ball in the angle bisector of the operating angle. Usually, a driven shaft (or a drive shaft) is joined to an outer ring, and a shaft part such as a drive shaft (or a driven shaft) or an intermediate shaft is serrated or spline-fitted to an inner ring for use. Then, when an angular displacement occurs between the drive shaft and the driven shaft, the torque transmitting balls are guided by the guide grooves of the inner and outer rings and move in the ball track, so that the inner and outer rings form an operating angle. Corresponds to angular displacement. As is well known, serrations and splines are distinguished by the tooth shape, splines are key-shaped teeth parallel to the axis formed on the outer peripheral surface of the shaft portion at equal intervals, and serrations are spline teeth. It is a small triangular mountain. Since serrations have a low tooth depth and a large number of teeth, they can transmit even greater torque than splines, and splines are generally used for large diameter shafts, whereas serrations are used for small diameter shafts. There are many.

【０００３】従来より、例えば固定型等速自在継手の内
輪と軸部との嵌合構造として、図５〜図７に示すような
嵌合構造が採用されてきた。Conventionally, for example, a fitting structure as shown in FIGS. 5 to 7 has been adopted as a fitting structure between an inner ring and a shaft portion of a fixed type constant velocity universal joint.

【０００４】図５に示すのはいわゆる２クリップタイプ
の嵌合構造であり、内輪１１と軸部１２とを丸サークリ
ップ１３と角サークリップ１４とによって軸方向の両側
から拘束するものである。内輪１１と軸部１２との間の
トルク伝達は、内輪１１の内周面に形成されたセレーシ
ョン１１ｄと、軸部１２の軸端部外周面に形成されたセ
レーション１２ｄとの噛み合いによってなされる。丸サ
ークリップ１３は軸部１２の軸端部に形成された環状溝
１２ｂに装着され、セレーション１１ｄの両端チャンフ
ァのうち継手内部側Ｙに位置する内部側チャンファ１１
ｄｙに当接している。角サークリップ１４はセレーショ
ン１２ｄの切欠き部に嵌着され、内輪１１の継手入口側
Ｚの端面に当接している。丸サークリップ１３は、一般
に、セレーション１１ｄの内径よりも大径のＣ型リング
であり、これを弾性的に縮径させながらセレーション１
１ｄの内径に組み入れる。そして、この状態で軸部１２
を押してゆくと、丸サークリップ１３が軸部１２と共に
セレーション１１ｄの内径に案内されて継手内部側Ｙに
移動し、内部側チャンファ１１ｄｙに達した時点で復元
力により自動拡径するようになっている。FIG. 5 shows a so-called two-clip type fitting structure in which the inner ring 11 and the shaft portion 12 are constrained from both sides in the axial direction by a round circlip 13 and a square circlip 14. Torque is transmitted between the inner ring 11 and the shaft portion 12 by engagement between the serrations 11d formed on the inner peripheral surface of the inner ring 11 and the serrations 12d formed on the outer peripheral surface of the shaft end portion of the shaft portion 12. The circular circlip 13 is mounted in the annular groove 12b formed in the shaft end of the shaft 12, and the inner chamfer 11 located on the joint inner side Y of the chamfers at both ends of the serration 11d.
It is in contact with dy. The square circlip 14 is fitted into the cutout portion of the serration 12d and is in contact with the end surface of the inner ring 11 on the joint inlet side Z. The circular circlip 13 is generally a C-shaped ring having a diameter larger than the inner diameter of the serration 11d.
Incorporated into the inner diameter of 1d. Then, in this state, the shaft portion 12
When is pushed, the circular circlip 13 is guided by the inner diameter of the serration 11d together with the shaft portion 12 to move to the inside Y of the joint, and when the inner chamfer 11dy is reached, the diameter is automatically expanded by the restoring force. There is.

【０００５】図６に示すのはいわゆる１クリップタイプ
の嵌合構造であり、内輪１１と軸部１２とを１つの丸サ
ークリップ１３で軸方向に拘束するものである。丸サー
クリップ１３は軸部１２の軸端部に形成された環状溝１
２ｂに装着され、内輪１１の内周面に形成された環状溝
１１ｂに係合している。FIG. 6 shows a so-called one-clip type fitting structure in which the inner ring 11 and the shaft portion 12 are axially restrained by a single circular circlip 13. The circular circlip 13 is an annular groove 1 formed at the shaft end of the shaft 12.
2b, and is engaged with an annular groove 11b formed on the inner peripheral surface of the inner ring 11.

【０００６】図７に示すのはいわゆる１クリップ肩止め
タイプの嵌合構造であり、内輪１１と軸部１２とを丸サ
ークリップ１３と軸部１２に形成した肩部１２ｅとによ
って軸方向の両側から拘束するものである。肩部１２ｅ
はセレーション１２ｄよりも軸中央側に設けられ、セレ
ーション１２ｄの軸中央側チャンファ１２ｄｚに間隔を
隔てて対向している。丸サークリップ１３はセレーショ
ン１１ｄの継手内部側Ｙに位置する内部側チャンファ１
１ｄｙに当接し、肩部１２ｅは継手入口側Ｚに位置する
入口側チャンファ１１ｄｚに当接している。FIG. 7 shows a so-called one-clip shoulder stop type fitting structure, in which the inner ring 11 and the shaft portion 12 are formed by the circular circlip 13 and the shoulder portion 12e formed on the shaft portion 12 on both sides in the axial direction. Is to be restrained from. Shoulder 12e
Is provided on the axial center side of the serration 12d and faces the axial center side chamfer 12dz of the serration 12d at a distance. The circular circlip 13 is the inner chamfer 1 located inside the joint inner side Y of the serration 11d.
1 dy, and the shoulder 12e abuts on the inlet side chamfer 11dz located on the joint inlet side Z.

【０００７】[0007]

【発明が解決しようとする課題】近時の傾向として、等
速自在継手の小型・軽量化が重要な課題となっている。
これは、特に、等速自在継手の主たる用途である自動車
の業界において、低燃費化の一貫として車体重量の軽減
に積極的に取組んでいることと対応している。小型・軽
量化の最も有効な手段としては、トルク伝達容量の増大
による１サイズダウンが挙げられる。また、等速自在継
手においては、高作動角、低コストといった特性も要求
される。As a recent tendency, it is important to reduce the size and weight of constant velocity universal joints.
This corresponds to the fact that in the automobile industry, which is the main application of constant velocity universal joints, the weight of the vehicle body is being actively reduced as a part of low fuel consumption. One of the most effective means to reduce the size and weight is to reduce the size by increasing the torque transmission capacity. Further, the constant velocity universal joint is also required to have characteristics such as a high operating angle and low cost.

【０００８】ところで、等速自在継手のトルク伝達容量
は、内輪の強度それも継手入口側部分の強度によって事
実上決まってくる。これは、主として、固定型等速自在
継手などの内輪では案内溝の溝底部分の肉厚が入口側に
おいて最も薄くなっていること、作動角付与時、反作動
角側のトルク伝達ボールが案内溝の入口側へ移動してト
ルクを伝達することに起因する。特に、高作動角になれ
ばなる程、トルク伝達ボールが入口付近に近付いてくる
ので、この部分の強度によって最大作動角も大きく左右
される。By the way, the torque transmission capacity of the constant velocity universal joint is practically determined by the strength of the inner ring and the strength of the joint inlet side portion. This is mainly because the inner ring of a fixed type constant velocity universal joint has the thinnest wall thickness of the guide groove on the inlet side, and when the operating angle is applied, the torque transmission ball on the opposite operating angle side guides. This is because the torque is transmitted by moving to the entrance side of the groove. In particular, the higher the operating angle, the closer the torque transmitting ball comes to the vicinity of the entrance, so the maximum operating angle also largely depends on the strength of this portion.

【０００９】そこで、上述した３つのタイプの嵌合構造
に関し、小型・軽量化ならびに高作動角化の観点から内
輪１１の強度、コスト性の観点から内輪１１と軸部１２
との組付性についてそれぞれ検討し、簡単に整理すると
以下のようになる（詳細は後述）。Therefore, regarding the above-mentioned three types of fitting structures, the inner ring 11 and the shaft portion 12 are strong from the viewpoint of size and weight reduction and a high operating angle, and the cost of the inner ring 11.
The following is a brief summary of the assemblability with and each of them (the details will be given later).

【００１０】［図５に示す２クリップタイプ］[2 clip type shown in FIG. 5]

【００１１】（１）内輪１１の強度に関して、構造上、
特別な配慮は払われていない。(1) With respect to the strength of the inner ring 11, structurally,
No special consideration has been paid.

【００１２】（２）セレーション１１ｄの入口側チャン
ファ１１ｄｚのチャンファ角θｚが４５度であり、内輪
１１と軸部１２との組付を自動化することが不可であ
る。(2) Since the chamfer angle θz of the chamfer 11dz on the inlet side of the serration 11d is 45 degrees, the assembly of the inner ring 11 and the shaft portion 12 cannot be automated.

【００１３】［図６に示す１クリップタイプ］[1 clip type shown in FIG. 6]

【００１４】（１）内輪１１の強度は、上記２クリップ
タイプと同等以上である。(1) The strength of the inner ring 11 is equal to or higher than that of the two-clip type.

【００１５】（２）セレーション１１ｄの入口側チャン
ファ１１ｄｚのチャンファ角θｚが２５度であり、内輪
１１と軸部１２との組付を自動化することが可能であ
る。(2) Since the chamfer angle θz of the chamfer 11dz on the inlet side of the serration 11d is 25 degrees, the assembling of the inner ring 11 and the shaft portion 12 can be automated.

【００１６】［図７に示す１クリップ肩止めタイプ］[One-clip shoulder type shown in FIG. 7]

【００１７】（１）内輪１１の強度は、３つのタイプの
中で一番大きい。(1) The strength of the inner ring 11 is the largest of the three types.

【００１８】（２）セレーション１１ｄの入口側チャン
ファ１１ｄｚのチャンファ角θｚが４５度であり、内輪
１１と軸部１２との組付を自動化することが不可であ
る。(2) Since the chamfer angle θz of the entrance side chamfer 11dz of the serration 11d is 45 degrees, it is impossible to automate the assembling of the inner ring 11 and the shaft portion 12.

【００１９】まず、内輪１１の強度に関して比較してみ
ると、内輪１１の強度は１クリップ肩止めタイプにおい
て最も大となっている。これは次の理由による。すなわ
ち、内輪１１と軸部１２との間でトルクが伝達される
時、セレーション１１ｄとセレーション１２ｄとの嵌合
開始位置に最大着力が発生するが、２クリップタイプお
よび１クリップタイプにおいては、この嵌合開始位置が
セレーション１１ｄの入口側チャンファ１１ｄｚである
のに対し、１クリップ肩止めタイプにおいては、入口側
チャンファ１１ｄｚよりも継手内部側Ｙに位置するセレ
ーション１２ｄの軸中央側チャンファ１２ｄｚが嵌合開
始位置になる。つまり、１クリップ肩止めタイプは、最
大着力点が上記２つのタイプよりも継手内部側Ｙに入り
込んだ構造をしており、最大着力を内輪１１のより厚肉
の部分で負荷することができるので、強度が他のタイプ
よりも大となるのである。First, comparing the strength of the inner ring 11, the strength of the inner ring 11 is the largest in the one-clip shoulder type. This is for the following reason. That is, when torque is transmitted between the inner ring 11 and the shaft portion 12, the maximum force is generated at the fitting start position between the serrations 11d and 12d. While the joining start position is the entrance side chamfer 11dz of the serration 11d, in the one-clip shoulder type, the shaft center side chamfer 12dz of the serration 12d located on the joint inner side Y than the entrance side chamfer 11dz starts fitting. Be in position. In other words, the one-clip shoulder type has a structure in which the maximum force point enters the joint inner side Y more than the above two types, and the maximum force can be applied to the thicker portion of the inner ring 11. , The strength is greater than other types.

【００２０】つぎに、組付性に関して比較してみると、
上記３つのタイプのうち１クリップタイプのみが自動組
付可能になっている。これは、上記１クリップタイプに
おいて、セレーション１１ｄの入口側チャンファ１１ｄ
ｚのチャンファ角θｚが２５度と比較的小さく設定され
ており、軸部１２を組入れる際、丸サークリップ１３が
入口側チャンファ１１ｄｚによって案内され、必要な寸
法（セレーション１１ｄの内径寸法）まで自動縮径する
からである。ところが、他の２つタイプにおいては、入
口側チャンファ１１ｄｚのチャンファ角θｚが４５度と
比較的大きく設定されているため、軸部１２を組入れる
際、入口側チャンファ１１ｄｚによる案内が不十分とな
り、丸サークリップ１３が自動縮径しない。そのため、
他の２つタイプでは、自動組付が不可である。Next, comparing the assembling ability,
Of the above three types, only one clip type can be automatically assembled. This is the chamfer 11d on the entrance side of the serration 11d in the one clip type.
The chamfer angle θz of z is set to a relatively small value of 25 degrees, and when the shaft portion 12 is assembled, the circular circlip 13 is guided by the chamfer 11dz on the inlet side, and is automatically reduced to the required dimension (the inner diameter dimension of the serration 11d). This is because the diameter. However, in the other two types, since the chamfer angle θz of the entrance side chamfer 11dz is set to be relatively large at 45 degrees, the guide by the entrance side chamfer 11dz becomes insufficient when the shaft part 12 is assembled, and the Circlip 13 does not automatically reduce its diameter. for that reason,
With the other two types, automatic assembly is not possible.

【００２１】以上のように、従来の嵌合構造には長所、
短所が混在しており、改良すべき余地が多い。そこで、
本発明の目的は、従来構成における問題点を克服し、等
速自在継手の小型・軽量化並びに高作動角化を達成する
と同時に、組付性の向上を図ることにある。As described above, the advantages of the conventional fitting structure are as follows.
There are many disadvantages and there is much room for improvement. Therefore,
An object of the present invention is to overcome the problems in the conventional structure, to achieve the downsizing and weight reduction of the constant velocity universal joint, and to increase the working angle, and at the same time to improve the assembling property.

【００２２】[0022]

【課題を解決するための手段】請求項１の発明は、外周
面に軸方向に延びた複数の案内溝を形成し、内周面にセ
レーション又はスプライン状の歯型を形成した等速自在
継手の内輪と、軸端部外周面に内輪の歯型と嵌合するセ
レーション又はスプライン状の歯型を形成した軸部との
嵌合構造において、内輪の歯型の両端チャンファのうち
継手内部側に位置する内部側チャンファを軸部の軸端部
に装着したサークリップに当接させると共に、継手入口
側に位置する入口側チャンファを軸部の歯型よりも軸中
央側に設けた肩部に当接させたものであって、入口側チ
ャンファのチャンファ角を３２．５度以下にしたもので
ある。According to a first aspect of the present invention, a constant velocity universal joint is provided in which a plurality of guide grooves extending in the axial direction are formed on the outer peripheral surface and serration or spline tooth patterns are formed on the inner peripheral surface. In the fitting structure of the inner ring and the shaft part where the serration or spline tooth profile that fits the tooth profile of the inner ring is formed on the outer peripheral surface of the shaft end, inside the joint of the chamfers on both ends of the tooth profile of the inner ring Abut the inner chamfer located on the circlip attached to the shaft end of the shaft, and place the inlet chamfer located on the inlet side of the joint on the shoulder provided on the shaft center side rather than the tooth profile of the shaft. The chamfer angle of the inlet side chamfer is 32.5 degrees or less.

【００２３】請求項２の発明は、請求項１の構成におい
て、入口側チャンファのチャンファ角を１５度以上３
２．５度以下にしたものである。According to the invention of claim 2, in the structure of claim 1, the chamfer angle of the chamfer on the inlet side is 15 degrees or more and 3 or more.
It is set to 2.5 degrees or less.

【００２４】ここで、チャンファ角とは、チャンファの
母線が軸線となす角度をいう。Here, the chamfer angle means an angle formed by the chamfer generatrix and the axis.

【００２５】[0025]

【作用】本発明の嵌合構造はいわゆる１クリップ肩止め
タイプであり、軸部の軸端部に装着したサークリップと
軸中央側に設けた肩部とによって、内輪と軸部とを軸方
向の両側から相互に拘束するものである。内輪の歯型の
入口側チャンファが当接する肩部は、軸部の歯型よりも
軸中央側に設けられており、両歯型の嵌合開始位置（最
大着力点）は入口側チャンファよりも継手内部側に入り
込んでいる。これにより、内輪の強度向上が図られる。The fitting structure of the present invention is a so-called one-clip shoulder stopper type, and the inner ring and the shaft portion are axially moved by the circlip mounted on the shaft end portion of the shaft portion and the shoulder portion provided on the shaft center side. Both sides are bound by each other. The shoulder that the chamfer on the inlet side of the tooth profile of the inner ring contacts is provided closer to the center of the shaft than the tooth profile on the shaft, and the fitting start position (maximum force application point) of both tooth models is greater than that on the inlet chamfer. It has entered the inside of the joint. This improves the strength of the inner ring.

【００２６】入口側チャンファのチャンファ角を３２．
５度以下にしたのは、主に、組付性を考慮したものであ
る。内輪と軸部との自動組付が可能であるか否かは、入
口側チャンファのチャンファ角の大小によって決まって
くる。このチャンファ角が大きすぎると、軸部を内輪の
内周面に組入れる際、サークリップが自動縮径しないた
め、自動組付が不可になる。本出願人による多くの実験
の結果、自動組付が可能なチャンファ角の限界値が３
２．５度であることが確認されている。また、後述する
ように、このチャンファ角を小さくすることは、内輪の
強度向上にもつながる。The chamfer angle of the chamfer on the inlet side is 32.
The reason why the angle is set to 5 degrees or less is mainly to consider the assembling property. Whether automatic assembly of the inner ring and the shaft is possible depends on the size of the chamfer angle of the chamfer on the entrance side. If this chamfer angle is too large, the circlip does not automatically reduce its diameter when the shaft portion is mounted on the inner peripheral surface of the inner ring, which makes automatic assembly impossible. As a result of many experiments by the applicant, the limit value of the chamfer angle at which automatic assembly is possible is 3
It has been confirmed to be 2.5 degrees. Further, as will be described later, reducing the chamfer angle also improves the strength of the inner ring.

【００２７】入口側チャンファのチャンファ角を１５度
以上としたのは、内輪の歯型の寸法精度を考慮したもの
である。すなわち、入口側チャンファのチャンファ角を
あまり小さくしすぎると、歯型の全幅（有効長）の精度
確保が加工上困難になるためである。The chamfer angle of the chamfer on the inlet side is set to 15 degrees or more in consideration of the dimensional accuracy of the tooth profile of the inner ring. That is, if the chamfer angle of the inlet chamfer is too small, it becomes difficult to secure the accuracy of the entire width (effective length) of the tooth mold in terms of processing.

【００２８】[0028]

【実施例】以下、本発明の実施例について説明する。EXAMPLES Examples of the present invention will be described below.

【００２９】図１ａは、固定型等速自在継手の内輪１
と、内輪１に嵌合される軸部２とを示している。同図で
左側が継手内部側Ｙ、右側が継手入口側Ｚになる。FIG. 1a shows an inner ring 1 of a fixed type constant velocity universal joint.
And a shaft portion 2 fitted to the inner ring 1. In the figure, the left side is the joint inside side Y and the right side is the joint inlet side Z.

【００３０】内輪１の外周面１ａには軸方向に延びた複
数の案内溝１ｂが形成され、内周面１ｃにはセレーショ
ン１ｄが形成されている。セレーション１ｄの両端には
チャンファが施され、同図で左側が継手内部側Ｙに位置
する内部側チャンファ１ｄｙ、右側が継手入口側Ｚに位
置する入口側チャンファ１ｄｚである。入口側チャンフ
ァ１ｄｚのチャンファ角θｚは３２．５度以下、望まし
くは、１５度以上３２．５度以下に設定する。内部側チ
ャンファ１ｄｙのチャンファ角θｙは特に問わないが、
例えば４５度に設定する。尚、本明細書において、チャ
ンファ角とは、チャンファの母線が軸線Ｘとなす角度を
言う。A plurality of guide grooves 1b extending in the axial direction are formed on the outer peripheral surface 1a of the inner ring 1, and serrations 1d are formed on the inner peripheral surface 1c. A chamfer is applied to both ends of the serration 1d. In the figure, the left side is the inner chamfer 1dy located on the joint inner side Y, and the right side is the inlet side chamfer 1dz located on the joint inlet side Z. The chamfer angle θz of the entrance side chamfer 1dz is set to 32.5 degrees or less, preferably 15 degrees or more and 32.5 degrees or less. The chamfer angle θy of the inner chamfer 1dy is not particularly limited,
For example, it is set to 45 degrees. In the present specification, the chamfer angle means an angle formed by the chamfer generatrix with the axis X.

【００３１】軸部２の軸端部外周面２ａには、内輪１の
セレーション１ｄと嵌合するセレーション２ｄが形成さ
れている。また、軸部２の軸端部外周面２ａには環状溝
２ｂが形成され、環状溝２ｂに丸サークリップ２ｃが装
着されている。丸サークリップ２ｃは例えばＣ型リング
状のもので、その自然状態における外径は内輪１のセレ
ーション１ｄの内径よりも大きく、内径は環状溝２の外
径よりも大きい。さらに、軸部２のセレーション２ｄよ
りも軸中央側には肩部２ｅが形成され、セレーション２
ｄの軸中央側チャンファ２ｄｚに間隔を隔てて対向して
いる。肩部２ｅの母線が軸線Ｘとなす角θ’ｚは、入口
側チャンファ１ｄｚのチャンファ角θｚと同じである。A serration 2d that fits with the serration 1d of the inner ring 1 is formed on the outer peripheral surface 2a of the shaft end portion of the shaft portion 2. An annular groove 2b is formed on the outer peripheral surface 2a of the shaft end portion of the shaft portion 2, and a circular circlip 2c is attached to the annular groove 2b. The circular circlip 2c is, for example, a C-shaped ring, and the outer diameter in its natural state is larger than the inner diameter of the serration 1d of the inner ring 1, and the inner diameter is larger than the outer diameter of the annular groove 2. Further, a shoulder 2e is formed on the shaft center side of the shaft 2 with respect to the serration 2d.
The chamfer 2dz on the axial center of d is opposed to the chamfer 2dz at a distance. The angle θ′z formed by the generatrix of the shoulder portion 2e and the axis X is the same as the chamfer angle θz of the entrance chamfer 1dz.

【００３２】図１ｂは、軸部２を軸端側から内輪１の内
周面１ｃに組入れ、セレーション１ｄとセレーション２
ｄとを嵌合させた状態を示す。セレーション１ｄの内部
側チャンファ１ｄｙが丸サークリップ２ｃに当接し、さ
らに、入口側チャンファ１ｄｚが肩部２ｅに当接するこ
とにより、内輪１と軸部２とが軸方向に相互に拘束し合
っている。In FIG. 1b, the shaft portion 2 is incorporated into the inner peripheral surface 1c of the inner ring 1 from the shaft end side, and the serrations 1d and 2
The state which fitted with d is shown. The inner chamfer 1dy of the serration 1d comes into contact with the round circlip 2c, and the inlet chamfer 1dz comes into contact with the shoulder portion 2e, whereby the inner ring 1 and the shaft portion 2 are restrained from each other in the axial direction. .

【００３３】図２に拡大して示すように、軸部２を組入
れる際、丸サークリップ２ｃが入口側チャンファ１ｄｚ
によって案内されながら徐々に自動縮径し、セレーショ
ン１ｄの内径に嵌まり込む。そして、その状態で軸部２
を継手内部側Ｙに押してゆくと、丸サークリップ２ｃが
セレーション１ｄの内径に案内されて軸部２と共に継手
内部側Ｙに移動し、内部側チャンファ１ｄｙに達した時
点で復元力により自動拡径する。このように、この実施
例の嵌合構造では、丸サークリップ２ｃを特別な治具を
用いて人為的に縮径させる必要がなく、軸部２を内輪１
の内周面に挿通してゆくだけで自動的に組付を完了する
ことができる。尚、自動組付を可能とするためには、チ
ャンファ角θｚを３２．５度以下にすることが必要であ
り、チャンファ角θｚを３２．５度よりも大きくする
と、丸サークリップ２ｃが自動縮径せず、自動組付が不
可となる。しかしながら、チャンファ角θｚをがあまり
小さくしすぎると、セレーション１１の全幅Ａ（有効
長：図１ａ参照）の精度を確保することが困難になるの
で、できれば１５度以上とするのが良い。As shown in the enlarged view of FIG. 2, when the shaft portion 2 is assembled, the circular circlip 2c is moved into the chamfer 1dz on the inlet side.
The diameter is gradually reduced while being guided by and is fitted into the inner diameter of the serration 1d. Then, in that state, the shaft portion 2
Is pushed to the inside Y of the joint, the circular circlip 2c is guided by the inner diameter of the serration 1d and moves to the inside Y of the joint together with the shaft 2, and when it reaches the inner chamfer 1dy, the diameter is automatically expanded by the restoring force. To do. As described above, in the fitting structure of this embodiment, it is not necessary to artificially reduce the diameter of the circular circlip 2c by using a special jig, and the shaft portion 2 is fixed to the inner ring 1
The assembly can be completed automatically simply by inserting it into the inner peripheral surface of the. In order to enable automatic assembly, the chamfer angle θz needs to be 32.5 degrees or less. When the chamfer angle θz is larger than 32.5 degrees, the circular circlip 2c is automatically contracted. Without diameter, automatic assembly becomes impossible. However, if the chamfer angle θz is too small, it becomes difficult to secure the accuracy of the entire width A (effective length: see FIG. 1a) of the serration 11, so it is preferable to set it to 15 degrees or more.

【００３４】また、図３に拡大して示すように、セレー
ション２ｄの軸中央側チャンファ２ｄｚは、セレーショ
ン１ｄの入口側チャンファ１ｄｚよりも継手内部側Ｙに
位置しており、セレーション１ｄとセレーション２ｄと
の嵌合開始位置（最大着力点）Ｐ１は、点Ｐ２（図５お
よび図６に示す嵌合構造においては、入口側チャンファ
が最大着力点となる）に対して継手内部側Ｙに寸法Ｌ１
だけ入り込んでいる。最大着力を内輪１のより厚肉の部
分（継手内部側Ｙの方が厚肉である）で負荷することが
できるので、図５および図６に示す嵌合構造に比べ、内
輪１の強度が向上する。尚、寸法Ｌ１は、セレーション
１ｄの全幅Ａに対して約１０〜２０％程度とするのが効
果的である。As shown in an enlarged manner in FIG. 3, the chamfer 2dz on the axial center of the serration 2d is located closer to the inside Y of the joint than the chamfer 1dz on the inlet side of the serration 1d. The fitting start position (maximum force application point) P1 of the above is a dimension L1 on the joint inner side Y with respect to the point P2 (in the fitting structure shown in FIGS. 5 and 6, the inlet side chamfer is the maximum force application point).
It's just entering. Since the maximum force can be applied to the thicker portion of the inner ring 1 (the inner side Y of the joint is thicker), the strength of the inner ring 1 is stronger than that of the fitting structure shown in FIGS. 5 and 6. improves. It is effective that the dimension L1 is about 10 to 20% with respect to the entire width A of the serration 1d.

【００３５】図４は、図１に示す本実施例の嵌合構造
（チャンファ角θｚ：２５度、３２．５度の２種類）、
図５および図７に示す従来の嵌合構造（チャンファ角θ
ｚ：４５度）のそれぞれについて、内輪の片振り捩り疲
労強度を試験した結果を示す。同図から明らかなよう
に、本実施例の嵌合構造において、内輪１の捩り強度は
従来の嵌合構造よりも大幅に向上している。これは、セ
レーション１ｄとセレーション２ｄとの嵌合開始位置
（最大着力点）Ｐ１が、継手内部側Ｙに入り込んでいる
ためである。ただ、本実施例の嵌合構造においても、チ
ャンファ角θｚが２５．０度の場合と３２．５度の場合
とでは、２５．０度の場合の方が内輪１の捩り強度が大
となっている。このように、チャンファ角θｚが小さく
なると、内輪１の捩り強度が大となる傾向にある。した
がって、入口側チャンファ１ｄｚのチャンファ角θｚは
組付性のみならず内輪１の捩り強度にも直接関係してお
り、これをどの程度の値に設定するかは極めて重要であ
る。FIG. 4 shows the fitting structure of the present embodiment shown in FIG. 1 (two types of chamfer angle θz: 25 degrees and 32.5 degrees).
The conventional fitting structure shown in FIGS. 5 and 7 (chamfer angle θ
(z: 45 degrees) shows the results of testing the one-sided torsional fatigue strength of the inner ring. As is clear from the figure, in the fitting structure of this embodiment, the torsional strength of the inner ring 1 is significantly improved as compared with the conventional fitting structure. This is because the fitting start position (maximum force application point) P1 between the serration 1d and the serration 2d has entered the joint inner side Y. However, also in the fitting structure of the present embodiment, when the chamfer angle θz is 25.0 degrees and when it is 32.5 degrees, the torsional strength of the inner ring 1 becomes larger when the chamfer angle θz is 25.0 degrees. ing. As described above, when the chamfer angle θz is small, the torsional strength of the inner ring 1 tends to be large. Therefore, the chamfer angle θz of the inlet side chamfer 1dz is directly related not only to the assembling property but also to the torsional strength of the inner ring 1, and it is extremely important to set the value of this.

【００３６】尚、上記実施例はセレーション嵌合に関す
るものであるが、本発明はスプライン嵌合の場合にも同
様に適用することができる。また、等速自在継手の形式
は、固定型に限らず摺動型にも適用することができる。
さらには、等速自在継手の内輪と軸部との嵌合構造に限
らず、セレーション又はスプライン嵌合構造一般に適用
が可能である。Although the above embodiment relates to the serration fitting, the present invention can be similarly applied to the spline fitting. Further, the type of the constant velocity universal joint is not limited to the fixed type, but can be applied to the sliding type.
Further, the invention is not limited to the fitting structure between the inner ring of the constant velocity universal joint and the shaft portion, but can be applied to general serration or spline fitting structure.

【００３７】[0037]

【発明の効果】以上説明したように、本発明の嵌合構造
によれば、内輪の歯型と軸部の歯型との嵌合開始位置
（最大着力点）が内輪歯型の入口側チャンファよりも継
手内部側に位置し、最大着力を内輪のより厚肉の部分で
負荷するので、内輪の強度が向上し、これにより、等速
自在継手におけるトルク伝達容量の増大及びこれに伴う
小型・軽量化、さらには、高作動角化を達成することが
できる。同時に、内輪歯型の入口側チャンファのチャン
ファ角を３２．５度以下としたので、内輪と軸部との自
動組付を可能にすることができ、コスト低減を図ること
ができる。As described above, according to the fitting structure of the present invention, the fitting start position (maximum force applied point) between the inner ring tooth profile and the shaft tooth profile is the inlet side chamfer of the inner ring tooth profile. Since the inner ring is located on the inner side of the joint, and the maximum force is applied to the thicker portion of the inner ring, the strength of the inner ring is improved, which increases the torque transmission capacity of the constant velocity universal joint and the resulting small size. It is possible to achieve a reduction in weight and a high operating angle. At the same time, since the chamfer angle of the chamfer on the inlet side of the inner ring tooth type is set to 32.5 degrees or less, it is possible to automatically assemble the inner ring and the shaft portion, and the cost can be reduced.

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

【図１】本考案の実施例の嵌合構造に係わる内輪及び軸
部を示す断面図（図ａ）、嵌合構造を示す断面図（図
ｂ）である。FIG. 1 is a cross-sectional view (FIG. A) showing an inner ring and a shaft portion related to a fitting structure of an embodiment of the present invention, and a cross-sectional view (FIG. B) showing the fitting structure.

【図２】入口側チャンファ周辺の拡大断面図である。FIG. 2 is an enlarged cross-sectional view around an entrance-side chamfer.

【図３】入口側チャンファ周辺の拡大断面図である。FIG. 3 is an enlarged cross-sectional view around the entrance-side chamfer.

【図４】内輪の片振り捩り疲労強度試験の結果を示す図
である。FIG. 4 is a diagram showing the results of a one-sided torsional fatigue strength test of an inner ring.

【図５】従来の嵌合構造に係わる内輪を示す断面図（図
ａ）、嵌合構造を示す断面図（図ｂ）である。FIG. 5 is a cross-sectional view (FIG. A) showing an inner ring relating to a conventional fitting structure, and a cross-sectional view (FIG. B) showing the fitting structure.

【図６】従来の嵌合構造に係わる内輪を示す断面図（図
ａ）、嵌合構造を示す断面図（図ｂ）である。FIG. 6 is a cross-sectional view (FIG. A) showing an inner ring relating to a conventional fitting structure, and a cross-sectional view (FIG. B) showing the fitting structure.

【図７】従来の嵌合構造に係わる内輪を示す断面図（図
ａ）、嵌合構造を示す断面図（図ｂ）である。FIG. 7 is a cross-sectional view (FIG. A) showing an inner ring relating to a conventional fitting structure and a cross-sectional view (FIG. B) showing the fitting structure.

【符号の説明】[Explanation of symbols]

１ 内輪 １ａ 外周面 １ｂ 案内溝 １ｃ 内周面 １ｄ セレーション １ｄｙ 内部側チャンファ １ｄｚ 入口側チャンファ θｚ チャンファ角 ２ 軸部 ２ａ 軸端部外周面 ２ｃ 丸サークリップ ２ｄ セレーション ２ｅ 肩部 1 inner ring 1a outer peripheral surface 1b guide groove 1c inner peripheral surface 1d serration 1dy inner chamfer 1dz inlet chamfer θz chamfer angle 2 shaft portion 2a shaft end outer peripheral surface 2c round circlip 2d serration 2e shoulder portion

Claims (2)

【特許請求の範囲】[Claims] 【請求項１】 外周面に軸方向に延びた複数の案内溝を
形成し、内周面にセレーション又はスプライン状の歯型
を形成した等速自在継手の内輪と、軸端部外周面に前記
内輪の歯型と嵌合するセレーション又はスプライン状の
歯型を形成した軸部との嵌合構造において、前記内輪の
歯型の両端チャンファのうち継手内部側に位置する内部
側チャンファを前記軸部の軸端部に装着したサークリッ
プに当接させると共に、継手入口側に位置する入口側チ
ャンファを前記軸部の歯型よりも軸中央側に設けた肩部
に当接させたものであって、前記入口側チャンファのチ
ャンファ角を３２．５度以下にしたことを特徴とする等
速自在継手の内輪と軸部との嵌合構造。1. An inner ring of a constant velocity universal joint, wherein a plurality of guide grooves extending in the axial direction are formed on the outer peripheral surface, and serrations or spline-shaped tooth patterns are formed on the inner peripheral surface, and the outer peripheral surface of the shaft end portion is provided with the above-mentioned inner ring. In a fitting structure with a shaft portion formed with serrations or splined tooth molds that fit with a tooth mold of an inner ring, an inner chamfer located on the inner side of the joint among the chamfers at both ends of the tooth mold of the inner ring is the shaft part. The circlip mounted on the shaft end of the shaft, and the inlet side chamfer located on the joint inlet side is contacted with the shoulder provided on the shaft center side with respect to the tooth profile of the shaft. The fitting structure between the inner ring and the shaft portion of the constant velocity universal joint, wherein the chamfer angle of the inlet chamfer is 32.5 degrees or less. 【請求項２】 前記入口側チャンファのチャンファ角を
１５度以上３２．５度以下にしたことを特徴とする等速
自在継手の内輪と軸部との嵌合構造。2. A fitting structure between an inner ring and a shaft portion of a constant velocity universal joint, wherein a chamfer angle of the chamfer on the inlet side is 15 degrees or more and 32.5 degrees or less.
JP34573892A 1992-12-25 1992-12-25 Fitting structure between inner ring and shaft of constant velocity universal joint Expired - Lifetime JP3188001B2 (en)

Priority Applications (1)

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EP1703157A2 (en) * 2005-03-18 2006-09-20 Ntn Corporation Structure for preventing shaft of constant velocity joint from coming off
JP2006275239A (en) * 2005-03-30 2006-10-12 Ntn Corp Shaft fitting structure of constant velocity joint
WO2007074630A1 (en) * 2005-12-26 2007-07-05 Ntn Corporation Constant velocity universal joint and inner member of the same
JP2008527250A (en) * 2005-01-03 2008-07-24 ジーケイエヌ ドライブライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Shaft hub connection with locking system
JP2009228735A (en) * 2008-03-21 2009-10-08 Ntn Corp Shaft coupling
US7926611B2 (en) 2007-03-20 2011-04-19 Honda Motor Co., Ltd. Shaft drive device
US11125277B2 (en) 2017-07-19 2021-09-21 Zhejiang CFMOTO Power Co., Ltd. Type of constant velocity universal joint with the spline slip structure
US11242896B2 (en) * 2017-07-19 2022-02-08 Zhejiang Cfmoto Power Co. Ltd. Spline slip constant velocity joint

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JP2009180315A (en) * 2008-01-31 2009-08-13 Ntn Corp Power transmitting shaft and shaft assembly
JP2009185878A (en) * 2008-02-05 2009-08-20 Ntn Corp Constant speed universal joint and shaft assembly
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Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008527250A (en) * 2005-01-03 2008-07-24 ジーケイエヌ ドライブライン インターナショナル ゲゼルシャフト ミット ベシュレンクテル ハフツング Shaft hub connection with locking system
EP1703157A2 (en) * 2005-03-18 2006-09-20 Ntn Corporation Structure for preventing shaft of constant velocity joint from coming off
JP2006258254A (en) * 2005-03-18 2006-09-28 Ntn Corp Structure preventing shaft of constant velocity joint from coming off
EP1703157A3 (en) * 2005-03-18 2008-12-31 Ntn Corporation Structure for preventing shaft of constant velocity joint from coming off
JP2006275239A (en) * 2005-03-30 2006-10-12 Ntn Corp Shaft fitting structure of constant velocity joint
WO2007074630A1 (en) * 2005-12-26 2007-07-05 Ntn Corporation Constant velocity universal joint and inner member of the same
JP2007170628A (en) * 2005-12-26 2007-07-05 Ntn Corp Constant velocity universal joint and its inward member
US8066575B2 (en) 2005-12-26 2011-11-29 Ntn Corporation Constant velocity universal joint and inner member of the same
US7926611B2 (en) 2007-03-20 2011-04-19 Honda Motor Co., Ltd. Shaft drive device
JP2009228735A (en) * 2008-03-21 2009-10-08 Ntn Corp Shaft coupling
US11125277B2 (en) 2017-07-19 2021-09-21 Zhejiang CFMOTO Power Co., Ltd. Type of constant velocity universal joint with the spline slip structure
US11242896B2 (en) * 2017-07-19 2022-02-08 Zhejiang Cfmoto Power Co. Ltd. Spline slip constant velocity joint

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