JP2023088013A - Sprocket fixing structure - Google Patents

Sprocket fixing structure Download PDF

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JP2023088013A
JP2023088013A JP2021202625A JP2021202625A JP2023088013A JP 2023088013 A JP2023088013 A JP 2023088013A JP 2021202625 A JP2021202625 A JP 2021202625A JP 2021202625 A JP2021202625 A JP 2021202625A JP 2023088013 A JP2023088013 A JP 2023088013A
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spacing member
ring
spacer
inner ring
contact
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JP7033817B1 (en
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惠嗣 片山
Keishi Katayama
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KATAYAMA CHAIN KK
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  • Mounting Of Bearings Or Others (AREA)
  • Rolling Contact Bearings (AREA)
  • Gears, Cams (AREA)

Abstract

To prevent assembly failure of a rolling bearing into an inner periphery of a boss part of a sprocket.SOLUTION: A sprocket includes: a cylindrical boss part 11; a teeth part 12 erected from the boss part 11; and a protruding part 13 protruding at an inner periphery of the boss part 11. Rolling bearings 40 are disposed at both axial sides sandwiching the protruding part 13. Each rolling bearing 40 comprises: an inner ring 41 and an outer ring 42; and rolling elements 43 disposed between the inner ring 41 and the outer ring 42. Inner end surfaces 42a, 42a of the outer rings 42, 42 contact with side surfaces 13a, 13a of the protruding part 13 and inner end surfaces 41a, 41a of the inner rings 41, 41 contact with positioning side surfaces 25, 25 provided at a spacing member 20, which is arranged facing an inner diameter side of the protruding part 13, and oriented in an axial direction.SELECTED DRAWING: Figure 1

Description

この発明は、スプロケットの固定構造に関するものである。 The present invention relates to a sprocket fixing structure.

チェーンが巻回されるスプロケットの軸への固定構造として、軸に対してスプロケットを相対回転可能に支持するものがある。この構造に用いられるスプロケットはアイドラースプロケットとも呼ばれ、スプロケットのボス部の内面に沿って転がり軸受を備えたものが一般的である。軸に対して相対回転可能に支持されるスプロケットとして、例えば、特許文献１に記載されたものがある。特許文献１のスプロケットは、スプロケットの厚さ方向に沿って、転がり軸受を２つ並列して備えている。 As a structure for fixing a sprocket around which a chain is wound to a shaft, there is a structure that supports the sprocket so as to be relatively rotatable with respect to the shaft. The sprocket used in this structure is also called an idler sprocket, and generally has rolling bearings along the inner surface of the boss portion of the sprocket. A sprocket that is supported so as to be relatively rotatable with respect to a shaft is disclosed, for example, in Patent Document 1. The sprocket of Patent Document 1 has two rolling bearings arranged side by side along the thickness direction of the sprocket.

また、転がり軸受を２つ並列して備えたスプロケットとして、例えば、図９に示すものがある。このスプロケット３０は、円筒状のボス部３１と、そのボス部３１から立ち上がる歯部３２と、ボス部３１の内周に突出する凸部３３とを備え、その凸部３３を挟んで軸方向両側に転がり軸受４０，４０が配置されている。転がり軸受４０は、内輪４１及び外輪４２と、その内輪４１と外輪４２との間に配置される転動体４３とで構成されている。凸部３３の介在により、並列する２つの転がり軸受４０，４０は、軸方向に沿って距離を隔てた場所に位置決めされている。 A sprocket having two rolling bearings arranged in parallel is shown in FIG. 9, for example. The sprocket 30 includes a cylindrical boss portion 31, a tooth portion 32 rising from the boss portion 31, and a convex portion 33 projecting to the inner periphery of the boss portion 31. Rolling bearings 40, 40 are arranged in . The rolling bearing 40 includes an inner ring 41 , an outer ring 42 , and rolling elements 43 arranged between the inner ring 41 and the outer ring 42 . The two rolling bearings 40, 40 arranged side by side are positioned apart from each other along the axial direction by the interposition of the convex portion 33. As shown in FIG.

特開２００３－２８２４７号公報Japanese Patent Application Laid-Open No. 2003-28247

図９に示すスプロケット３０では、例えば、ボス部３１の内周やボス部３１に挿通される軸の外周に、転がり軸受４０を抜け止めする止め輪を用いる場合がある。また、例えば、図１０に示すように、ボス部３１に挿通される軸１に対してナット２を矢印Ｘ，Ｙ方向に締め付けて、軸１とスプロケット３０を固定する場合もある。 In the sprocket 30 shown in FIG. 9, for example, a snap ring may be used on the inner periphery of the boss portion 31 and the outer periphery of the shaft inserted through the boss portion 31 to prevent the rolling bearing 40 from coming off. Alternatively, for example, as shown in FIG. 10, the shaft 1 and the sprocket 30 may be fixed by tightening the nut 2 in the directions of the arrows X and Y on the shaft 1 inserted through the boss portion 31 .

ナット２の締め付けにより軸１とスプロケット３０を固定すると、転がり軸受４０から内輪４１や転動体４３が脱落してしまう場合がある。これは、例えば、図１０に示すように、外輪４２の奥端面４２ａが凸部３３に当接しているにもかかわらず、さらに内輪４１を軸方向へ押圧してしまうことで生じやすい。図１０の符号ｗは、内輪４１が適切な位置よりも過度に押込まれて、組み込み不良が生じていることを示している。 When the shaft 1 and the sprocket 30 are fixed by tightening the nut 2 , the inner ring 41 and the rolling elements 43 may drop off from the rolling bearing 40 . For example, as shown in FIG. 10, this tends to occur when the inner ring 41 is pushed further in the axial direction even though the rear end surface 42a of the outer ring 42 is in contact with the protrusion 33 . A symbol w in FIG. 10 indicates that the inner ring 41 is excessively pushed in from an appropriate position, resulting in an assembly failure.

そこで、この発明の課題は、転がり軸受の組み込み不良を防ぐことである。 SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to prevent a rolling bearing assembly failure.

上記の課題を解決するために、この発明は、円筒状のボス部と、前記ボス部から立ち上がる歯部と、前記ボス部の内周に突出する凸部とを備え、前記凸部を挟んで軸方向両側にそれぞれ転がり軸受が配置され、前記転がり軸受は、内輪及び外輪と、前記内輪と前記外輪との間に配置される転動体とで構成され、前記外輪の内方端面は、それぞれ前記凸部の側面に当接し、前記内輪の内方端面は、前記凸部の内径側に対向して配置した間隔保持部材に設けられた軸方向へ向く位置決め側面に当接しているスプロケットを採用した。 In order to solve the above problems, the present invention includes a cylindrical boss portion, a tooth portion rising from the boss portion, and a convex portion protruding toward the inner circumference of the boss portion, and a toothed structure having the convex portion sandwiched therebetween. Rolling bearings are arranged on both sides in the axial direction. The rolling bearings are composed of an inner ring, an outer ring, and rolling elements arranged between the inner ring and the outer ring. A sprocket is employed in which the inner end surface of the inner ring abuts on the axially oriented positioning side surface provided on the spacing member arranged to face the inner diameter side of the protrusion. .

ここで、前記間隔保持部材は、対向する前記内輪の内方端面間に配置される間隔材であり、前記位置決め側面は前記間隔材に設けられている構成を採用できる。 Here, it is possible to employ a configuration in which the spacing member is a spacing member arranged between the inner end faces of the inner rings facing each other, and the positioning side surface is provided on the spacing member.

また、前記間隔材は、それに対向する前記凸部の頂面又は前記凸部の内径側に配置したスペーサ部の内径面によって、前記ボス部に対して半径方向への移動が規制されている構成を採用できる。 Further, the spacing member is restricted from moving in the radial direction with respect to the boss portion by the top surface of the convex portion facing it or the inner diameter surface of the spacer portion arranged on the inner diameter side of the convex portion. can be adopted.

さらに、前記間隔材の内径面と前記位置決め側面との間の稜線部に面取り部を備え、前記面取り部の半径方向への設定高さは、前記間隔材の外径面とそれに対向する前記凸部の頂面との間の半径差、又は、前記間隔材の外径面とそれに対向する前記スペーサ部の内径面との半径差よりも大きく設定されている構成を採用できる。 Further, a chamfered portion is provided on a ridge between the inner diameter surface of the spacing member and the positioning side surface, and the set height of the chamfered portion in the radial direction is equal to the outer diameter surface of the spacing member and the convex surface facing it. It is possible to adopt a configuration in which the difference in radius between the top surface of the spacer portion and the difference in radius between the outer diameter surface of the spacer member and the inner diameter surface of the spacer portion opposed thereto is set larger than the difference in radius.

一方、前記間隔保持部材として、前記内輪の内面に当接する外面を有する筒状部と、前記筒状部から外径方向に突出する位置決め凸部を備え、前記位置決め側面は前記位置決め凸部に設けられている構成を採用できる。 On the other hand, the spacing member includes a cylindrical portion having an outer surface that abuts on the inner surface of the inner ring, and a positioning convex portion that protrudes radially outward from the cylindrical portion, and the positioning side surface is provided on the positioning convex portion. You can adopt the configuration that is

また、前記間隔保持部材は、前記内輪の外方端面に当接する補助端面と、前記内輪の内面に当接する補助外面を有する補助部材を前記筒状部とは別体に備え、前記筒状部の外面は、前記内輪の内面のうち内方寄りの部分にのみ当接し、前記補助外面は、前記内輪の内面のうち外方寄りの部分にのみ当接する構成を採用できる。 Further, the spacing member includes an auxiliary member, which is separate from the tubular portion and has an auxiliary end surface that abuts the outer end surface of the inner ring and an auxiliary outer surface that abuts the inner surface of the inner ring. The outer surface of the inner ring contacts only an inner portion of the inner surface of the inner ring, and the auxiliary outer surface contacts only an outer portion of the inner surface of the inner ring.

この発明は、スプロケットのボス部の内周への転がり軸受の組み込み不良を防ぐことができる。 According to the present invention, it is possible to prevent the rolling bearing from being improperly assembled to the inner circumference of the boss portion of the sprocket.

この発明の第１の実施形態を示す縦断面図1 is a vertical sectional view showing a first embodiment of the present invention; FIG. 第１の実施形態の分解斜視図Exploded perspective view of the first embodiment 第１の実施形態の比較例を示す縦断面図FIG. 3 is a longitudinal sectional view showing a comparative example of the first embodiment; 軸挿通前の状態を示す要部拡大図Enlarged view of the main part showing the state before the shaft is inserted この発明の第２の実施形態を示す縦断面図FIG. 2 is a vertical cross-sectional view showing a second embodiment of the present invention; この発明の第３の実施形態を示す縦断面図FIG. 3 is a vertical cross-sectional view showing a third embodiment of the present invention; この発明の第４の実施形態を示す縦断面図FIG. 4 is a vertical cross-sectional view showing a fourth embodiment of the present invention; 第４の実施形態の分解斜視図Exploded perspective view of the fourth embodiment この発明の第５の実施形態を示す縦断面図FIG. 5 is a vertical cross-sectional view showing a fifth embodiment of the present invention; 従来例の縦断面図Longitudinal cross-sectional view of conventional example 従来例の縦断面図Longitudinal cross-sectional view of conventional example

この発明の実施形態を図１～図８に基づいて説明する。図１～図３Ｂは第１の実施形態を、図４は第２の実施形態を、図５は第３の実施形態を、図６及び図７は第４の実施形態を、図８は第５の実施形態を示している。 An embodiment of the invention will be described with reference to FIGS. 1 to 8. FIG. 1 to 3B show the first embodiment, FIG. 4 shows the second embodiment, FIG. 5 shows the third embodiment, FIGS. 6 and 7 show the fourth embodiment, and FIG. 5 embodiment.

（第１の実施形態）
スプロケット１０は、図１に示すように、円筒状のボス部１１と、ボス部１１から立ち上がる歯部１２と、ボス部１１の内周に突出する凸部１３とを備えている。歯部１２は、外径方向へ突出する複数個の歯１２ａと谷１２ｂが周方向に沿って交互に形成され、その歯１２ａと谷１２ｂがチェーン（図示せず）と噛み合うようになっている。以下、ボス部１１の軸方向に対して、凸部１３が存在する軸方向中心位置に近づく側を内方又は内方側と称し、軸方向中心位置から遠ざかる側を外方又は外方側と称する。 (First embodiment)
As shown in FIG. 1 , the sprocket 10 includes a cylindrical boss portion 11 , tooth portions 12 rising from the boss portion 11 , and convex portions 13 protruding from the inner circumference of the boss portion 11 . The tooth portion 12 has a plurality of radially protruding teeth 12a and troughs 12b alternately formed along the circumferential direction, and the teeth 12a and troughs 12b mesh with a chain (not shown). . Hereinafter, with respect to the axial direction of the boss portion 11, the side closer to the axial center position where the convex portion 13 is present will be referred to as the inner side, and the side farther from the axial center position will be referred to as the outer side. called.

図１では、歯部１２は、ボス部１１の軸方向一方の端部から立ち上がっているが、歯部１２の立ち上がり位置は仕様に応じて自由に設定でき、例えば、ボス部１１の軸方向中ほどで歯部１２が立ち上がっている態様も考えられる。また、図１では、凸部１３の幅方向中心は、ボス部１１の軸方向中心と一致しているが、この突出位置が、軸方向中心の位置から軸方向に沿っていずれかの側へ偏心している態様も考えられる。 1, the tooth portion 12 rises from one axial end of the boss portion 11, but the rising position of the tooth portion 12 can be freely set according to specifications. A mode in which the tooth portion 12 stands up at about 10 mm is also conceivable. In FIG. 1, the center of the projection 13 in the width direction coincides with the center of the boss 11 in the axial direction. An eccentric mode is also conceivable.

ボス部１１の内周には、凸部１３を挟んで軸方向両側にそれぞれ転がり軸受４０が配置されている。転がり軸受４０は、内輪４１及び外輪４２と、内輪４１と外輪４２との間に配置される転動体４３とで構成されている。転動体４３は、内輪４１及び外輪４２にそれぞれ設けられた凹状の軌道溝に収容されて、内輪４１と外輪４２とを軸回り相対回転可能としている。また、転動体４３を保持するため、内輪４１と外輪４２との間に保持器等が配置されている。なお、この実施形態の転がり軸受４０は、転動体４３としてボールを使用した玉軸受を採用しているが、コロ等の他の形式の転動体４３を用いた転がり軸受４０を採用してもよい。転がり軸受４０は、外輪４２，４２の外面４５がボス部１１の内周１１ａに摺動しながら、そのボス部１１内に圧入される。 Rolling bearings 40 are arranged on the inner periphery of the boss portion 11 on both sides in the axial direction with the convex portion 13 interposed therebetween. The rolling bearing 40 includes an inner ring 41 , an outer ring 42 , and rolling elements 43 arranged between the inner ring 41 and the outer ring 42 . The rolling elements 43 are accommodated in concave raceway grooves provided in the inner ring 41 and the outer ring 42, respectively, so that the inner ring 41 and the outer ring 42 can rotate relative to each other. A cage or the like is arranged between the inner ring 41 and the outer ring 42 to hold the rolling elements 43 . Although the rolling bearing 40 of this embodiment employs a ball bearing using balls as the rolling elements 43, the rolling bearing 40 using other types of rolling elements 43 such as rollers may be employed. . The rolling bearing 40 is press-fitted into the boss portion 11 while the outer surfaces 45 of the outer rings 42 , 42 slide on the inner circumference 11 a of the boss portion 11 .

それぞれの転がり軸受４０，４０において、外輪４２，４２の軸方向内側へ向く端面（外輪の内方端面と称する）４２ａ，４２ａは、それぞれ凸部１３の側面１３ａ，１３ａに当接している。外輪４２，４２の内方端面４２ａ，４２ａ及び凸部１３の側面１３ａ，１３ａの面方向は軸直交方向であり、両者は互いに面接触している。なお、この実施形態では、凸部１３は、その側面１３ａ，１３ａが内方端面４２ａ，４２ａの一部に面接触し得る突出高さとしているが、これを内方端面４２ａ，４２ａの全域に面接触し得る突出高さとしていてもよい。なお、外輪４２の軸方向外側へ向く端面（外輪の外方端面と称する）４２ｂ，４２ｂは、それぞれボス部１１の軸方向両側の端面１４，１４と面一である。 In the respective rolling bearings 40, 40, end surfaces 42a, 42a facing inward in the axial direction of the outer rings 42, 42 are in contact with side surfaces 13a, 13a of the convex portion 13, respectively. The plane directions of the inner end faces 42a, 42a of the outer rings 42, 42 and the side faces 13a, 13a of the convex portion 13 are perpendicular to the axis, and they are in surface contact with each other. In this embodiment, the projection 13 has a projection height that allows the side surfaces 13a, 13a to come into surface contact with a part of the inner end surfaces 42a, 42a. The projection height may be such that surface contact is possible. End faces 42b, 42b facing axially outward of the outer ring 42 (referred to as outer end faces of the outer ring) are flush with the end faces 14, 14 on both axial sides of the boss portion 11, respectively.

内輪４１，４１の軸方向内側に向く端面（内輪の内方端面と称する）４１ａ，４１ａは、凸部１３の内径側に対向して配置した間隔保持部材２０に設けられた軸方向外側に向く側面（位置決め側面と称する）２５，２５に当接している。内輪４１，４１の内方端面４１ａ，４１ａ及び間隔保持部材２０の位置決め側面２５，２５の面方向は軸直交方向であり、両者は互いに面接触している。なお、この実施形態では、位置決め側面２５は、内輪４１の内方端面４１ａ，４１ａの一部に面接触し得る突出高さとしているが、これを内方端面４１ａ，４１ａの全域に面接触し得る突出高さとしていてもよい。 End faces 41a, 41a facing inward in the axial direction of the inner rings 41, 41 (referred to as inner end faces of the inner rings) face outward in the axial direction provided on the spacing member 20 disposed facing the inner diameter side of the convex portion 13. It abuts on side surfaces (referred to as positioning side surfaces) 25 , 25 . The inner end surfaces 41a, 41a of the inner rings 41, 41 and the positioning side surfaces 25, 25 of the spacing member 20 are perpendicular to the axis, and are in surface contact with each other. In this embodiment, the positioning side surface 25 has a protruding height that allows surface contact with a part of the inner end surfaces 41a, 41a of the inner ring 41. You may set it as the protrusion height to obtain.

ここで、第１の実施形態では、間隔保持部材２０として、環状の部材からなる間隔材２３’を採用している。間隔材２３’は、対向する内輪４１，４１の内方端面４１ａ，４１ａ間に配置され、その軸方向両側の側面が位置決め側面２５となっている。また、間隔材２３’の内周は、フレーム等に固定された軸が挿通される軸穴部２４となっている。軸穴部２４は、軸１の断面に対応するように、間隔材２３’の軸心に沿って断面円形に形成されている。 Here, in the first embodiment, as the spacing member 20, a spacing member 23' made of an annular member is employed. The spacing member 23 ′ is arranged between the inner end surfaces 41 a of the inner rings 41 , 41 facing each other, and the side surfaces on both sides in the axial direction serve as the positioning side surfaces 25 . Further, the inner circumference of the spacing member 23' serves as a shaft hole portion 24 through which a shaft fixed to a frame or the like is inserted. The shaft hole portion 24 is formed to have a circular cross section along the axis of the spacing member 23 ′ so as to correspond to the cross section of the shaft 1 .

間隔材２３’の外径側にスペーサ部３１を配置している。スペーサ部３１は、環状の部材である。スペーサ部３１の外径面３１ｂは、ボス部１１の凸部１３の頂面（内径面）１３ｂに当接している。これにより、スペーサ部３１は、ボス部１１に対して半径方向への移動が規制されている。また、スぺーサ部３１の軸心がボス部１１の軸心に合致した状態（以下、軸心合致状態と称する）で、スペーサ部３１の内径面３１ａと間隔材２３’の外径面２３ａとの間に、図１に示すように全周に亘って僅かな隙間ｔが生じるように、スペーサ部３１の内径面３１ａ及び間隔材２３’の外径面２３ａの直径が設定されている。これにより、間隔材２３’は、ボス部１１及びスペーサ部３１に対して半径方向への一定以上の移動が規制されている。また、軸１を挿通した状態で、スペーサ部３１と間隔材２３’とが接触しないことで、内輪４１と外輪４２との円滑な相対回転を阻害しないようになっている。 A spacer portion 31 is arranged on the outer diameter side of the spacing member 23'. The spacer portion 31 is an annular member. An outer diameter surface 31 b of the spacer portion 31 is in contact with a top surface (inner diameter surface) 13 b of the projection 13 of the boss portion 11 . Thereby, the spacer portion 31 is restricted from moving in the radial direction with respect to the boss portion 11 . In addition, in a state in which the axis of the spacer portion 31 coincides with the axis of the boss portion 11 (hereinafter referred to as an axis-aligned state), the inner diameter surface 31a of the spacer portion 31 and the outer diameter surface 23a of the spacing member 23' are aligned. The diameters of the inner diameter surface 31a of the spacer portion 31 and the outer diameter surface 23a of the spacing member 23' are set so that a slight gap t is formed over the entire circumference as shown in FIG. As a result, the spacing member 23 ′ is restricted from moving radially beyond a certain amount with respect to the boss portion 11 and the spacer portion 31 . Further, since the spacer portion 31 and the spacing member 23' do not contact each other when the shaft 1 is inserted, smooth relative rotation between the inner ring 41 and the outer ring 42 is not hindered.

また、スペーサ部３１の軸方向両側の側面には、それぞれ切欠き３１ｃが設けられているので、スペーサ部３１と内輪４１とは接触しないようになっている。図３Ｂでは、両側の切欠き３１ｃ間の距離ｗと、間隔材２３’の内輪４１との接触部分における最大幅ｇとの関係において、ｗ＜ｇとなっている。 In addition, notches 31c are provided on both sides of the spacer portion 31 in the axial direction, so that the spacer portion 31 and the inner ring 41 do not come into contact with each other. In FIG. 3B, the relationship between the distance w between the notches 31c on both sides and the maximum width g of the contact portion of the spacer 23' with the inner ring 41 satisfies w<g.

なお、スペーサ部３１を用いない態様を採用することも可能である。しかし、この場合、例えば、図３Ａに示すように、間隔保持部材２０としての間隔材２３’が、ボス部１１の軸心からずれてしまう場合がある。このようなずれが生じると、軸１を挿通する際に間隔材２３’の位置を調整する必要が生じる。このため、ずれ止め用のスペーサ部３１の活用が好ましい。 In addition, it is also possible to employ a mode in which the spacer portion 31 is not used. However, in this case, for example, as shown in FIG. 3A, the spacing member 23 ′ as the spacing member 20 may be displaced from the axial center of the boss portion 11 . If such a deviation occurs, it becomes necessary to adjust the position of the spacer 23' when the shaft 1 is inserted. Therefore, it is preferable to utilize the spacer portion 31 for anti-slippage.

この実施形態のスプロケット１０を組み立てる際には、ボス１１内にスペーサ部３１及び間隔材２３’を挿し入れつつ、内輪４１、外輪４２、及び、転動体４３が組み付けられた転がり軸受４０を軸方向両側からボス部１１内に軽く圧入する。軸１を挿通してナット２を締め付けることにより、やがて外輪４２，４２の内方端面４２ａ，４２ａが、凸部１３の側面１３ａ、１３ａに当接する。このとき、同時に、内輪４１，４１の内方端面４１ａ，４１ａと、間隔材２３’の位置決め側面２５，２５も当接する。このため、転がり軸受４０の内輪４１が過度に押し込まれることがない。したがって、組み込み不良が生じることはない。 When assembling the sprocket 10 of this embodiment, while inserting the spacer portion 31 and the spacing member 23' into the boss 11, the rolling bearing 40 having the inner ring 41, the outer ring 42, and the rolling elements 43 assembled therein is axially moved. It is lightly press-fitted into the boss portion 11 from both sides. By inserting the shaft 1 and tightening the nut 2 , the inner end surfaces 42 a and 42 a of the outer rings 42 and 42 come into contact with the side surfaces 13 a and 13 a of the projection 13 . At this time, the inner end surfaces 41a, 41a of the inner rings 41, 41 and the positioning side surfaces 25, 25 of the spacer 23' are also brought into contact at the same time. Therefore, the inner ring 41 of the rolling bearing 40 is not pushed excessively. Therefore, assembly defects do not occur.

ここで、軸１を挿通する前の状態では、図３Ｂに示すように、間隔材２３’は重力によって下方へ落下するので、その位置は軸心合致状態よりも僅かに下方へ偏心している（以下、軸心偏心状態と称する）。間隔材２３’とスペーサ部３１の内径面３１ａとの間に全周に亘って隙間ｔが設定されているからである。図３Ｂでは、間隔材２３’の下方の隙間を０（ゼロ）、上方の隙間をｔ×２＝２tで図示している。 Here, before the shaft 1 is inserted, as shown in FIG. 3B, the spacing member 23' drops downward due to gravity, so its position is slightly eccentric below the axially aligned state ( hereinafter referred to as the axial eccentric state). This is because the gap t is set over the entire circumference between the spacing member 23 ′ and the inner diameter surface 31 a of the spacer portion 31 . In FIG. 3B, the gap below the spacer 23' is shown as 0 (zero), and the gap above it is shown as t*2=2t.

この実施形態では、間隔材２３’の内径面２３ｄ（軸穴部２４の内面）と位置決め側面２５，２５との間の稜線部に、面取り部２３ｅを備えている。面取り部２３ｅは、図３Ｂに示すように、軸方向への設定幅をｃ１、半径方向への設定高さをｃ２としている（通常はｃ１＝ｃ２）。面取り部２３ｅの半径方向への設定高さｃ２は、間隔材２３’の外径面２３ａとそれに対向するスペーサ部３１の内径面３１ａとの半径差ｔよりも大きく設定されている。このため、軸心偏心状態では、間隔材２３’の上方側で内輪４１の内面４４の延長線上に面取り部２３ｅが位置している。すなわち、面取り部２３ｅは、内輪４１の内面４４よりも内径側へ突出した状態となっている。このため、軸１の挿通時に、その軸１の先端が面取り部２３ｅに当たることによって、間隔材２３’がスムーズに軸心合致状態に修正される。すなわち、ｃ２＞ｔであることが望ましい。 In this embodiment, a chamfered portion 23e is provided on the ridge between the inner diameter surface 23d (the inner surface of the shaft hole portion 24) of the spacing member 23' and the positioning side surfaces 25,25. As shown in FIG. 3B, the chamfered portion 23e has a set width c1 in the axial direction and a set height c2 in the radial direction (usually c1=c2). The set height c2 of the chamfered portion 23e in the radial direction is set to be larger than the radial difference t between the outer diameter surface 23a of the spacing member 23' and the inner diameter surface 31a of the spacer portion 31 facing thereto. Therefore, in the axially eccentric state, the chamfered portion 23e is positioned on the extension line of the inner surface 44 of the inner ring 41 on the upper side of the spacer 23'. That is, the chamfered portion 23e protrudes from the inner surface 44 of the inner ring 41 toward the inner diameter side. Therefore, when the shaft 1 is inserted, the front end of the shaft 1 abuts against the chamfered portion 23e, so that the spacing member 23' is smoothly aligned with the shaft center. That is, it is desirable that c2>t.

なお、面取り部２３ｅは、実施形態のようなＣ面（部材の角を斜めに落とす加工）であってもよいし、稜線部を滑らかにした円弧状のアール面であってもよい。面取り部２３ｅとは、部材の角を滑らかにしたものを意味し、このようなＣ面やアール面等を含む概念である。 The chamfered portion 23e may be a chamfered surface (processing for obliquely cutting the corners of the member) as in the embodiment, or may be an arc-shaped rounded surface with smooth ridges. The chamfered portion 23e means a member whose corners are smoothed, and is a concept including such a chamfered surface, rounded surface, and the like.

また、図３Ｂにおいて、符号ｅ１は、スペーサ部３１の外輪４２への当接部の径方向厚さを、符号ｅ２は、間隔材２３’の径方向厚さを示している。外輪４２の径方向への肉厚をｄ１、内輪４１の径方向への肉厚をｄ２とすると、ｄ１＞ｅ１、ｄ２＞ｅ２であることが望ましい。 In FIG. 3B, symbol e1 denotes the radial thickness of the contact portion of the spacer portion 31 with the outer ring 42, and symbol e2 denotes the radial thickness of the spacer 23'. Assuming that the radial thickness of the outer ring 42 is d1 and the radial thickness of the inner ring 41 is d2, it is desirable that d1>e1 and d2>e2.

（第２の実施形態）
この発明の第２の実施形態を、図４に基いて説明する。スプロケット１０の主たる構成は前述の実施形態と同様であるので、以下、その差異点を中心に説明する。この実施形態では、第１の実施形態におけるスペーサ部３１を、ボス部１１の凸部１３と一体化したものである。すなわち、前述の実施形態のスペーサ部３１に相当する分だけ凸部１３を内径方向へ延長してその突出高さを高くしている。凸部１３の延長部の頂面１３ｂと間隔材２３’の外径面２３ａとの間には、全周に亘って僅かな隙間ｔが生じるように、凸部１３の頂面１３ｂ及び間隔材２３’の外径面２３ａの直径が設定されている。これにより、間隔材２３’は、ボス部１１に対して半径方向への一定以上の移動が規制されている。また、軸１を挿通した状態で、凸部１３と間隔材２３’とが接触しないことで、内輪４１と外輪４２との円滑な相対回転を阻害しないようになっている。また、凸部１３の軸方向両側の側面には、それぞれ切欠き１３ｃが設けられているので、凸部１３と内輪４１とは接触しないようになっている。 (Second embodiment)
A second embodiment of the invention will be described with reference to FIG. Since the main configuration of the sprocket 10 is the same as that of the above-described embodiment, the differences will be mainly described below. In this embodiment, the spacer portion 31 in the first embodiment is integrated with the convex portion 13 of the boss portion 11 . That is, the protruding portion 13 is extended in the inner diameter direction by an amount corresponding to the spacer portion 31 of the above-described embodiment to increase the protruding height. The top surface 13b of the projection 13 and the spacer 23' are arranged such that a slight gap t is formed over the entire circumference between the top surface 13b of the extension of the projection 13 and the outer diameter surface 23a of the spacer 23'. The diameter of the outer diameter surface 23a of 23' is set. As a result, the spacing member 23 ′ is restricted from moving in the radial direction with respect to the boss portion 11 over a certain amount. In addition, when the shaft 1 is inserted, the convex portion 13 and the spacing member 23' do not come into contact with each other, so that smooth relative rotation between the inner ring 41 and the outer ring 42 is not hindered. Moreover, since the notch 13c is provided in the side surface of the axial direction both sides of the convex part 13, respectively, the convex part 13 and the inner ring|wheel 41 are prevented from contacting.

この第２の実施形態では、間隔材２３’の面取り部２３ｅの半径方向への設定高さｃ２は、間隔材２３’の外径面２３ａとそれに対向する凸部１３の頂面１３ｂとの間の半径差ｔよりも大きく設定されている（図４に面取り部２３ｅの寸法ｃ２等は図示せず）。このため、前述の実施形態と同じく、軸心偏心状態では、間隔材２３’の上方側で内輪４１の内面４４の延長線上に面取り部２３ｅが位置している。このため、軸１の挿通時に、その軸１の先端が面取り部２３ｅに当たることによって、間隔材２３’がスムーズに軸心合致状態に修正される点は同様である。 In this second embodiment, the set height c2 in the radial direction of the chamfered portion 23e of the spacing member 23' is between the outer diameter surface 23a of the spacing member 23' and the top surface 13b of the convex portion 13 facing thereto. (the dimension c2 of the chamfered portion 23e and the like are not shown in FIG. 4). Therefore, as in the above-described embodiment, the chamfered portion 23e is positioned on the extension line of the inner surface 44 of the inner ring 41 above the spacing member 23' in the axial eccentric state. Therefore, when the shaft 1 is inserted, the front end of the shaft 1 abuts against the chamfered portion 23e, so that the spacer 23' can be smoothly adjusted to match the axial center.

（第３の実施形態）
この発明の第３の実施形態を、図５に基いて説明する。この実施形態では、第１の実施形態におけるスペーサ部３１を、間隔材２３’と一体化したものである。すなわち、間隔材２３’を、第１の実施形態のスペーサ部３１に相当する分だけ外径方向へ延長してその径方向高さを高くしている。凸部１３の頂面１３ｂと間隔材２３’の延長部の外径面２３ａとの間には、全周に亘って僅かな隙間ｔが生じるように、凸部１３の頂面１３ｂ及び間隔材２３’の外径面２３ａの直径が設定されている。これにより、間隔材２３’は、ボス部１１に対して半径方向への一定以上の移動が規制されている。また、軸１を挿通した状態で、凸部１３と間隔材２３’とが接触しないことで、内輪４１と外輪４２との円滑な相対回転を阻害しないようになっている。また、間隔材２３’の軸方向両側の側面には、それぞれ切欠き２３ｃが設けられているので、間隔材２３’と外輪４２とは接触しないようになっている。 (Third embodiment)
A third embodiment of the invention will be described with reference to FIG. In this embodiment, the spacer portion 31 in the first embodiment is integrated with the spacer 23'. That is, the spacing member 23' is extended in the outer diameter direction by an amount corresponding to the spacer portion 31 of the first embodiment to increase its radial height. Between the top surface 13b of the convex portion 13 and the outer diameter surface 23a of the extended portion of the spacer 23', the top surface 13b of the convex portion 13 and the spacer 23' are arranged so that a slight gap t is formed over the entire circumference. The diameter of the outer diameter surface 23a of 23' is set. As a result, the spacing member 23 ′ is restricted from moving in the radial direction with respect to the boss portion 11 over a certain amount. In addition, when the shaft 1 is inserted, the convex portion 13 and the spacing member 23' do not come into contact with each other, so that smooth relative rotation between the inner ring 41 and the outer ring 42 is not hindered. In addition, notches 23c are provided on both sides of the spacing member 23' in the axial direction, so that the spacing member 23' and the outer ring 42 do not come into contact with each other.

この第３の実施形態においても、間隔材２３’に設けられる面取り部２３ｅの構成については、前述の各実施形態と同様である。 Also in this third embodiment, the configuration of the chamfered portion 23e provided in the spacing member 23' is the same as in the above-described embodiments.

（第４の実施形態）
この発明の第４の実施形態を、図６及び図７に基いて説明する。この実施形態では、間隔保持部材２０として、ボス部１１の軸方向全長と同じ全長を有する筒状部２１と、筒状部２１の軸方向中ほどから外径方向に突出する位置決め凸部２３を備えている。筒状部２１は、内輪４１の内面４４に当接する外面２６を有し、位置決め側面２５は位置決め凸部２３の側面に設定されている。また、筒状部２１の内周は、フレーム等に固定された軸１が挿通される軸穴部２４といなっている。軸穴部２４は、筒状部２１の軸心に沿って断面円形に形成されている。 (Fourth embodiment)
A fourth embodiment of the invention will be described with reference to FIGS. 6 and 7. FIG. In this embodiment, as the spacing member 20, a cylindrical portion 21 having the same overall length as the boss portion 11 in the axial direction, and a positioning convex portion 23 protruding radially outward from the center of the cylindrical portion 21 in the axial direction. I have it. The cylindrical portion 21 has an outer surface 26 that contacts the inner surface 44 of the inner ring 41 , and the positioning side surface 25 is set on the side surface of the positioning convex portion 23 . Further, the inner periphery of the cylindrical portion 21 forms a shaft hole portion 24 through which the shaft 1 fixed to the frame or the like is inserted. The shaft hole portion 24 is formed to have a circular cross section along the axis of the tubular portion 21 .

このスプロケット１０を組み立てる際には、図７に示すように、歯部１２と一体のボス部１１の内周に間隔保持部材２０を差し入れる。次に、予め組付けられた転がり軸受４０を軸方向両側からボス部１１内に圧入する。このとき、外輪４２の外面４５がボス部１１の内周１１ａに摺動し、内輪４１の内面４４が筒状部２１の外面２６に摺動する。この圧入の作業は、前述の実施形態と同様に、軸１をボス部１１の内周に（間隔保持材２０の内周に）挿通するとともに、その軸１の先端の雄ネジ部にナット２を締め付けることによって行う。 When assembling this sprocket 10, as shown in FIG. Next, the pre-assembled rolling bearings 40 are press-fitted into the boss portion 11 from both sides in the axial direction. At this time, the outer surface 45 of the outer ring 42 slides on the inner circumference 11 a of the boss portion 11 , and the inner surface 44 of the inner ring 41 slides on the outer surface 26 of the cylindrical portion 21 . This press-fitting operation involves inserting the shaft 1 into the inner circumference of the boss portion 11 (into the inner circumference of the spacing member 20) and inserting the nut 2 into the male screw portion at the tip of the shaft 1, as in the previous embodiment. by tightening the

軸１の段部の端面１ａとナット２の端面２ａが内輪４１を軸方向へ押し込むことで、転がり軸受４０の圧入が行われる。ボス部１１内に転がり軸受４０が圧入されていき、やがて、外輪４２，４２の内方端面４２ａ，４２ａが凸部１３の側面１３ａ，１３ａに当接する。このとき、同時に、内輪４１，４１の内方端面４１ａ，４１ａと、位置決め凸部２３の位置決め側面２５，２５も当接する。このため、転がり軸受４０の内輪４１が過度に押し込まれることがない。したがって、組み込み不良が生じることはない。 The rolling bearing 40 is press-fitted by axially pressing the inner ring 41 with the end face 1a of the stepped portion of the shaft 1 and the end face 2a of the nut 2 . The rolling bearing 40 is press-fitted into the boss portion 11, and the inner end surfaces 42a, 42a of the outer rings 42, 42 come into contact with the side surfaces 13a, 13a of the convex portion 13 before long. At this time, the inner end surfaces 41a, 41a of the inner rings 41, 41 and the positioning side surfaces 25, 25 of the positioning protrusion 23 are also brought into contact at the same time. Therefore, the inner ring 41 of the rolling bearing 40 is not pushed excessively. Therefore, assembly defects do not occur.

（第５の実施形態）
この発明の第５の実施形態を、図８に基いて説明する。図８に示すように、間隔保持部材２０は、ボス部１１の軸方向全長よりも短い全長を有する筒状部２１と、筒状部２１の軸方向中ほどから外径方向に突出する位置決め凸部２３を備えている。筒状部２１は、内輪４１の内面４４に当接する外面２６を有し、位置決め側面２５は位置決め凸部２３の側面に設定されている。筒状部２１の外面２６は、内輪４１の内面４４のうち内方寄りの部分にのみ当接している。 (Fifth embodiment)
A fifth embodiment of the invention will be described with reference to FIG. As shown in FIG. 8, the spacing member 20 includes a tubular portion 21 having an overall length shorter than the overall length in the axial direction of the boss portion 11, and a positioning projection protruding radially outward from the middle portion of the tubular portion 21 in the axial direction. A portion 23 is provided. The cylindrical portion 21 has an outer surface 26 that contacts the inner surface 44 of the inner ring 41 , and the positioning side surface 25 is set on the side surface of the positioning convex portion 23 . The outer surface 26 of the cylindrical portion 21 is in contact only with the inner portion of the inner surface 44 of the inner ring 41 .

また、間隔保持部材２０は、筒状部２１とは別体の部材で構成された補助部材２２，２２を備えている。補助部材２２，２２は、ボス部１１に対して軸方向両側にそれぞれ配置されている。それぞれの補助部材２２，２２は、内輪４１，４１の外方端面４１ｂ，４１ｂに当接する補助端面２７，２７と、内輪４１の内面４４に当接する補助外面２８を有している。補助外面２８は、内輪４１の内面４４のうち外方寄りの部分にのみ当接している。また、筒状部２１の軸方向端面３０と補助部材２２の内方側の端面２９との間には隙間が設定されているので、筒状部２１と補助部材２２とは直接当接しないようになっている。筒状部２１の内周、及び、補助部材２２の内周は、ともにフレーム等に固定された軸が挿通される軸穴部２４である。 Further, the spacing member 20 is provided with auxiliary members 22, 22 which are separate members from the cylindrical portion 21. As shown in FIG. The auxiliary members 22 , 22 are arranged on both axial sides of the boss portion 11 . Each of the auxiliary members 22 , 22 has auxiliary end surfaces 27 , 27 that contact the outer end surfaces 41 b, 41 b of the inner rings 41 , 41 and an auxiliary outer surface 28 that contacts the inner surface 44 of the inner ring 41 . The auxiliary outer surface 28 is in contact only with the outer portion of the inner surface 44 of the inner ring 41 . Further, since a gap is set between the axial end face 30 of the tubular portion 21 and the inner end face 29 of the auxiliary member 22, the tubular portion 21 and the auxiliary member 22 are prevented from coming into direct contact with each other. It has become. The inner periphery of the tubular portion 21 and the inner periphery of the auxiliary member 22 are both shaft holes 24 through which shafts fixed to a frame or the like are inserted.

このスプロケット１０を組み立てる際には、歯部１２と一体のボス部１１の内周に筒状部２１を差し入れる。予め組み付けられた転がり軸受４０を軸方向両側からボス部１１内に圧入する。図８では、軸１やナット２の図示を省略しているが、圧入の方法は前述の各実施形態と同様である。この圧入の際、外輪４２の外面４５がボス部１１の内周１１ａに摺動し、内輪４１の内面４４が筒状部２１の外面２６に摺動する。やがて、外輪４２，４２の内方端面４２ａ，４２ａが、凸部１３の側面１３ａ、１３ａに当接する。このとき、同時に、内輪４１，４１の内方端面４１ａ，４１ａと、間隔保持部材２０の位置決め側面２５，２５も当接する。このため、転がり軸受４０の内輪４１が過度に押し込まれることがない。したがって、組み込み不良が生じることはない。最後に、補助部材２２を圧入する。内輪４１の内面４４に補助外面２８が摺動しつつ、内輪４１，４１の外方端面４１ｂ，４１ｂに補助端面２７，２７が当接した時点で補助部材２２の圧入を終了する。 When assembling this sprocket 10 , the cylindrical portion 21 is inserted into the inner periphery of the boss portion 11 integral with the tooth portion 12 . The pre-assembled rolling bearings 40 are press-fitted into the boss portion 11 from both sides in the axial direction. Although illustration of the shaft 1 and the nut 2 is omitted in FIG. 8, the press-fitting method is the same as in the above-described embodiments. During this press fitting, the outer surface 45 of the outer ring 42 slides on the inner circumference 11 a of the boss portion 11 , and the inner surface 44 of the inner ring 41 slides on the outer surface 26 of the cylindrical portion 21 . Inner end surfaces 42 a , 42 a of the outer rings 42 , 42 come into contact with the side surfaces 13 a , 13 a of the convex portion 13 before long. At this time, the inner end surfaces 41a, 41a of the inner rings 41, 41 and the positioning side surfaces 25, 25 of the spacing member 20 are also brought into contact at the same time. Therefore, the inner ring 41 of the rolling bearing 40 is not pushed excessively. Therefore, assembly defects do not occur. Finally, the auxiliary member 22 is press-fitted. When the auxiliary outer surface 28 slides on the inner surface 44 of the inner ring 41 and the auxiliary end surfaces 27, 27 contact the outer end surfaces 41b, 41b of the inner rings 41, 41b, the press-fitting of the auxiliary member 22 is completed.

１０ スプロケット
１１ ボス部
１２ 歯部
１３ 凸部
２０ 間隔保持部材
２１ 筒状部
２２ 補助部材
２３ 位置決め凸部
２３’ 間隔材
２５ 位置決め側面
２６ 外面
２７ 補助端面
２８ 補助外面
４０ 転がり軸受
４１ 内輪
４２ 外輪
４３ 転動体
４１ａ 内方端面（内輪の内方端面）
４１ｂ 外方端面（内輪の外方端面）
４２ａ 内方端面（外輪の内方端面）
４４ 内面 10 Sprocket 11 Boss portion 12 Tooth portion 13 Protruding portion 20 Spacing member 21 Cylindrical portion 22 Auxiliary member 23 Positioning protruding portion 23 ′ Spacing member 25 Positioning side surface 26 Outer surface 27 Auxiliary end surface 28 Auxiliary outer surface 40 Rolling bearing 41 Inner ring 42 Outer ring 43 Rolling Moving body 41a inner end surface (inner end surface of inner ring)
41b Outer end face (outer end face of inner ring)
42a inner end face (inner end face of outer ring)
44 inner surface

Claims (6)

円筒状のボス部（１１）と、前記ボス部（１１）から立ち上がる歯部（１２）と、前記ボス部（１１）の内周に突出する凸部（１３）とを備え、前記凸部（１３）を挟んで軸方向両側にそれぞれ転がり軸受（４０）が配置され、
前記転がり軸受（４０）は、内輪（４１）及び外輪（４２）と、前記内輪（４１）と前記外輪（４２）との間に配置される転動体（４３）とで構成され、前記外輪（４２，４２）の内方端面（４２ａ，４２ａ）は、それぞれ前記凸部（１３）の側面（１３ａ、１３ａ）に当接し、前記内輪（４１，４１）の内方端面（４１ａ，４１ａ）は、前記凸部（１３）の内径側に対向して配置した間隔保持部材（２０）に設けられた軸方向へ向く位置決め側面（２５，２５）に当接しているスプロケット。 A cylindrical boss portion (11), a tooth portion (12) rising from the boss portion (11), and a convex portion (13) projecting to the inner periphery of the boss portion (11), wherein the convex portion ( 13) are arranged on both sides in the axial direction, respectively, and
The rolling bearing (40) comprises an inner ring (41), an outer ring (42), and rolling elements (43) arranged between the inner ring (41) and the outer ring (42). The inner end faces (42a, 42a) of the inner rings (41, 41) contact the side faces (13a, 13a) of the protrusion (13), respectively, and the inner end faces (41a, 41a) of the inner rings (41, 41) , a sprocket in contact with axial positioning side surfaces (25, 25) provided on a spacing member (20) disposed facing the inner diameter side of the projection (13). 前記間隔保持部材（２０）は、対向する前記内輪（４１，４１）の内方端面（４１ａ，４１ａ）間に配置される間隔材（２３’）であり、前記位置決め側面（２５，２５）は前記間隔材（２３’）に設けられている請求項１に記載のスプロケット。 The spacing member (20) is a spacing member (23') disposed between the inner end surfaces (41a, 41a) of the inner rings (41, 41) facing each other, and the positioning side surfaces (25, 25) are A sprocket according to claim 1, provided on said spacer (23'). 前記間隔材（２３’）は、それに対向する前記凸部（１３）の頂面（１３ｂ）又は前記凸部（１３）の内径側に配置したスペーサ部（３１）の内径面（３１ａ）によって、前記ボス部（１１）に対して半径方向への移動が規制されている請求項２に記載のスプロケット。 The spacing member (23') is formed by the top surface (13b) of the convex portion (13) facing it or the inner diameter surface (31a) of the spacer portion (31) arranged on the inner diameter side of the convex portion (13). A sprocket according to claim 2, wherein radial movement is restricted with respect to said boss (11). 前記間隔材（２３’）の内径面（２３ｄ）と前記位置決め側面（２５，２５）との間の稜線部に面取り部（２３ｅ）を備え、前記面取り部（２３ｅ）の半径方向への設定高さは、前記間隔材（２３’）の外径面（２３ａ）とそれに対向する前記凸部（１３）の頂面（１３ｂ）との間の半径差、又は、前記間隔材（２３’）の外径面（２３ａ）とそれに対向する前記スペーサ部（３１）の内径面（３１ａ）との半径差よりも大きく設定されている請求項３に記載のスプロケット。 A chamfered portion (23e) is provided on a ridge between the inner diameter surface (23d) of the spacing member (23′) and the positioning side surfaces (25, 25), and the set height of the chamfered portion (23e) in the radial direction The height is the difference in radius between the outer diameter surface (23a) of the spacer (23') and the top surface (13b) of the convex portion (13) facing it, or the distance of the spacer (23'). The sprocket according to claim 3, wherein the difference in radius between the outer diameter surface (23a) and the inner diameter surface (31a) of the spacer portion (31) opposing thereto is set larger than the difference. 前記間隔保持部材（２０）は、前記内輪（４１）の内面（４４）に当接する外面（２６）を有する筒状部（２１）と、前記筒状部（２１）から外径方向に突出する位置決め凸部（２３）を備え、前記位置決め側面（２５）は前記位置決め凸部（２３）に設けられている請求項１に記載のスプロケット。 The spacing member (20) includes a tubular portion (21) having an outer surface (26) that contacts the inner surface (44) of the inner ring (41), and protrudes radially from the tubular portion (21). A sprocket according to claim 1, comprising a positioning projection (23), said positioning flank (25) being provided on said positioning projection (23). 前記間隔保持部材（２０）は、前記内輪（４１，４１）の外方端面（４１ｂ，４１ｂ）に当接する補助端面（２７）と、前記内輪（４１）の内面（４４）に当接する補助外面（２８）を有する補助部材（２２）を前記筒状部（２１）とは別体に備え、
前記筒状部（２１）の外面（２６）は、前記内輪（４１）の内面（４４）のうち内方寄りの部分にのみ当接し、前記補助外面（２８）は、前記内輪（４１）の内面（４４）のうち外方寄りの部分にのみ当接する請求項１又は５に記載のスプロケット。 The spacing member (20) has an auxiliary end surface (27) in contact with the outer end surfaces (41b, 41b) of the inner rings (41, 41) and an auxiliary outer surface in contact with the inner surface (44) of the inner ring (41). An auxiliary member (22) having (28) is provided separately from the cylindrical portion (21),
The outer surface (26) of the cylindrical portion (21) abuts only an inward portion of the inner surface (44) of the inner ring (41), and the auxiliary outer surface (28) contacts the inner ring (41). A sprocket according to claim 1 or 5, wherein the inner surface (44) abuts only the outward portion thereof.
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