JPH09177809A - Constant velocity universal joint - Google Patents
Constant velocity universal jointInfo
- Publication number
- JPH09177809A JPH09177809A JP33937895A JP33937895A JPH09177809A JP H09177809 A JPH09177809 A JP H09177809A JP 33937895 A JP33937895 A JP 33937895A JP 33937895 A JP33937895 A JP 33937895A JP H09177809 A JPH09177809 A JP H09177809A
- Authority
- JP
- Japan
- Prior art keywords
- wall surface
- inner ring
- ring
- outer ring
- shaft portion
- 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.)
- Withdrawn
Links
Landscapes
- Pivots And Pivotal Connections (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、自動車や各種産業
機械における動力伝達に用いられる等速自在継手に関
し、特に、自動車等のステアリング装置に適したものに
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a constant velocity universal joint used for power transmission in automobiles and various industrial machines, and more particularly to a constant velocity universal joint suitable for steering devices for automobiles and the like.
【０００２】[0002]
【従来の技術】一般に、自動車のステアリング装置等に
使用される等速自在継手には、高作動角を取れること、
回転バックラッシュ（円周方向のガタツキ）が小さいこ
と、小型・軽量であること、さらには、低コストである
ことなどが要求される。2. Description of the Related Art Generally, a constant velocity universal joint used in an automobile steering device or the like has a high working angle,
It is required that the rotary backlash (circumferential rattling) is small, that it is small and lightweight, and that it is low in cost.
【０００３】本出願人は、上記のような特性を備え、特
に、ステアリング装置に適した等速自在継手として図１
０〜図１２に示す等速自在継手（特願平６−８６０７５
号）、図１３に示す等速自在継手｛特願平３−３４４２
９２号（特開平５−１７２１５２号）｝を開発し、既に
出願している。図１０〜図１２に示す等速自在継手はボ
タン部材３を備え、図１３に示す等速自在継手はボタン
部材を備えていないが、その他の構成については同様で
あるので、図１０〜図１２に示す等速自在継手につい
て、その概要を以下に説明する。The applicant of the present invention has a characteristic as described above, and as a constant velocity universal joint particularly suitable for a steering device, FIG.
0 to FIG. 12 constant velocity universal joint (Japanese Patent Application No. 6-86075
No.), a constant velocity universal joint shown in FIG. 13 (Japanese Patent Application No. 3-3442).
No. 92 (Japanese Patent Laid-Open No. 5-172152)} has been developed and already filed. The constant velocity universal joint illustrated in FIGS. 10 to 12 includes the button member 3, and the constant velocity universal joint illustrated in FIG. 13 does not include the button member, but the other configurations are similar, and therefore, FIGS. An outline of the constant velocity universal joint shown in will be described below.
【０００４】図１０および図１１に示すように、この既
出願に係わる等速自在継手は、軸線Ｘに平行な６つの平
坦面１ａで囲まれた正六角形状の中空穴を有する外輪１
と、外輪１の中空穴に組み込まれた内輪２と、内輪２と
外輪１との間に介装された６つのブロック状のボタン部
材３とを主要な要素として構成される。内輪２には軸部
４がセレーション結合等され、外輪１の開口と軸部４と
の間がブーツ５で被覆されている。また、外輪１の底部
には断面コ字状のエンドプレートが装着されている。As shown in FIGS. 10 and 11, the constant velocity universal joint according to this prior application has an outer ring 1 having a regular hexagonal hollow hole surrounded by six flat surfaces 1a parallel to the axis X.
The inner ring 2 incorporated in the hollow hole of the outer ring 1 and the six block-shaped button members 3 interposed between the inner ring 2 and the outer ring 1 are main components. A shaft portion 4 is serrated and connected to the inner ring 2, and a boot 5 covers the space between the opening of the outer ring 1 and the shaft portion 4. An end plate having a U-shaped cross section is attached to the bottom of the outer ring 1.
【０００５】図１２に示すように、内輪２には、外輪１
の平坦面１ａに対応した６つの球面状外壁面２ａ（同図
で右回転方向に２ａ１、２ａ２、・・・、２ａ６とす
る。）が形成されている。球面状外壁面２ａ１と球面状
外壁面２ａ４は、ＰＣＤ（荷重がかかる中心の円：継手
を使用する負荷条件によって異なる。）と中空穴の対角
線Ａ１との交点Ｏ１を球面中心とする半径ｒの球面で描
かれ、球面状外壁面２ａ３と球面状外壁面２ａ６は、Ｐ
ＣＤと中空穴の対角線Ａ２との交点Ｏ２を球面中心とす
る半径ｒの球面で描かれ、球面状外壁面２ａ２と球面状
外壁面２ａ５は、ＰＣＤと中空穴の対角線Ａ３との交点
Ｏ３を球面中心とする半径ｒの球面で描かれている。３
つの球面中心Ｏ１、Ｏ２、Ｏ３は、ＰＣＤ上の円周等配
位置にある。このように、各球面状外壁面２ａの球面中
心が継手中心Ｏから所定方向に所定量だけずれた位置に
オフセットされているため、円周等配位置にある３つの
球面状外壁面２ａ１、２ａ３、２ａ５はそれぞれ同図で
左回転方向に偏曲し、円周等配位置にある残りの３つの
球面状外壁面２ａ２、２ａ４、２ａ６はそれぞれ同図で
右回転方向に偏曲した形状をなす。そして、この偏曲の
向きが円周方向に隣り合った球面状外壁面２ａ間で相反
した関係になる。As shown in FIG. 12, the inner ring 2 has an outer ring 1
Six spherical outer wall surfaces 2a (corresponding to 2a1, 2a2, ..., 2a6 in the clockwise direction in the figure) corresponding to the flat surface 1a of the above are formed. The spherical outer wall surface 2a1 and the spherical outer wall surface 2a4 have a radius r of which the spherical center is the intersection O1 of the PCD (the center circle on which the load is applied: it depends on the load condition using the joint) and the diagonal line A1 of the hollow hole. The spherical outer wall surface 2a3 and the spherical outer wall surface 2a6 are drawn as spherical surfaces.
The spherical outer wall surface 2a2 and the spherical outer wall surface 2a5 are drawn as a spherical surface having a radius r whose center is the intersection O2 of the CD and the diagonal line A2 of the hollow hole. It is drawn as a spherical surface with a radius r as the center. 3
The two spherical centers O1, O2, O3 are equidistantly arranged on the circumference of the PCD. As described above, since the spherical center of each spherical outer wall surface 2a is offset from the joint center O by a predetermined amount in the predetermined direction, the three spherical outer wall surfaces 2a1, 2a3 located at the circumferentially equidistant positions. 2a5 is bent in the left rotation direction in the same figure, and the remaining three spherical outer wall surfaces 2a2, 2a4, 2a6 in the circumferentially equidistant positions are each bent in the right rotation direction in the same figure. . Then, the direction of the inflection has a contradictory relationship between the spherical outer wall surfaces 2a adjacent to each other in the circumferential direction.
【０００６】ボタン部材３は、軸方向縦長のブロック状
をなし、外輪１の平坦面１ａに適合接触する平坦状の外
側面３ａと、内輪２の球面状外壁面２ａに適合接触する
球面状の内側面３ｂとを有する。The button member 3 is in the form of a block that is vertically long in the axial direction, and has a flat outer surface 3a that conforms to the flat surface 1a of the outer ring 1 and a spherical outer surface that conforms to the spherical outer wall surface 2a of the inner ring 2. And an inner surface 3b.
【０００７】内輪２と外輪１との間のトルク伝達は、内
輪２の球面状外壁面２ａとボタン部材３の内側面３ｂと
の接触部、ボタン部材３の外側面３ａと外輪１の平坦面
１ａとの接触部を介してなされる。例えば、図１２にお
いて、駆動軸となる軸部４が同図で左回転方向に回転す
ると、円周等配位置にある３つの球面状外壁面２ａ１、
２ａ３、２ａ５とボタン部材３の内側面３ｂとの接触
部、および、球面状外壁面２ａ１、２ａ３、２ａ５に対
応するボタン部材３の外側面３ａと外輪１の平坦面１ａ
との接触部を介して、軸部４→内輪２→ボタン部材３→
外輪１といった経路で回転トルクが伝達される。The torque is transmitted between the inner ring 2 and the outer ring 1 by the contact portion between the spherical outer wall surface 2a of the inner ring 2 and the inner side surface 3b of the button member 3, the outer surface 3a of the button member 3 and the flat surface of the outer ring 1. It is done through the contact part with 1a. For example, in FIG. 12, when the shaft portion 4 serving as the drive shaft rotates in the leftward rotation direction in the figure, the three spherical outer wall surfaces 2a1 at the circumferentially equidistant positions,
2a3, 2a5 and the inner surface 3b of the button member 3, and the outer surface 3a of the button member 3 and the flat surface 1a of the outer ring 1 corresponding to the spherical outer wall surfaces 2a1, 2a3, 2a5.
Shaft 4 → Inner ring 2 → Button member 3 →
Rotational torque is transmitted through a route such as the outer ring 1.
【０００８】[0008]
【発明が解決しようとする課題】ところで、上述した等
速自在継手は、高作動角、小型・軽量、低コストで、し
かも回転バックラッシュを小さくすることが可能であ
り、ステアリング装置用等速自在継手として好適なもの
であった。The constant velocity universal joint described above has a high operating angle, a small size, a light weight, a low cost, and can reduce the rotary backlash, and is a constant velocity universal joint for a steering device. It was suitable as a joint.
【０００９】しかしながら、回転バックラッシュをより
一層低減するためには、内輪、ボタン部材、外輪の精度
を高度に管理する必要があり、そのためコスト的に不利
になることも予想される。また、精度を高度に管理した
としても、長期使用による接触面の摩耗等により、回転
バックラッシュが増大することも心配される。さらに、
回転バックラッシュを防止するために、各構成構成部材
間の隙間を詰めると、組立が面倒になるという問題もあ
る。However, in order to further reduce the rotational backlash, it is necessary to highly control the accuracy of the inner ring, the button member, and the outer ring, which may be disadvantageous in terms of cost. Further, even if the precision is controlled to a high degree, there is a concern that the rotational backlash may increase due to wear of the contact surface due to long-term use. further,
If the gaps between the constituent members are reduced to prevent the rotation backlash, there is a problem that the assembly becomes troublesome.
【００１０】本発明は、上記に例示したような滑り型の
等速自在継手において、コスト面、組立性に配慮しつ
つ、回転バックラッシュを効果的に防止することを目的
とするものである。It is an object of the present invention to effectively prevent rotational backlash in the sliding type constant velocity universal joint as exemplified above, while considering cost and assemblability.
【００１１】[0011]
【課題を解決するための手段】請求項１は、内輪を複数
の分割体で構成すると共に、内輪の内壁面と、軸部の外
壁面と、両者の間に介装したくさび部材とによってくさ
びを形成し、くさび部材を弾性手段でくさびの作用する
方向に押圧することにより、内輪を外輪の平坦面側に押
圧したものである。According to a first aspect of the present invention, the inner ring is composed of a plurality of divided bodies, and the inner wall surface of the inner ring, the outer wall surface of the shaft portion, and a wedge member interposed therebetween are used to form a wedge. Is formed and the wedge member is pressed by the elastic means in the direction in which the wedge acts, thereby pressing the inner ring toward the flat surface side of the outer ring.
【００１２】請求項２は、内輪を複数の分割体で構成す
ると共に、内輪の内壁面と軸部の外壁面とによってくさ
びを形成し、内輪と軸部とを弾性手段で前記くさびの作
用する方向に相互に押圧することにより、内輪を外輪の
平坦面側に押圧したものである。According to a second aspect of the present invention, the inner ring is composed of a plurality of divided bodies, and a wedge is formed by the inner wall surface of the inner ring and the outer wall surface of the shaft portion, and the inner ring and the shaft portion act as the wedge by elastic means. The inner ring is pressed against the flat surface side of the outer ring by pressing each other in the directions.
【００１３】上記構成において、外輪と軸部とを除く少
なくとも一の構成部材を樹脂材料で形成しても良い（請
求項３）。In the above structure, at least one of the constituent members other than the outer ring and the shaft portion may be made of a resin material (claim 3).
【００１４】請求項４は、軸線に平行な複数の平坦面で
囲まれた正多角形状の中空穴を有する外輪と、外輪の中
空穴に組み込まれ、外輪の平坦面に接触し又は外輪の平
坦面との間に介装されたボタン部材に接触する球面状外
壁面を有する内輪と、内輪に連結される軸部とを備えた
等速自在継手において、外輪と軸部とを除く少なくとも
一の構成部材を樹脂材料で形成したものである。According to a fourth aspect of the present invention, an outer ring having a regular polygonal hollow hole surrounded by a plurality of flat surfaces parallel to the axis, and a hollow hole of the outer ring, which is incorporated into the outer ring, comes into contact with the flat surface of the outer ring or has a flat outer ring. A constant velocity universal joint including an inner ring having a spherical outer wall surface that comes into contact with a button member interposed between the inner surface and a shaft, and a shaft portion connected to the inner ring, and at least one of the outer ring and the shaft portion is excluded. The constituent members are made of a resin material.
【００１５】[0015]
【発明の実施の形態】以下、本発明の実施形態を図面に
従って説明する。尚、図１０〜図１２に示す従来構成に
対応する部材および部分には同一の符号を付してある。Embodiments of the present invention will be described below with reference to the drawings. Members and portions corresponding to the conventional configuration shown in FIGS. 10 to 12 are designated by the same reference numerals.
【００１６】図１および図２は、本発明の第１の実施形
態を示している。図１は全体構成を示し、図２は主要構
成部材を示している。この等速自在継手は、軸線Ｘに平
行な６つの平坦面１ａで囲まれた正六角形状の中空穴を
有する外輪１と、外輪１の中空穴に組み込まれた３つの
内輪２と、内輪２と外輪１との間に介装された６つのブ
ロック状のボタン部材３と、内輪２の内壁面２ｂ（２ｂ
１、２ｂ２）に組み込まれた軸部４と、内輪２の内壁面
２ｂと軸部４の外壁面４ｂ（４ｂ１、４ｂ２）との間に
介装された３対のくさび部材５と、対になるくさび部材
５の間に介装された３つの弾性手段例えばコイルスプリ
ング６とを主要な要素として構成される。1 and 2 show a first embodiment of the present invention. FIG. 1 shows the overall structure, and FIG. 2 shows the main constituent members. This constant velocity universal joint has an outer ring 1 having a regular hexagonal hollow hole surrounded by six flat surfaces 1 a parallel to the axis X, three inner rings 2 incorporated in the hollow hole of the outer ring 1, and an inner ring 2. Six block-shaped button members 3 interposed between the inner ring 2 and the outer ring 1, and the inner wall surface 2b (2b) of the inner ring 2.
1, 2b2), three pairs of wedge members 5, which are interposed between the inner wall surface 2b of the inner ring 2 and the outer wall surface 4b (4b1, 4b2) of the inner ring 2, and the pair of wedge members 5. It comprises three elastic means such as a coil spring 6 interposed between the wedge members 5 as main elements.
【００１７】各内輪２には、それぞれ、外輪１の平坦面
１ａに対応した２つの球面状外壁面２ａが形成されてい
る（同図で右回転方向に２ａ１、２ａ２、・・・、２ａ
６とする。）。球面状外壁面２ａ１と球面状外壁面２ａ
４は、ＰＣＤ（荷重がかかる中心の円：継手を使用する
負荷条件によって異なる。）と中空穴の対角線Ａ１との
交点Ｏ１を球面中心とする半径ｒの球面で描かれ、球面
状外壁面２ａ３と球面状外壁面２ａ６は、ＰＣＤと中空
穴の対角線Ａ２との交点Ｏ２を球面中心とする半径ｒの
球面で描かれ、球面状外壁面２ａ２と球面状外壁面２ａ
５は、ＰＣＤと中空穴の対角線Ａ３との交点Ｏ３を球面
中心とする半径ｒの球面で描かれている。３つの球面中
心Ｏ１、Ｏ２、Ｏ３は、ＰＣＤ上の円周等配位置にあ
る。このように、各球面状外壁面２ａの球面中心が継手
中心Ｏから所定方向に所定量だけずれた位置にオフセッ
トされているため、円周等配位置にある３つの球面状外
壁面２ａ１、２ａ３、２ａ５はそれぞれ同図で左回転方
向に偏曲し、円周等配位置にある残りの３つの球面状外
壁面２ａ２、２ａ４、２ａ６はそれぞれ同図で右回転方
向に偏曲した形状をなす。そして、この偏曲の向きが円
周方向に隣り合った球面状外壁面２ａ間で相反した関係
になる。Each inner ring 2 is formed with two spherical outer wall surfaces 2a corresponding to the flat surface 1a of the outer ring 1 (2a1, 2a2, ..., 2a in the clockwise direction in the figure).
6 is assumed. ). Spherical outer wall surface 2a1 and spherical outer wall surface 2a
4 is drawn as a spherical outer surface 2a3 having a radius r whose center is the intersection O1 of PCD (a center circle on which a load is applied: it depends on the load condition using the joint) and the diagonal line A1 of the hollow hole. The spherical outer wall surface 2a6 and the spherical outer wall surface 2a6 are drawn as a spherical surface having a radius r with the intersection O2 of the PCD and the diagonal line A2 of the hollow hole as the spherical center, and the spherical outer wall surface 2a2 and the spherical outer wall surface 2a.
5 is drawn as a spherical surface having a radius r with the center O3 of the intersection O3 of the diagonal line A3 of the PCD and the hollow hole. The three spherical centers O1, O2, O3 are equidistantly arranged on the PCD. As described above, since the spherical center of each spherical outer wall surface 2a is offset from the joint center O by a predetermined amount in the predetermined direction, the three spherical outer wall surfaces 2a1, 2a3 located at the circumferentially equidistant positions. 2a5 is bent in the left rotation direction in the same figure, and the remaining three spherical outer wall surfaces 2a2, 2a4, 2a6 in the circumferentially equidistant positions are each bent in the right rotation direction in the same figure. . Then, the direction of the inflection has a contradictory relationship between the spherical outer wall surfaces 2a adjacent to each other in the circumferential direction.
【００１８】各ボタン部材３は、それぞれ、軸方向縦長
のブロック状をなし、外輪１の平坦面１ａに適合接触す
る平坦状の外側面３ａと、内輪２の球面状外壁面２ａに
適合接触する球面状の内側面３ｂとを有する。Each of the button members 3 is in the form of a block that is vertically long in the axial direction, and has a flat outer surface 3a that conforms to the flat surface 1a of the outer ring 1 and a spherical outer wall surface 2a of the inner ring 2. It has a spherical inner surface 3b.
【００１９】各内輪２の内壁面２ｂは、それぞれ、軸方
向中心を境にした２つのテーパ状内壁面２ｂ１、２ｂ２
で構成される｛図１（ｂ）参照｝。テーパ状内壁面２ｂ
１、２ｂ２は、それぞれ、円周方向中心を境にして、円
周方向の相反した向きに傾斜し｛図１（ａ）参照｝かつ
軸方向の一方に傾斜した２つのテーパ面（符号省略）で
構成されるが、軸方向の傾斜の向きは、テーパ状内壁面
２ｂ１とテーパ状内壁面２ｂ２との間で相反している。The inner wall surface 2b of each inner ring 2 has two tapered inner wall surfaces 2b1 and 2b2 with the center in the axial direction as a boundary.
{See FIG. 1B}. Tapered inner wall surface 2b
Two tapered surfaces 1 and 2b2 are inclined in opposite directions in the circumferential direction with respect to the center of the circumferential direction as a boundary (see FIG. 1 (a)) and are inclined in one axial direction (reference numeral is omitted). However, the directions of the inclination in the axial direction are opposite to each other between the tapered inner wall surface 2b1 and the tapered inner wall surface 2b2.
【００２０】内輪２の内壁面２ｂに組み込まれる軸部４
の外壁面４ｂは、軸方向中心を境にした２つのテーパ状
外壁面４ｂ１、４ｂ２で構成される。テーパ状外壁面４
ｂ１、４ｂ２は、それぞれ、正六角形状の横断面を有し
｛図２（ａ）参照｝かつ軸方向の一方に傾斜している
が、軸方向の傾斜の向きは、テーパ状外壁面４ｂ１とテ
ーパ状外壁面４ｂ２との間で相反している。A shaft portion 4 incorporated in the inner wall surface 2b of the inner ring 2.
The outer wall surface 4b is composed of two tapered outer wall surfaces 4b1 and 4b2 with the center in the axial direction as a boundary. Tapered outer wall surface 4
b1 and 4b2 each have a regular hexagonal cross section {see FIG. 2 (a)} and are inclined in one axial direction, but the direction of the axial inclination is the same as the tapered outer wall surface 4b1. It contradicts with the tapered outer wall surface 4b2.
【００２１】各くさび部材５は、テーパ状外側面５ａと
テーパ状内側面５ｂとを備えている。テーパ状外側面５
ａおよびテーパ状内側面５ｂは、それぞれ、円周方向の
相反した向きに傾斜し｛図１（ａ）参照｝かつ軸方向の
一方に傾斜した｛図１（ｂ）参照｝２つのテーパ面（符
号省略）で構成されるが、軸方向の傾斜の向きは、テー
パ状外側面４ａとテーパ状内側面４ｂとの間で相反して
いる。また、くさび部材５の一方の端部には、コイルス
プリング６の一端を収容するための凹部５ｃ｛図２
（ｃ）参照｝が形成されている。Each wedge member 5 has a tapered outer side surface 5a and a tapered inner side surface 5b. Tapered outer surface 5
a and the tapered inner side surface 5b are inclined in opposite directions in the circumferential direction {see FIG. 1 (a)} and inclined in one axial direction {see FIG. 1 (b)}. Although the reference numerals are omitted), the directions of the inclination in the axial direction are opposite between the tapered outer side surface 4a and the tapered inner side surface 4b. In addition, one end of the wedge member 5 has a recess 5c for accommodating one end of the coil spring 6 (see FIG. 2).
(See (c)} is formed.
【００２２】図１（ｂ）に示すように、内輪２のテーパ
状内壁面２ｂ１とこれに対応する軸部４のテーパ状外側
面４ｂ１とは軸方向の傾斜の向きが相反し、同様に、テ
ーパ状内壁面２ｂ２とこれに対応するテーパ状外壁面４
ｂ２とは軸方向の傾斜の向きが相反している。くさび部
材５は、上記のようなテーパ状内壁面２ｂ１、２ｂ２と
テーパ状外壁面４ｂ１、４ｂ２との間に形成される、向
きの相異なる２つの軸方向のくさび空間に、相互間の向
きを逆にして、２個一対として介装される。一対のくさ
び部材５のテーパ状外側面５ａはそれぞれ内輪２のテー
パ状内壁面２ｂ１、２ｂ２にテーパ嵌合し、テーパ状内
側面５ａはそれぞれ軸部４のテーパ状外壁面４ｂ１、４
ｂ２にテーパ嵌合する。このようにして、内輪２のテー
パ状内壁面２ｂ１、２ｂ２、軸部４のテーパ状外壁面４
ｂ１、４ｂ２、および、両者の間に介装された一対のく
さび部材５によって、向きが相異なる２つの軸方向のく
さびが形成される。そして、一対のくさび部材５の相対
向した凹部５ｃにコイルスプリングの両端が収容され、
その弾性力によって、各くさび部材５をそれぞれくさび
の作用する方向（軸方向反対側）に弾性的に押圧する。
そのため、内輪２は一対のくさび部材５によって外輪１
の平坦面１ａの側に押圧され、これにより、内輪２の球
面状外壁面２ａとボタン部材３の内側面３ｂとの間、ボ
タン部材３の外側面３ａと外輪１の平坦面１ａとの間の
隙間が詰められ、円周方向のガタツキがなくなる。尚、
組立に際しては、コイルスプリング６を圧縮し、一対の
くさび部材５間の間隔を狭めた状態にすることにより、
内輪２およびボタン部材３を隙間をもって外輪１に組み
入れることができるので、組立が容易である。そして、
組み入れ後に、コイルスプリング６の圧縮を解除する
と、上記の態様で、上記構成部材相互間の隙間が詰めら
れ、円周方向のガタツキがなくなる。As shown in FIG. 1 (b), the tapered inner wall surface 2b1 of the inner ring 2 and the corresponding tapered outer surface 4b1 of the shaft portion 4 have opposite axial inclination directions, and similarly, Tapered inner wall surface 2b2 and corresponding tapered outer wall surface 4
The direction of inclination in the axial direction is opposite to that of b2. The wedge member 5 is formed between the tapered inner wall surfaces 2b1 and 2b2 and the tapered outer wall surfaces 4b1 and 4b2 as described above. On the contrary, two pieces are inserted as a pair. The tapered outer side surfaces 5a of the pair of wedge members 5 are fitted into the tapered inner wall surfaces 2b1 and 2b2 of the inner ring 2, respectively, and the tapered inner side surfaces 5a are respectively tapered outer wall surfaces 4b1 and 4b of the shaft portion 4.
Tapered to b2. In this way, the tapered inner wall surfaces 2b1 and 2b2 of the inner ring 2 and the tapered outer wall surface 4 of the shaft portion 4 are formed.
Two axial wedges having different directions are formed by b1, 4b2 and the pair of wedge members 5 interposed therebetween. Then, both ends of the coil spring are housed in the recesses 5c of the pair of wedge members 5 which face each other,
The elastic force presses each wedge member 5 elastically in the direction in which the wedge acts (on the opposite side in the axial direction).
Therefore, the inner ring 2 is formed by the pair of wedge members 5
Between the spherical outer wall surface 2a of the inner ring 2 and the inner side surface 3b of the button member 3, and between the outer side surface 3a of the button member 3 and the flat surface 1a of the outer ring 1 of the inner ring 2. The gap is closed and there is no rattling in the circumferential direction. still,
At the time of assembly, the coil spring 6 is compressed so that the gap between the pair of wedge members 5 is narrowed,
Since the inner ring 2 and the button member 3 can be incorporated into the outer ring 1 with a gap, the assembly is easy. And
When the compression of the coil spring 6 is released after the assembling, the gaps between the constituent members are closed in the above-described manner, and the rattling in the circumferential direction is eliminated.
【００２３】軸部４と外輪１との間のトルク伝達は、軸
部４の外壁面４ｂとくさび部材５との接触部、くさび部
材５と内輪２の内壁面２ｂとの接触部、内輪２の球面状
外壁面２ａとボタン部材３との接触部、ボタン部材３と
外輪１の平坦面１ａとの接触部を介してなされる。Torque is transmitted between the shaft portion 4 and the outer ring 1 by the contact portion between the outer wall surface 4b of the shaft portion 4 and the wedge member 5, the contact portion between the wedge member 5 and the inner wall surface 2b of the inner ring 2, and the inner ring 2. Through the contact portion between the spherical outer wall surface 2a and the button member 3 and the contact portion between the button member 3 and the flat surface 1a of the outer ring 1.
【００２４】上記第１の実施形態は、軸方向のくさびを
利用して円周方向のガタツキを防止したものであるが、
図３および図４に示す第２の実施形態は、円周方向のく
さびを利用して円周方向のガタツキを防止したものであ
る。In the first embodiment, the axial wedge is used to prevent the rattling in the circumferential direction.
The second embodiment shown in FIGS. 3 and 4 utilizes a circumferential wedge to prevent circumferential rattling.
【００２５】各内輪２の内壁面２ｂは、それぞれ、円周
方向中心を境にして、円周方向の相反した向きに傾斜し
｛図３（ａ）参照｝かつ軸方向にストレートな｛図３
（ｂ）参照｝な２つのテーパ状内壁面２ｂ３、２ｂ４で
構成される。The inner wall surface 2b of each inner ring 2 is inclined in opposite circumferential directions with respect to the circumferential center (see FIG. 3 (a)) and is straight in the axial direction (FIG. 3).
(See (b)). Two tapered inner wall surfaces 2b3, 2b4.
【００２６】内輪２の内壁面２ｂに組み込まれる軸部４
の外壁面４ｂには、接線方向でかつ軸方向にストレート
な３つの平坦状外壁面４ｂ３が円周等間隔に形成されて
いる｛図４（ａ）参照｝。各平坦状外壁面４ｂ３は外壁
面４ｂの最外径よりも内径側に凹入しており、各平坦状
外壁面４ｂ３の軸方向両側にはそれぞれ鍔部４ｃ、４ｄ
が形成される。A shaft portion 4 incorporated in the inner wall surface 2b of the inner ring 2.
On the outer wall surface 4b, three flat outer wall surfaces 4b3 that are tangential and axially straight are formed at equal intervals around the circumference {see FIG. 4 (a)}. Each flat outer wall surface 4b3 is recessed on the inner diameter side with respect to the outermost diameter of the outer wall surface 4b, and the flange portions 4c and 4d are provided on both axial sides of each flat outer wall surface 4b3.
Is formed.
【００２７】くさび部材５’は、テーパ状外側面５’ａ
と平坦状内側面５’ｂとを備えている。また、くさび部
材５’の一方の端部には、コイルスプリング６の一端を
収容するための凹部５’ｃ｛図４（ｃ）参照｝が形成さ
れている。The wedge member 5'has a tapered outer surface 5'a.
And a flat inner surface 5'b. A recess 5'c (see FIG. 4 (c)) for accommodating one end of the coil spring 6 is formed at one end of the wedge member 5 '.
【００２８】図３（ａ）に示すように、くさび部材５’
は、上記のような内輪２のテーパ状内壁面２ｂ３、２ｂ
４と軸部４の平坦状外壁面４ｂ３との間に形成される、
向きの相異なる２つの円周方向のくさび空間に、相互間
の向きを逆にして、２個一対として介装される。一対の
くさび部材５’のテーパ状外側面５’ａはそれぞれ内輪
２のテーパ状内壁面２ｂ３、２ｂ４にテーパ嵌合し、平
坦状内側面５’ｂはそれぞれ軸部４の平坦状外壁面４ｂ
３に嵌合する。このようにして、内輪２のテーパ状内壁
面２ｂ３、２ｂ４、軸部４の平坦状外壁面４ｂ３、およ
び、両者の間に介装された一対のくさび部材５’によっ
て、向きが相異なる２つの円周方向のくさびが形成され
る。そして、一対のくさび部材５’の相対向した凹部
５’ｃにコイルスプリング６の両端が収容され、その弾
性力によって、各くさび部材５’をそれぞれくさびの作
用する方向（円周方向反対側）に弾性的に押圧する。そ
のため、内輪２は一対のくさび部材５’によって外輪１
の平坦面１ａの側に押圧され、これにより、内輪２の球
面状外壁面２ａとボタン部材３の内側面３ｂとの間、ボ
タン部材３の外側面３ａと外輪１の平坦面１ａとの間の
隙間が詰められ、円周方向のガタツキがなくなる。尚、
組立に際しては、コイルスプリング６を圧縮し、一対の
くさび部材５’間の間隔を狭めた状態にすることによ
り、内輪２およびボタン部材３を隙間をもって外輪１に
組み入れることができるので、組立が容易である。そし
て、組み入れ後に、コイルスプリング６の圧縮を解除す
ると、上記の態様で、隙間が詰められ、円周方向のガタ
ツキがなくなる。As shown in FIG. 3A, the wedge member 5 '
Is the tapered inner wall surface 2b3, 2b of the inner ring 2 as described above.
4 and the flat outer wall surface 4b3 of the shaft portion 4,
Two circumferentially-wedge spaces having different directions are inserted as a pair with the directions thereof being reversed. The tapered outer side surfaces 5'a of the pair of wedge members 5'are respectively fitted into the tapered inner wall surfaces 2b3, 2b4 of the inner ring 2, and the flat inner side surfaces 5'b are respectively the flat outer surface 4b of the shaft portion 4.
3 is fitted. In this way, the tapered inner wall surfaces 2b3, 2b4 of the inner ring 2, the flat outer wall surface 4b3 of the shaft portion 4, and the pair of wedge members 5 ′ interposed between the two allow the two directions to be different from each other. A circumferential wedge is formed. The opposite ends of the coil spring 6 are housed in the recesses 5'c of the pair of wedge members 5 ', which face each other, and the elastic force of each of the wedge members 5'in the direction in which the wedge acts (opposite to the circumferential direction). Elastically press against. Therefore, the inner ring 2 is connected to the outer ring 1 by the pair of wedge members 5 '.
Between the spherical outer wall surface 2a of the inner ring 2 and the inner side surface 3b of the button member 3, and between the outer side surface 3a of the button member 3 and the flat surface 1a of the outer ring 1 of the inner ring 2. The gap is closed and there is no rattling in the circumferential direction. still,
At the time of assembly, the coil spring 6 is compressed so that the gap between the pair of wedge members 5 ′ is narrowed, so that the inner ring 2 and the button member 3 can be incorporated into the outer ring 1 with a gap, so that the assembly is easy. Is. Then, when the compression of the coil spring 6 is released after the assembling, the gap is closed in the above-described mode, and the rattling in the circumferential direction is eliminated.
【００２９】図５および図６に示す第３の実施形態は、
内輪２の内壁面２ｂと軸部４の外壁面４ｂとによって形
成した軸方向のくさびを利用して円周方向のガタツキを
防止したものである。すなわち、この実施形態において
は、上述した実施形態におけるくさび部材５（５’）が
省略され、構造のより一層の簡略が図られている。The third embodiment shown in FIGS. 5 and 6 is
By using the axial wedge formed by the inner wall surface 2b of the inner ring 2 and the outer wall surface 4b of the shaft portion 4, rattling in the circumferential direction is prevented. That is, in this embodiment, the wedge member 5 (5 ') in the above-described embodiment is omitted, and the structure is further simplified.
【００３０】各内輪２の内壁面２ｂは、それぞれ、円周
方向中心を境にして、円周方向の相反した向きに傾斜し
｛図５（ａ）参照｝かつ軸方向の一方に傾斜した｛図５
（ｂ）参照｝テーパ状内壁面２ｂ５で構成される。テー
パ状内壁面２ｂ５の奥部側には、円板プレート７の外周
縁に係合する段部２ｃが形成されている。The inner wall surface 2b of each inner ring 2 is inclined in opposite directions in the circumferential direction with the center in the circumferential direction as a boundary {see FIG. 5 (a)} and inclined in one axial direction. Figure 5
See (b)} It is configured by the tapered inner wall surface 2b5. A step portion 2c that engages with the outer peripheral edge of the disc plate 7 is formed on the inner side of the tapered inner wall surface 2b5.
【００３１】軸部４の外壁面４ｂは、正六角形状の横断
面を有し｛図６（ａ）参照｝かつ軸方向の一方に傾斜し
たテーパ状外壁面４ｂ４で構成される。また、その軸端
には、コイルスプリング６の一端を収容するための凹部
４ｅが形成されている。The outer wall surface 4b of the shaft portion 4 has a regular hexagonal cross section {see FIG. 6 (a)} and is constituted by a tapered outer wall surface 4b4 inclined in one axial direction. In addition, a recess 4e for accommodating one end of the coil spring 6 is formed at the axial end thereof.
【００３２】図５（ｂ）に示すように、内輪２のテーパ
状内壁面２ｂ５と軸部４のテーパ状外壁面４ｂ４とがテ
ーパ嵌合することにより、軸方向のくさびが形成され
る。そして、軸部４の凹部４ｅに一端が収容され、他端
が円板プレート７に当接するコイルスプリング６の弾性
力によって、内輪２と軸部４とが相互にくさびの作用す
る方向（軸方向反対側）に弾性的に押圧される。そのた
め、内輪２は軸部４によって外輪１の平坦面１ａの側に
押圧され、これにより、内輪２の球面状外壁面２ａとボ
タン部材３の内側面３ｂとの間、ボタン部材３の外側面
３ａと外輪１の平坦面１ａとの間の隙間が詰められ、円
周方向のガタツキがなくなる。尚、組立に際しては、コ
イルスプリング６を圧縮した状態にすることにより、内
輪２およびボタン部材３を隙間をもって外輪１に組み入
れることができるので、組立が容易である。そして、組
み入れ後に、コイルスプリング６の圧縮を解除すると、
上記の態様で、隙間が詰められ、円周方向のガタツキが
なくなる。As shown in FIG. 5 (b), the tapered inner wall surface 2b5 of the inner ring 2 and the tapered outer wall surface 4b4 of the shaft portion 4 are taper-fitted with each other to form a wedge in the axial direction. The elastic force of the coil spring 6 whose one end is housed in the concave portion 4e of the shaft portion 4 and whose other end is in contact with the disc plate 7 causes the inner ring 2 and the shaft portion 4 to mutually act in a wedge direction (axial direction). The other side) is elastically pressed. Therefore, the inner ring 2 is pressed by the shaft portion 4 toward the flat surface 1a side of the outer ring 1, and as a result, between the spherical outer wall surface 2a of the inner ring 2 and the inner side surface 3b of the button member 3 and the outer side surface of the button member 3. The gap between 3a and the flat surface 1a of the outer ring 1 is closed, and rattling in the circumferential direction is eliminated. At the time of assembly, the inner ring 2 and the button member 3 can be assembled in the outer ring 1 with a gap by keeping the coil spring 6 in a compressed state, which facilitates the assembly. When the compression of the coil spring 6 is released after incorporation,
In the above-described mode, the gap is closed and the rattling in the circumferential direction is eliminated.
【００３３】軸部４と外輪１との間のトルク伝達は、軸
部４の外壁面４ｂと内輪２の内壁面２ｂとの接触部、内
輪２の球面状外壁面２ａとボタン部材３との接触部、ボ
タン部材３と外輪１の平坦面１ａとの接触部を介してな
される。The torque is transmitted between the shaft portion 4 and the outer ring 1 by the contact portion between the outer wall surface 4b of the shaft portion 4 and the inner wall surface 2b of the inner ring 2, the spherical outer wall surface 2a of the inner ring 2 and the button member 3. The contact portion is formed through the contact portion between the button member 3 and the flat surface 1a of the outer ring 1.
【００３４】図７および図８に示す第４の実施形態は、
基本的な考え方は第３の実施形態と同様であるが、軸部
４を軸部４１と軸部４２とに２分割し、内輪２の内壁面
２ｂと軸部４の外壁面４ｂとの間に向きが相異なる２つ
の軸方向のくさびを形成している点が異なる。The fourth embodiment shown in FIGS. 7 and 8 is
The basic idea is the same as in the third embodiment, but the shaft portion 4 is divided into a shaft portion 41 and a shaft portion 42, and the space between the inner wall surface 2b of the inner ring 2 and the outer wall surface 4b of the shaft portion 4 is divided. The difference is that two axial wedges having different directions are formed.
【００３５】各内輪２の内壁面２ｂは、それぞれ、軸方
向中心を境にした２つのテーパ状内壁面２ｂ６、２ｂ７
で構成される。テーパ状内壁面２ｂ６、２ｂ７は、それ
ぞれ、円周方向中心を境にして、円周方向の相反した向
きに傾斜し｛図７（ａ）参照｝かつ軸方向の一方に傾斜
した２つのテーパ面（符号省略）で構成されるが、軸方
向の傾斜の向きは、テーパ状内壁面２ｂ６とテーパ状内
壁面２ｂ７との間で相反している。The inner wall surface 2b of each inner ring 2 has two tapered inner wall surfaces 2b6, 2b7 with the axial center as a boundary.
It consists of. The tapered inner wall surfaces 2b6 and 2b7 are two tapered surfaces that are inclined in opposite directions in the circumferential direction with the center in the circumferential direction as a boundary (see FIG. 7 (a)) and are inclined in one axial direction. Although not shown, the directions of inclination in the axial direction are opposite between the tapered inner wall surface 2b6 and the tapered inner wall surface 2b7.
【００３６】軸部４の外壁面４ｂ（軸部４１の外壁面お
よび軸部４２外壁面）は、正六角形状の横断面を有し
｛図８（ａ）（ｂ）参照｝かつ軸方向の一方に傾斜した
テーパ状外壁面４１ｂ、４２ｂで構成される。テーパ状
外壁面４１ｂとテーパ状外壁面４２ｂとは、軸方向の傾
斜の向きが相反している。軸部４１の軸端と軸部４２の
軸端には、相互に適合する凹部４１ｃと凸部４２ｃが形
成され、また、軸部４２にはコイルスプリング６を収容
する凹部４２ｄが形成されている。The outer wall surface 4b of the shaft portion 4 (the outer wall surface of the shaft portion 41 and the outer wall surface of the shaft portion 42) has a regular hexagonal cross section {see FIGS. 8 (a) and 8 (b)} and in the axial direction. It is composed of tapered outer wall surfaces 41b and 42b that are inclined to one side. The taper-shaped outer wall surface 41b and the taper-shaped outer wall surface 42b have opposite axial inclination directions. The shaft end of the shaft portion 41 and the shaft end of the shaft portion 42 are formed with a recess 41c and a protrusion 42c which are compatible with each other, and the shaft portion 42 is formed with a recess 42d for accommodating the coil spring 6. .
【００３７】図７（ｂ）に示すように、内輪２のテーパ
状内壁面２ｂ６とこれに対応する軸部４１のテーパ状外
側面４１ｂとがテーパ嵌合し、同様に、内輪２のテーパ
状内壁面２ｂ７とこれに対応する軸部４２のテーパ状外
側面４２ｂとがテーパ嵌合することにより、向きが相異
なる２つの軸方向のくさびが形成される。そして、軸部
４２の凹部４２ｄ一端が収容され、他端が軸部４１の凹
部４１ｃの底壁に当接するコイルスプリング６の弾性力
によって、内輪２に対して、軸部４１と軸部４２とがく
さびの作用する方向（軸方向反対側）に弾性的に押圧さ
れる。そのため、内輪２は軸部４１および軸部４２によ
って外輪１の平坦面１ａの側に押圧され、これにより、
内輪２の球面状外壁面２ａとボタン部材３の内側面３ｂ
との間、ボタン部材３の外側面３ａと外輪１の平坦面１
ａとの間の隙間が詰められ、円周方向のガタツキがなく
なる。尚、組立に際しては、コイルスプリング６を圧縮
した状態にすることにより、内輪２およびボタン部材３
を隙間をもって外輪１に組み入れることができるので、
組立が容易である。そして、組み入れ後に、コイルスプ
リング６の圧縮を解除すると、上記の態様で、隙間が詰
められ、円周方向のガタツキがなくなる。As shown in FIG. 7 (b), the tapered inner wall surface 2b6 of the inner ring 2 and the corresponding tapered outer surface 41b of the shaft portion 41 are fitted in a tapered manner, and similarly, the inner ring 2 is tapered. By taper-fitting the inner wall surface 2b7 and the corresponding tapered outer surface 42b of the shaft portion 42, two axial wedges having different directions are formed. Then, by the elastic force of the coil spring 6 in which one end of the recess 42d of the shaft portion 42 is accommodated and the other end abuts the bottom wall of the recess 41c of the shaft portion 41, the shaft portion 41 and the shaft portion 42 are moved with respect to the inner ring 2. The wedge is elastically pressed in the direction in which the wedge works (opposite to the axial direction). Therefore, the inner ring 2 is pressed toward the flat surface 1a side of the outer ring 1 by the shaft portion 41 and the shaft portion 42, whereby
The spherical outer wall surface 2a of the inner ring 2 and the inner surface 3b of the button member 3
Between the outer surface 3 a of the button member 3 and the flat surface 1 of the outer ring 1.
The gap with a is closed, and there is no rattling in the circumferential direction. When assembling, the coil spring 6 is compressed so that the inner ring 2 and the button member 3 are
Since it can be incorporated into the outer ring 1 with a gap,
Easy to assemble. Then, when the compression of the coil spring 6 is released after the assembling, the gap is closed in the above-described mode, and the rattling in the circumferential direction is eliminated.
【００３８】尚、図９に例示するように、以上の実施形
態において、各内輪２の内壁面２ｂ（同図では２ｂ５）
に円周方向の溝８を設けると共に、各内輪２の溝８に１
つの円形リング９を嵌着した構成を併用しても良い。円
形リング９を嵌着することにより、各内輪２の軸方向位
置を略一致させ、各内輪２に作用するくさび力を略均等
にすることができる。As illustrated in FIG. 9, in the above embodiment, the inner wall surface 2b of each inner ring 2 (2b5 in the figure).
The groove 8 in the circumferential direction is provided on the
A configuration in which two circular rings 9 are fitted may be used together. By fitting the circular ring 9 in place, the axial positions of the inner rings 2 can be made to substantially coincide with each other, and the wedge forces acting on the inner rings 2 can be made substantially uniform.
【００３９】以上の実施形態において、外輪１と軸部４
とを除く少なくとも一の構成部材（内輪２、ボタン部材
３、くさび部材５、５’）を樹脂材料で形成することも
できる。継手の軽量化、コストダウン、摺動抵抗の低減
を図る上で有効である。また、樹脂材料の材料弾性によ
って、振動のより一層の低減にもなる。In the above embodiment, the outer ring 1 and the shaft portion 4 are
It is also possible to form at least one of the constituent members (the inner ring 2, the button member 3, the wedge members 5 and 5 ') except for and with a resin material. This is effective in reducing the weight of joints, cost, and sliding resistance. Further, the material elasticity of the resin material further reduces vibration.
【００４０】上記樹脂材料としては、例えば、ポリアミ
ド（ＰＡ）、ポリアセタール（ＰＯＭ）、ポリエーテル
サルフォン（ＰＥＳ）、ポリエーテルエーテルケトン
（ＰＥＥＫ）、ポリアミドイミド（ＰＡＩ）、ポリエー
テルイミド（ＰＥＩ）、ポリフェニレンサルファイド
（ＰＰＳ）、熱可塑性ポリイミド等の熱可塑性樹脂の
他、フェノール樹脂、全芳香族ポリイミド（ＰＩ）等の
熱硬化性樹脂等を用いることができる。ただ、摺動抵
抗低減の観点から良好な自己潤滑性を有すること、耐
久性確保の観点から機械的特性、摩耗特性、熱的特性に
優れていること、適度な弾性を有すること、また、
製作コスト低減の観点から安価でかつ易成形性に優れた
材料であることが望ましいことを考慮すると、これら合
成樹脂の中でも、ポリアミド樹脂（ＰＡ）、ポリエーテ
ルエーテルケトン樹脂（ＰＥＥＫ）が好ましいと考えら
れ、その中でも、ポリアミド樹脂（ＰＡ）が特に好まし
いと考えられる。Examples of the resin material include polyamide (PA), polyacetal (POM), polyether sulfone (PES), polyether ether ketone (PEEK), polyamide imide (PAI), polyether imide (PEI), In addition to thermoplastic resins such as polyphenylene sulfide (PPS) and thermoplastic polyimide, thermosetting resins such as phenol resin and wholly aromatic polyimide (PI) can be used. However, from the viewpoint of reducing sliding resistance, it has good self-lubricating properties, from the viewpoint of ensuring durability, it has excellent mechanical properties, wear properties, and thermal properties, and has appropriate elasticity.
Considering that it is desirable to use a material that is inexpensive and has excellent moldability from the viewpoint of manufacturing cost reduction, it is considered that among these synthetic resins, polyamide resin (PA) and polyether ether ketone resin (PEEK) are preferable. Among them, polyamide resin (PA) is considered to be particularly preferable.
【００４１】ポリアミドとしては、例えばポリアミド
６、ポリアミド６−６、ポリアミド４−６、ポリアミド
６−１０、ポリアミド６−１２、ポリアミド１１、ポリ
アミド１２等を用いることができる。As the polyamide, for example, polyamide 6, polyamide 6-6, polyamide 4-6, polyamide 6-10, polyamide 6-12, polyamide 11, polyamide 12, etc. can be used.
【００４２】また、摺動特性のより一層の低減を図るた
め、上記ポリアミド樹脂にフッ素系樹脂等を含有させて
も良い。フッ素系樹脂としては、例えばポリテトラフル
オロエチレン樹脂（ＰＴＦＥ）、テトラフルオロエチレ
ン−パーフルオロアルキルビニルエーテル共重合体（Ｐ
ＦＡ）、テトラフルオロエチレン−ヘキサプロロプロピ
レン共重合体（ＦＥＰ）、テトラフロオロエチレン−エ
チレン共重合体（ＥＴＦＥ）、ポリクロロトリフロロエ
チレン樹脂（ＰＣＴＦＥ）、ポリビニルフルオライド樹
脂（ＰＶＦ）等を用いることができ、その中でも、ＰＴ
ＦＥ、ＰＦＡ、ＦＥＰ、ＥＴＦＥが望ましく、これらの
中でも摩擦係数が最も低いＰＴＦＥ（動摩擦係数０．１
０）が特に望ましい。Further, in order to further reduce the sliding characteristics, the above polyamide resin may contain a fluorine resin or the like. Examples of the fluorine-based resin include polytetrafluoroethylene resin (PTFE) and tetrafluoroethylene-perfluoroalkyl vinyl ether copolymer (P
FA), using tetrafluoroethylene-hexapropropropylene copolymer (FEP), tetrafluoroethylene-ethylene copolymer (ETFE), polychlorotrifluoroethylene resin (PCTFE), polyvinyl fluoride resin (PVF), etc. And among them, PT
FE, PFA, FEP, and ETFE are desirable, and PTFE having the lowest friction coefficient (dynamic friction coefficient 0.1
0) is particularly desirable.
【００４３】また、本発明の効果を妨げない範囲で、各
種充填材を配合しても良い。充填材としては、ガラス繊
維、炭素繊維、アラミド繊維、チタン酸カリウムウィス
カ、ウォラストナイト、ホウ酸アルミニウムウィスカ、
硫酸カルシウムウィスカ等の補強材や、二硫化モリブデ
ン、グラファイト、カーボン、炭酸カルシウム、タル
ク、マイカ、カオリン、酸化鉄、ガラスビーズ、リン酸
化合物などの無機粉末、ポリイミド樹脂、芳香族ポリエ
ステル樹脂、ポリエーテルケトン樹脂、ポリフェニレン
サルファイド樹脂、シリコーン樹脂などの樹脂粉末、シ
リコーンオイル、フッ素オイル、ワックス、ステアリン
酸化合物などの内部滑材など種々の充填材を例示するこ
とができる。Further, various fillers may be blended within a range that does not impair the effects of the present invention. Fillers include glass fiber, carbon fiber, aramid fiber, potassium titanate whisker, wollastonite, aluminum borate whisker,
Reinforcing material such as calcium sulfate whisker, inorganic powder such as molybdenum disulfide, graphite, carbon, calcium carbonate, talc, mica, kaolin, iron oxide, glass beads, phosphate compound, polyimide resin, aromatic polyester resin, polyether Various fillers such as resin powder such as ketone resin, polyphenylene sulfide resin, and silicone resin, and internal lubricant such as silicone oil, fluorine oil, wax, and stearic acid compound can be exemplified.
【００４４】あるいは、図１０〜図１２に示す構成の等
速自在継手において、外輪１と軸部４とを除く少なくと
も一の構成部材（内輪２、ボタン部材３）を上記のよう
な樹脂材料で形成することもできる。継手の軽量化、コ
ストダウン、摺動抵抗の低減、振動のより一層の低減を
図ることができると同時に、樹脂材料の弾性を利用し
て、内輪２とボタン部材３との間、ボタン部材３と外輪
１との間に負隙間を与えることができ、また、各構成部
材の製作公差を広げることができるので、安価で円周方
向のガタツキのない等速自在継手を提供することができ
る。Alternatively, in the constant velocity universal joint having the structure shown in FIGS. 10 to 12, at least one of the constituent members (the inner ring 2 and the button member 3) except the outer ring 1 and the shaft portion 4 is made of the above resin material. It can also be formed. The weight of the joint can be reduced, the cost can be reduced, the sliding resistance can be further reduced, and the vibration can be further reduced. At the same time, the elasticity of the resin material can be used to make the space between the inner ring 2 and the button member 3 and the button member 3. Since a negative gap can be provided between the outer ring 1 and the outer ring 1, and the manufacturing tolerance of each component can be widened, it is possible to provide an inexpensive constant velocity universal joint without rattling in the circumferential direction.
【００４５】尚、以上に説明した種々の形態は、図１３
に示すような、ボタン部材を有しない等速自在継手にも
同様に適用することができる｛同図に示す構成の詳細に
ついては、本出願人による特願平３−３４４２９２号
（特開平５−１７２１５２号）ご参照｝。The various forms described above are shown in FIG.
The present invention can be similarly applied to a constant velocity universal joint having no button member as shown in FIG. {For details of the configuration shown in the figure, refer to Japanese Patent Application No. 3-344292 filed by the present applicant. 172152) reference}.
【００４６】[0046]
【発明の効果】以上説明したように、本発明によれば、
高作動角、小型・軽量、低コスト、組立性に優れ、回転
バックラッシュのないを等速自在継手を提供することが
できる。As described above, according to the present invention,
It is possible to provide a constant velocity universal joint with a high operating angle, small size / light weight, low cost, excellent assembling property, and no rotation backlash.
【図１】本発明の第１の実施形態を示す一部横断面図
（図ａ）、縦断面図（図ｂ）である。FIG. 1 is a partial cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B) showing a first embodiment of the present invention.
【図２】図１における主要構成部材を示す図である。FIG. 2 is a diagram showing main constituent members in FIG.
【図３】本発明の第２の実施形態を示す一部横断面図
（図ａ）、縦断面図（図ｂ）である。FIG. 3 is a partial transverse sectional view (FIG. A) and a longitudinal sectional view (FIG. B) showing a second embodiment of the present invention.
【図４】図３における主要構成部材を示す図である。FIG. 4 is a diagram showing main constituent members in FIG.
【図５】本発明の第３の実施形態を示す一部横断面図
（図ａ）、縦断面図（図ｂ）である。FIG. 5 is a partial cross-sectional view (FIG. A) and a vertical cross-sectional view (FIG. B) showing a third embodiment of the present invention.
【図６】図５における主要構成部材を示す図である。FIG. 6 is a diagram showing main constituent members in FIG. 5;
【図７】本発明の第４の実施形態を示す一部横断面図
（図ａ）、縦断面図（図ｂ）である。FIG. 7 is a partial transverse sectional view (FIG. A) and a longitudinal sectional view (FIG. B) showing a fourth embodiment of the present invention.
【図８】図７における主要構成部材を示す図である。FIG. 8 is a view showing main constituent members in FIG. 7.
【図９】本発明の第５の実施形態を示す縦断面図であ
る。FIG. 9 is a vertical cross-sectional view showing a fifth embodiment of the present invention.
【図１０】従来構成を示す一部縦断面図である。FIG. 10 is a partial vertical cross-sectional view showing a conventional configuration.
【図１１】図１０に示す従来継手の分解斜視図である。11 is an exploded perspective view of the conventional joint shown in FIG.
【図１２】図１０に示す従来継手の一部横断面図であ
る。12 is a partial cross-sectional view of the conventional joint shown in FIG.
【図１３】従来構成を示す一部横断面図（図ａ）、縦断
面図（図ｂ）である。FIG. 13 is a partial transverse sectional view (FIG. A) and a longitudinal sectional view (FIG. B) showing a conventional configuration.
１ 外輪 １ａ 平坦面 ２ 内輪 ２ａ 球面状外壁面 ２ｂ 内壁面 ３ ボタン部材 ４ 軸部 ４ｂ 外壁面 ５、５’ くさび部材 ６ コイルスプリング 1 outer ring 1a flat surface 2 inner ring 2a spherical outer wall surface 2b inner wall surface 3 button member 4 shaft portion 4b outer wall surface 5 5'wedge member 6 coil spring
Claims (4)
多角形状の中空穴を有する外輪と、外輪の中空穴に組み
込まれ、外輪の平坦面に接触し又は外輪の平坦面との間
に介装されたボタン部材に接触する球面状外壁面を有す
る内輪と、内輪の内壁面に組み込まれる外壁面を有する
軸部とを備えた等速自在継手において、 前記内輪を複数の分割体で構成すると共に、前記内輪の
内壁面と、前記軸部の外壁面と、両者の間に介装したく
さび部材とによってくさびを形成し、前記くさび部材を
弾性手段で前記くさびの作用する方向に押圧することに
より、前記内輪を外輪の平坦面側に押圧したことを特徴
とする等速自在継手。1. An outer ring having a regular polygonal hollow hole surrounded by a plurality of flat surfaces parallel to an axis, and an outer ring which is incorporated in the hollow hole of the outer ring and contacts the flat surface of the outer ring or the flat surface of the outer ring. A constant velocity universal joint including an inner ring having a spherical outer wall surface that comes into contact with a button member interposed between the inner ring and a shaft portion having an outer wall surface incorporated into the inner wall surface of the inner ring, wherein the inner ring is divided into a plurality of split bodies. A wedge is formed by the inner wall surface of the inner ring, the outer wall surface of the shaft portion, and a wedge member interposed therebetween, and the wedge member is formed by elastic means in the direction in which the wedge acts. A constant velocity universal joint characterized in that the inner ring is pressed against the flat surface side of the outer ring by pressing.
多角形状の中空穴を有する外輪と、外輪の中空穴に組み
込まれ、外輪の平坦面に接触し又は外輪の平坦面との間
に介装されたボタン部材に接触する球面状外壁面を有す
る内輪と、内輪の内壁面に組み込まれる外壁面を有する
軸部とを備えた等速自在継手において、 前記内輪を複数の分割体で構成すると共に、前記内輪の
内壁面と前記軸部の外壁面とによってくさびを形成し、
前記内輪と前記軸部とを弾性手段で前記くさびの作用す
る方向に相互に押圧することにより、前記内輪を外輪の
平坦面側に押圧したことを特徴とする等速自在継手。2. An outer ring having a regular polygonal hollow hole surrounded by a plurality of flat surfaces parallel to the axis, and an outer ring which is incorporated in the hollow hole of the outer ring and contacts the flat surface of the outer ring or the flat surface of the outer ring. A constant velocity universal joint including an inner ring having a spherical outer wall surface that comes into contact with a button member interposed between the inner ring and a shaft portion having an outer wall surface incorporated into the inner wall surface of the inner ring, wherein the inner ring is divided into a plurality of split bodies. And a wedge is formed by the inner wall surface of the inner ring and the outer wall surface of the shaft portion.
A constant velocity universal joint characterized in that the inner ring and the shaft portion are pressed against each other in the direction in which the wedge acts by elastic means to press the inner ring toward the flat surface side of the outer ring.
一の構成部材を樹脂材料で形成したことを特徴とする請
求項１又は２の等速自在継手。3. The constant velocity universal joint according to claim 1, wherein at least one constituent member excluding the outer ring and the shaft portion is formed of a resin material.
多角形状の中空穴を有する外輪と、外輪の中空穴に組み
込まれ、外輪の平坦面に接触し又は外輪の平坦面との間
に介装されたボタン部材に接触する球面状外壁面を有す
る内輪と、内輪に連結される軸部とを備えた等速自在継
手において、 前記外輪と前記軸部とを除く少なくとも一の構成部材を
樹脂材料で形成したことを特徴とする等速自在継手。4. An outer ring having a regular polygonal hollow hole surrounded by a plurality of flat surfaces parallel to the axis, and an outer ring which is incorporated in the hollow hole of the outer ring and contacts the flat surface of the outer ring or the flat surface of the outer ring. A constant velocity universal joint including an inner ring having a spherical outer wall surface that contacts a button member interposed between the inner ring and a shaft portion connected to the inner ring, and at least one configuration excluding the outer ring and the shaft portion. A constant velocity universal joint characterized in that the member is made of a resin material.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33937895A JPH09177809A (en) | 1995-12-26 | 1995-12-26 | Constant velocity universal joint |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP33937895A JPH09177809A (en) | 1995-12-26 | 1995-12-26 | Constant velocity universal joint |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09177809A true JPH09177809A (en) | 1997-07-11 |
Family
ID=18326906
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP33937895A Withdrawn JPH09177809A (en) | 1995-12-26 | 1995-12-26 | Constant velocity universal joint |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09177809A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000055518A1 (en) * | 1999-03-12 | 2000-09-21 | Ntn Corporation | Constant velocity universal joint |
-
1995
- 1995-12-26 JP JP33937895A patent/JPH09177809A/en not_active Withdrawn
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2000055518A1 (en) * | 1999-03-12 | 2000-09-21 | Ntn Corporation | Constant velocity universal joint |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20030304 |