JPH0791459A - Spring clutch - Google Patents
Spring clutchInfo
- Publication number
- JPH0791459A JPH0791459A JP23806193A JP23806193A JPH0791459A JP H0791459 A JPH0791459 A JP H0791459A JP 23806193 A JP23806193 A JP 23806193A JP 23806193 A JP23806193 A JP 23806193A JP H0791459 A JPH0791459 A JP H0791459A
- Authority
- JP
- Japan
- Prior art keywords
- coil spring
- driven
- driven shaft
- driving wheel
- main driving
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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
- F16D13/00—Friction clutches
- F16D13/02—Friction clutches disengaged by the contact of a part mounted on the clutch with a stationarily-mounted member
- F16D13/025—Friction clutches disengaged by the contact of a part mounted on the clutch with a stationarily-mounted member with a helical band or equivalent member with two or more turns embracing a drum or the like
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はプリンターあるいはコピ
ー機の給紙部等に用いて好適なスプリングクラッチに関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spring clutch suitable for use in a paper feeding section of a printer or a copying machine.
【０００２】[0002]
【従来の技術】図７、図８は給紙部１０の一例を示す。
１１はトレー、１２、１２は一対の送りローラ、１３は
給紙ローラである。給紙ローラ１３は従動軸１４上に固
定されていて、スプリングクラッチ１５を介して駆動モ
ータ１６により回転駆動される。同時に送りローラ１２
も駆動モータ１６により回転駆動される。給紙ローラ１
３は紙の一端側が送りローラ１２、１２の間に送り込ま
れた際にストッパ装置のストッパレバー１７がスプリン
グクラッチ１５に作用することにより、駆動モータ１６
の駆動力が伝達されず、回転を停止するように制御され
る。2. Description of the Related Art FIGS. 7 and 8 show an example of a paper feed section 10.
11 is a tray, 12 and 12 are a pair of feed rollers, and 13 is a paper feed roller. The paper feed roller 13 is fixed on a driven shaft 14 and is rotationally driven by a drive motor 16 via a spring clutch 15. At the same time, the feed roller 12
Is also rotationally driven by the drive motor 16. Paper feed roller 1
3 is a drive motor 16 when the stopper lever 17 of the stopper device acts on the spring clutch 15 when one end side of the paper is fed between the feed rollers 12, 12.
The driving force is not transmitted and the rotation is controlled to stop.
【０００３】上記従来のスプリングクラッチ１５の一般
的な構成を図９に示す。２０は主動輪であり、従動軸１
４上に遊転自在に設けられる。主動輪２０はコスト低減
化のために合成樹脂で形成されている。主動輪２０の筒
状のボス部２１上には後記する理由により鉄製リング２
２が固定されている。従動軸１４上には従動輪２３がネ
ジ２４により固定されている。該従動輪２３と前記ボス
部２１の大径部に跨がって前記ストッパレバー１７が係
止する逆止爪２５を外周に有するストッパリング２６が
従動軸１４の軸線を中心として回転自在に設けられてい
る。従動輪２３の小径部上と前記鉄製リング２２とに跨
がって巻き締め状態のコイルスプリング２７が装着され
ている。コイルスプリング２７の一端側は外方に曲折さ
れてストッパリング２６の一端面に形成された溝に係入
する係止端２７ａに形成され、コイルスプリング２７の
他端側は従動軸１４の軸線方向に曲折されて、従動輪２
３に設けられた溝に係入する係止端２７ｂに形成されて
いる。２８はスプリングクラッチ１５を従動軸１４上に
固定するための固定リングである。FIG. 9 shows a general structure of the conventional spring clutch 15 described above. 20 is a main driving wheel, and a driven shaft 1
It is provided on 4 in a freely rotatable manner. The main driving wheel 20 is made of synthetic resin for cost reduction. On the cylindrical boss portion 21 of the driving wheel 20, the iron ring 2 is attached for the reason described below.
2 is fixed. A driven wheel 23 is fixed on the driven shaft 14 by screws 24. A stopper ring 26 is provided rotatably around the axis of the driven shaft 14, the stopper ring 26 having a non-return pawl 25 on the outer periphery of the driven wheel 23 and the large diameter portion of the boss portion 21 for locking the stopper lever 17. Has been. A coil spring 27 in a tightly wound state is mounted across the small diameter portion of the driven wheel 23 and the iron ring 22. One end of the coil spring 27 is bent outward and is formed as a locking end 27a that engages with a groove formed in one end surface of the stopper ring 26, and the other end of the coil spring 27 is formed in the axial direction of the driven shaft 14. Driven wheel 2
It is formed on the locking end 27b that engages with the groove provided in the No. 3 connector. Reference numeral 28 denotes a fixing ring for fixing the spring clutch 15 on the driven shaft 14.
【０００４】上記のように構成されていて、前記した駆
動モータ１６により主動輪２０が回転されると、鉄製リ
ング２２と従動輪２３とに跨がって巻き締められている
コイルスプリング２７を介して従動軸１４が回転され、
紙送りが開始される。給紙ローラ１３が１回転すると、
ストッパレバー１７が作動されて逆止爪２５に係合する
とストッパリング２６の回転が停止される。これにより
コイルスプリング２７の一端側の係止端２７ａは拘束さ
れる。主動輪２０がなおも回転を継続すると、摩擦力に
より従動輪２３がなおも回転するが、コイルスプリング
２７は上記のように拘束されて一体回転を停止するの
で、従動輪２３がコイルスプリング２７の他端側の係止
端２７ｂにコイルスプリング２７が緩む方向から作用
し、コイルスプリング２７と鉄製リング２２との間の摩
擦力が負荷と均衡する位置で主動輪２０は従動軸１４に
対して空転し、従動輪１４の回転は停止される。紙は先
端部が送りローラ１２、１２に挾持される位置まで送り
こまれている。これ以後の紙送りは駆動モータ１６、送
りローラ１２、１２により定寸送り等され、印字等され
る。When the main drive wheel 20 is rotated by the drive motor 16 having the above-mentioned structure, the coil spring 27 is wound around the iron ring 22 and the driven wheel 23 and tightened. Driven shaft 14 is rotated,
Paper feeding starts. When the paper feed roller 13 makes one rotation,
When the stopper lever 17 is operated to engage the check claw 25, the rotation of the stopper ring 26 is stopped. As a result, the locking end 27a on one end side of the coil spring 27 is restrained. When the main driving wheel 20 continues to rotate, the driven wheel 23 still rotates due to the frictional force, but the coil spring 27 is constrained as described above and stops the integral rotation. The main driving wheel 20 idles with respect to the driven shaft 14 at a position where the coil spring 27 acts on the locking end 27b on the other end side from the direction of loosening, and the frictional force between the coil spring 27 and the iron ring 22 balances the load. Then, the rotation of the driven wheel 14 is stopped. The paper has been fed to a position where the leading end is held by the feed rollers 12, 12. Subsequent paper feed is performed by the drive motor 16 and the feed rollers 12 and 12 at a fixed size, and printing is performed.
【０００５】[0005]
【発明が解決しようとする課題】ところで従来の上記ス
プリングクラッチ１５には次のような問題点がある。ま
ずコイルスプリング２７が鉄製リング２２と従動輪２３
との間に跨がって装着されているので、鉄製リング２２
と従動輪２３との径にバラツキがあったり回転振れが生
じた場合、図１０に示すように角にだれが生じたり、コ
イルスプリング２７の浮きが生じて巻きつき角が少なく
なり必要なトルクを伝えられなくなる。したがって鉄製
リング２２や従動輪２３の高精度の加工が必要となりコ
スト高となる。The conventional spring clutch 15 has the following problems. First, the coil spring 27 includes the iron ring 22 and the driven wheel 23.
Since it is mounted across the
When there is a variation in the diameter between the driven wheel 23 and the driven wheel 23 or rotational runout occurs, as shown in FIG. 10, the angle is drooped, the coil spring 27 floats, and the wrapping angle is reduced to reduce the required torque. I can't communicate. Therefore, it is necessary to process the iron ring 22 and the driven wheel 23 with high precision, resulting in high cost.
【０００６】またコイルスプリング２７も加工時に真円
度がでているとは限らず、また断面方形のコイルスプリ
ングを用いるがこれが図１１に示すように軸線に対して
傾いていることもあり、やはり巻きつき角が減少するな
どから高精度の内面研摩等が必要となり、コスト高につ
ながる。なお、原理的にはコイルスプリング２７は鉄製
リング２２のみに巻きつけ、従動輪２３には単に係止す
るだけでもよいが、そうすると全負荷が係止端２７ｂに
掛かり、係止端２７ｂが伸びてしまって伝達精度が落ち
ることになるので、従動輪２３側にも巻きつけて負荷の
分担を図るようにしている。Further, the coil spring 27 does not always have a circularity at the time of processing, and a coil spring having a rectangular cross section is used, but this may be inclined with respect to the axis as shown in FIG. Since the wrapping angle is reduced, highly accurate inner surface polishing etc. is required, which leads to high cost. In principle, the coil spring 27 may be wound only on the iron ring 22 and simply locked to the driven wheel 23, but then, the full load is applied to the locking end 27b and the locking end 27b extends. Since the transmission accuracy is deteriorated, the winding is also wound around the driven wheel 23 side to share the load.
【０００７】強度的な面から従動輪２３は金属製のもの
とする必要があり、一方主動輪２０はコストの面から合
成樹脂製のものとせざるをえないものであるが、主動輪
２０の空転時にはコイルスプリング２７との間の摩擦に
より熱が発生する。これによりコイルスプリング２７の
巻き付き部である主動輪２０の部位や従動輪２３が膨張
する。主動輪２０と従動輪２３とが異材質のものである
と膨張度が相違し、図１０と同様にコイルスプリング２
７の巻き付き部に段差が生じ、上記と同様の問題が生じ
る。このため主動輪２０の側と従動輪２３との線膨張係
数を揃える必要があり、主動輪２０に合成樹脂のものを
使う場合に鉄製リング２２を用いる必要があるのであ
る。From the standpoint of strength, the driven wheel 23 must be made of metal, while the main driving wheel 20 must be made of synthetic resin for cost reasons. During idling, heat is generated due to friction with the coil spring 27. As a result, the portion of the main driving wheel 20 that is the winding portion of the coil spring 27 and the driven wheel 23 expand. If the main driving wheel 20 and the driven wheel 23 are made of different materials, the expansion degrees are different, and the coil spring 2 is the same as in FIG.
A step is formed at the winding part of 7 and the same problem as described above occurs. Therefore, it is necessary to make the linear expansion coefficients of the main driving wheel 20 side and the driven wheel 23 uniform, and it is necessary to use the iron ring 22 when using synthetic resin for the main driving wheel 20.
【０００８】このように鉄製リング２２を用いると主動
輪２０との一体成形にコストがかかるばかりか、空転時
にキーキーという異音が発生するという問題点がある。
この異音は、主としてコイルスプリング２７と鉄製リン
グ２２、従動輪２３との間の接触部の面精度が悪いと、
どちらか硬い方の部材により柔らかい部材の方が削り取
られ、これによって異音が発生すると考えられるところ
であり、この異音発生防止のため面精度を可能な限り向
上するという方向で対策がたてられているが、異音対策
のため製品原価の３０％以上のコストがかけられている
という問題点がある。When the iron ring 22 is used as described above, not only is it costly to integrally mold the main ring 20 with the main driving wheel 20, but also there is a problem that abnormal noise is generated when the wheel is idling.
This abnormal noise is caused mainly by poor surface accuracy of the contact portion between the coil spring 27, the iron ring 22, and the driven wheel 23.
It is considered that the softer member is scraped off by the harder one, which causes abnormal noise.Therefore, measures are taken to improve the surface accuracy as much as possible to prevent this abnormal noise. However, there is a problem that 30% or more of the product cost is incurred as a measure against abnormal noise.
【０００９】そこで、本発明は上記問題点を解決すべく
なされたものであり、その目的とするところは、コスト
の低減化が図れ、また異音の発生を効果的に防止できる
スプリングクラッチを提供するにある。Therefore, the present invention has been made to solve the above problems, and an object of the present invention is to provide a spring clutch capable of reducing the cost and effectively preventing the generation of abnormal noise. There is.
【００１０】[0010]
【課題を解決するための手段】本発明は上記目的を達成
するため次の構成を備える。すなわち、従動軸上に軸線
を中心として遊転自在に装着可能な、合成樹脂製の主動
輪と、該主動輪と一体に合成樹脂で主動輪と同軸に形成
された筒体と、該筒体の内側に、主動輪の回転方向と同
一方向に巻かれると共に、外周で筒体内周面に圧接する
よう組み込まれ、両端部が各々内方に曲折されて係止端
に形成されたコイルスプリングと、従動軸上に適宜固定
部材により固定可能に設けられ、前記コイルスプリング
の一端側の係止端が係入する係合部が形成された従動部
材と、前記コイルスプリングの他端側の係止端が係入す
る係合部が形成され、外部からの適宜なストッパ装置か
ら前記主動輪に対する回転停止を掛けられることが可能
なストッパ部材とを具備することを特徴としている。The present invention has the following constitution in order to achieve the above object. That is, a synthetic resin main driving wheel that can be mounted on the driven shaft so as to be freely rotatable around the axis, a cylindrical body integrally formed with the main driving wheel and made of synthetic resin and coaxial with the main driving wheel, and the cylindrical body. Inside, the coil spring is wound in the same direction as the direction of rotation of the main driving wheel, and is assembled so as to make pressure contact with the inner peripheral surface of the cylinder at the outer periphery, and both ends are bent inward and formed at the locking end. A driven member that is provided on the driven shaft so that it can be fixed by an appropriate fixing member, and has an engaging portion into which the one end of the coil spring engages, and the other end of the coil spring that is locked. It is characterized in that it is provided with a stopper member which is formed with an engaging portion whose end is engaged and which can stop rotation of the driving wheel from an appropriate stopper device from the outside.
【００１１】前記ストッパ部材の係合部を、ストッパ部
材の端面に周方向に所定間隔をおいて設けた複数の係合
溝にすると好適である。また、前記コイルスプリングの
一部または全部を粗巻きに形成すると好適である。It is preferable that the engaging portion of the stopper member be a plurality of engaging grooves provided on the end surface of the stopper member at predetermined intervals in the circumferential direction. Further, it is preferable that a part or the whole of the coil spring is formed into a coarse winding.
【００１２】さらに前記固定部材４４は、金属板をプレ
ス加工して形成され、一対の対向片４６、４６が連絡片
４７で連絡された断面コの字状をなし、一対の対向片４
６、４６には従動軸１４が差し渡し状に挿通する軸孔４
８、４８が形成され、さらに一対の対向片４６、４６と
連絡片４７とに亙って両軸孔４８、４８を連絡する連絡
孔４９が形成されることによって従動軸１４を挾む両側
に一対の挾持部５０ａ、５０ｂが形成され、両対向片４
６、４６には前記従動部材３３の係止片３６が嵌入しう
る回転止め部５１が形成された固定金具４５と、固定金
具４５の両挾持部５０ａ、５０ｂ間に保持されたナット
５３とで構成し、該ナット５３に螺合される締めつけネ
ジ５５により従動軸１４を締めつけるようにすると好適
である。Further, the fixing member 44 is formed by pressing a metal plate and has a U-shaped cross section in which a pair of facing pieces 46, 46 are connected by a connecting piece 47.
6 and 46, the shaft hole 4 through which the driven shaft 14 is inserted.
8 and 48 are formed, and further, a pair of opposing pieces 46, 46 and a connecting piece 47 are formed with a connecting hole 49 for connecting the shaft holes 48, 48 to both sides of the driven shaft 14. A pair of holding parts 50a, 50b are formed, and both facing pieces 4
6 and 46 are composed of a fixing fitting 45 having a rotation stopping portion 51 into which the locking piece 36 of the driven member 33 can be fitted, and a nut 53 held between both holding portions 50a and 50b of the fixing fitting 45. It is preferable that the driven shaft 14 is configured to be tightened by a tightening screw 55 screwed to the nut 53.
【００１３】[0013]
【作用】図１〜３により作用を説明する。 トルク伝達時：駆動モータ等の駆動部から主動輪３１に
動力が伝達されて主動輪３１が回転すると、筒体３２と
コイルスプリング４１との間の摩擦力によりコイルスプ
リング４１も回転し、係止端４２を介して従動部材３
３、したがって従動軸１４が回転される。ストッパ部材
３７もコイルスプリング４１の係止端４３が係合溝３９
に係合していることから回転される。The operation will be described with reference to FIGS. During torque transmission: When power is transmitted from a drive unit such as a drive motor to the main driving wheel 31 and the main driving wheel 31 rotates, the coil spring 41 also rotates and locks due to the frictional force between the tubular body 32 and the coil spring 41. Driven member 3 via end 42
3, thus the driven shaft 14 is rotated. As for the stopper member 37, the engaging end 43 of the coil spring 41 has an engaging groove 39.
It is rotated because it is engaged with.
【００１４】トルク非伝達時：ストッパレバーが逆止爪
４０に係止するとストッパ部材３７はその回転が停止さ
れる。したがってコイルスプリング４１の係止端４３も
拘束される。主動輪３１がなおも回転すると、従動部材
３３は係止端４３よりも先方側のコイルスプリング４１
と筒体３２との間の摩擦力によってなおも若干回転され
るが、図３に明確なように、係止端４３はストッパ部材
３７に拘束されるので、従動部材３３の回転はコイルス
プリング４１の筒体３２への接触度を緩める方向に係止
端４２に作用する。そして従動側の負荷と、コイルスプ
リング４１と筒体３２内周面との間の摩擦力とが均衡し
たところで主動輪３１は空転し、従動側へのトルクの伝
達はなくなり、従動軸１４の回転は停止する。ストッパ
部材３７に設けた切欠３８の大きさはストッパ部材３７
の回転が停止した後主動輪３１が空転するまでの従動部
材３３の回転を許容する幅に若干の余裕を持たせた大き
さであればよい。ストッパ部材３７に係止端４３の係合
溝３９を複数設けたのは、係止端４３と係止端４２の折
り曲げ位置にコイルスプリング毎にバラツキがあっても
これを吸収するためである。When torque is not transmitted: When the stopper lever is engaged with the check claw 40, the rotation of the stopper member 37 is stopped. Therefore, the locking end 43 of the coil spring 41 is also restrained. When the main driving wheel 31 still rotates, the driven member 33 causes the coil spring 41 on the front side of the locking end 43 to move.
Although it is still slightly rotated due to the frictional force between the cylinder 32 and the cylindrical body 32, as shown in FIG. 3, since the locking end 43 is constrained by the stopper member 37, the rotation of the driven member 33 causes the coil spring 41 to rotate. Acts on the locking end 42 in a direction to loosen the degree of contact of the cylinder body 32 with the cylinder body 32. Then, when the load on the driven side and the frictional force between the coil spring 41 and the inner peripheral surface of the cylindrical body 32 are balanced, the main driving wheel 31 idles, the torque is not transmitted to the driven side, and the driven shaft 14 rotates. Will stop. The size of the notch 38 provided in the stopper member 37 is different from that of the stopper member 37.
It is sufficient that the width that allows the rotation of the driven member 33 until the main driving wheel 31 idles after the rotation of No. 2 has a slight margin. The stopper member 37 is provided with a plurality of engaging grooves 39 of the locking ends 43 in order to absorb the variation in the bending positions of the locking ends 43 and the locking positions 42 between the coil springs.
【００１５】[0015]
【実施例】以下、本発明の好適な実施例を添付図面に基
づいて詳細に説明する。図１はスプリングクラッチ３０
の一例を示す断面図である。３１は主動輪であり、従動
軸１４上で従動軸１４の軸線を中心として回転可能に装
着されるようになっている。主動輪３１には同軸に前方
に伸びる筒体３２がポリアセタール樹脂等の耐磨耗性の
大きな合成樹脂で一体的に形成されている。筒体３２の
内径は入口側が大径の大径部３２ａに奥側が小径の小径
部３２ｂになるように設けるのがよい。３３は筒状に形
成された従動部材で、主動輪３１に対して筒体３２側の
従動軸１４上に外嵌されている。従動部材３３は強度上
の点から金属で形成するのが好ましいが、合成樹脂で形
成してもよい。従動部材３３の外周上には規制突起３４
が突設され、該規制突起３４には係合部たる係入溝３５
が径方向に設けられている。また筒体３２と反対側の従
動部材３３の端面には一対の係止片３６が軸方向に突設
されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described in detail below with reference to the accompanying drawings. FIG. 1 shows a spring clutch 30.
It is sectional drawing which shows an example. Reference numeral 31 is a main driving wheel, which is mounted on the driven shaft 14 so as to be rotatable around the axis of the driven shaft 14. A cylindrical body 32 that extends coaxially forward is integrally formed with the main drive wheel 31 with a synthetic resin having a large abrasion resistance, such as polyacetal resin. The inner diameter of the cylindrical body 32 is preferably provided so that the inlet side is a large diameter portion 32a having a large diameter and the inner side is a small diameter portion 32b having a small diameter. Reference numeral 33 denotes a driven member formed in a tubular shape, which is fitted onto the driven shaft 14 on the cylindrical body 32 side with respect to the main driving wheel 31. The driven member 33 is preferably made of metal in terms of strength, but may be made of synthetic resin. A restriction protrusion 34 is provided on the outer periphery of the driven member 33.
Is provided so that the restricting protrusion 34 has an engaging groove 35 as an engaging portion.
Are provided in the radial direction. Further, a pair of locking pieces 36 are axially projected on the end surface of the driven member 33 on the side opposite to the tubular body 32.
【００１６】３７は筒状をなすストッパ部材で、従動部
材３３上に外嵌され、軸線を中心として所定角度範囲内
で回転自在に設けられている。すなわち、図２に明確な
ようにストッパ部材３７の筒体３２側には方形の切欠３
８が形成され、この切欠３８内に従動部材３３の規制突
起３４が突出しており、ストッパ部材３７は切欠３８の
対向する両内壁面が規制突起３４に当接する範囲で回転
可能になっている。またストッパ部材３７の筒体３２側
の端面には周方向に所定の間隔をおいて複数の係合溝３
９が設けられている。さらにストッパ部材３７の外周面
には逆止爪４０が設けられている。ストッパ部材３７の
筒体３２内に進入する部位の外径は他の部分よりも小径
の小径部３７ａに形成されている。該小径部３７ａの先
端側は筒体部３２の奥側の小径部３２ｂ内に嵌入してい
る。Reference numeral 37 denotes a cylindrical stopper member which is fitted onto the driven member 33 and is rotatable within the predetermined angle range about the axis. That is, as clearly shown in FIG. 2, the rectangular notch 3 is formed on the cylindrical body 32 side of the stopper member 37.
8 is formed, and the restriction protrusion 34 of the driven member 33 projects in the notch 38, and the stopper member 37 is rotatable within a range in which both inner wall surfaces of the notch 38 facing each other contact the restriction protrusion 34. Further, a plurality of engagement grooves 3 are provided on the end surface of the stopper member 37 on the cylinder body 32 side at predetermined intervals in the circumferential direction.
9 is provided. Further, a check claw 40 is provided on the outer peripheral surface of the stopper member 37. The outer diameter of the portion of the stopper member 37 that enters the cylindrical body 32 is formed in a small diameter portion 37a having a smaller diameter than the other portions. The tip side of the small diameter portion 37a is fitted into the small diameter portion 32b on the inner side of the tubular body portion 32.
【００１７】４１はコイルスプリングで、筒体３２の大
径部３２ａ内周面とストッパ部材３７の小径部３７ａ外
周面との間の空間に縮径状態で収納され、縮径状態が開
放されることにより筒体３２内周面にその外周で圧接状
態で接触している。コイルスプリング４１の巻き方向は
図３に示すように主動輪３１（筒体３２）の回転方向と
同一の方向に設定される。コイルスプリング４１の両端
部はそれぞれ内方に曲折されて係止端４２、４３に形成
され、係止端４２は従動部材３３の係入溝３５に係入さ
れ、他方の係止端４３はストッパ部材３７の適所の係合
溝３９に係合されている。なおコイルスプリング４１は
密に巻回したものでもよいが一部または全部を粗巻きに
したものを用いるのが好ましく、軸方向に圧縮状態で組
み込むことにより、その弾発力により特に係止端４２が
係入溝３５の奥側に弾発され、確実に係入溝３５内に位
置させることができる。Reference numeral 41 denotes a coil spring, which is accommodated in the space between the inner peripheral surface of the large diameter portion 32a of the cylindrical body 32 and the outer peripheral surface of the small diameter portion 37a of the stopper member 37 in a reduced diameter state, and the reduced diameter state is released. As a result, the outer peripheral surface of the cylindrical body 32 is in pressure contact with the inner peripheral surface thereof. The winding direction of the coil spring 41 is set in the same direction as the rotating direction of the main driving wheel 31 (cylindrical body 32) as shown in FIG. Both ends of the coil spring 41 are bent inwardly to form locking ends 42 and 43, respectively. The locking end 42 is locked in the locking groove 35 of the driven member 33, and the other locking end 43 is a stopper. It is engaged with an engaging groove 39 at a proper position of the member 37. The coil spring 41 may be tightly wound, but it is preferable to use a part or all of the coil spring roughly wound. When the coil spring 41 is assembled in a compressed state in the axial direction, it is particularly elastic due to its elastic force. Is elastically pushed to the inner side of the engaging groove 35, and can be reliably positioned in the engaging groove 35.
【００１８】４４は前記従動部材３３を従動軸１４上に
固定するための固定部材である。固定部材４４は固定金
具４５とナット５３を具備する。固定金具４５は金属板
をプレス加工して形成される。固定金具４５は一対の対
向片４６、４６が連絡片４７で連絡された断面コの字状
をなす（図１）。一対の対向片４６、４６には従動軸１
４が差し渡し状に挿通する軸孔４８、４８が形成されて
いる。さらに一対の対向片４６、４６と連絡片４７とに
亙って両軸孔４８、４８を連絡する連絡孔４９が形成さ
れている。連絡孔４９の対向辺は平行な直線状に形成さ
れている。したがって一対の対向片４６、４６および連
絡片４７は軸孔４８、４８および連絡孔４９により分離
されて、図４の正面形状において従動軸１４を挾む両側
に一対の挾持部５０ａ、５０ｂが形成されることにな
る。両対向片４６、４６の側縁部には前記従動部材３３
の一対の係止片３６が嵌入しうる切欠５１（回転止め
部）が形成されている。Reference numeral 44 is a fixing member for fixing the driven member 33 on the driven shaft 14. The fixing member 44 includes a fixing fitting 45 and a nut 53. The fixing bracket 45 is formed by pressing a metal plate. The fixing member 45 has a U-shaped cross section in which a pair of facing pieces 46, 46 are connected by a connecting piece 47 (FIG. 1). The driven shaft 1 is provided on the pair of facing pieces 46, 46.
Shaft holes 48, 48 through which 4 is inserted are formed. Further, a connecting hole 49 is formed across the pair of facing pieces 46, 46 and the connecting piece 47 to connect the shaft holes 48, 48. Opposite sides of the communication hole 49 are formed in parallel straight lines. Therefore, the pair of facing pieces 46, 46 and the connecting piece 47 are separated by the shaft holes 48, 48 and the connecting hole 49, and a pair of holding portions 50a, 50b are formed on both sides of the driven shaft 14 in the front view of FIG. Will be done. The driven member 33 is provided on the side edge portions of the opposing pieces 46, 46.
A notch 51 (rotation stopping portion) into which the pair of locking pieces 36 can be fitted is formed.
【００１９】５３はナットであり、両挾持部５０ａ、５
０ｂ間に挾持部５０ａ、５０ｂの弾性に抗して押入され
ることで保持されている。またナット５３の外周部には
一対の対向片４６、４６間に進入する突起部５４が設け
られ、この突起部５４が連絡片４７に内側から当接す
る。固定部材４４は上記のように構成されているから、
ナット５３のネジ孔に固定ネジ５５を螺入していくこと
で、固定ネジ５５と軸孔４８、４８との間で従動軸１４
を締めつけることができ、固定部材４４は従動軸１４上
に固定される。同時に切欠５１内に従動部材３３の係止
片３６が嵌入されるようにしておくことで、従動部材３
３は従動軸１４上での軸線を中心とする回転が阻止され
る。図１において５７は固定リングで、ネジ５８により
従動軸１４上に固定することで固定部材４４とでスプリ
ングクラッチ３０の従動軸１４の軸方向への移動を規制
する。なお固定リング５７も金属板をプレス加工して固
定部材４４と同様の構成にしてもよい。Reference numeral 53 is a nut, which holds the two holding portions 50a, 5a.
It is held by being pushed in between 0b against the elasticity of the holding parts 50a, 50b. Further, a protrusion 54 is provided on the outer peripheral portion of the nut 53 so as to enter between the pair of facing pieces 46, 46, and the protrusion 54 abuts the connecting piece 47 from the inside. Since the fixing member 44 is configured as described above,
By screwing the fixing screw 55 into the screw hole of the nut 53, the driven shaft 14 is inserted between the fixing screw 55 and the shaft holes 48, 48.
Can be tightened and the fixing member 44 is fixed on the driven shaft 14. At the same time, the engaging piece 36 of the driven member 33 is fitted in the notch 51, so that the driven member 3
3 is prevented from rotating about the axis on the driven shaft 14. In FIG. 1, a fixing ring 57 is fixed on the driven shaft 14 by a screw 58 to restrict the movement of the spring clutch 30 in the axial direction of the driven shaft 14 together with the fixing member 44. Note that the fixing ring 57 may have the same structure as the fixing member 44 by pressing a metal plate.
【００２０】続いて動作を説明する。駆動モータ等の駆
動部から主動輪３１に動力が伝達されて主動輪３１が回
転すると、筒体３２とコイルスプリング４１との間の摩
擦力によりコイルスプリング４１も回転し、係止端４２
を介して従動部材３３、したがって従動軸１４が回転さ
れる。ストッパ部材３７もコイルスプリング４１の係止
端４３が係合溝３９に係合していることから回転され
る。Next, the operation will be described. When power is transmitted from a drive unit such as a drive motor to the driving wheel 31 and the driving wheel 31 rotates, the coil spring 41 also rotates due to the frictional force between the tubular body 32 and the coil spring 41, and the locking end 42
The driven member 33, and thus the driven shaft 14, is rotated via. The stopper member 37 is also rotated because the locking end 43 of the coil spring 41 is engaged with the engagement groove 39.
【００２１】ストッパレバーが逆止爪４０に係止すると
ストッパ部材３７はその回転が停止される。したがって
コイルスプリング４１の係止端４３も拘束される。主動
輪３１がなおも回転すると、従動部材３３は係止端４３
よりも先方側のコイルスプリング４１と筒体３２との間
の摩擦力によってなおも若干回転されるが、図３に明確
なように、係止端４３はストッパ部材３７に拘束される
ので、従動部材３３の回転はコイルスプリング４１の筒
体３２への接触度を緩める方向に係止端４２に作用す
る。そして従動側の負荷と、コイルスプリング４１と筒
体３２内周面との間の摩擦力とが均衡したところで主動
輪３１は空転し、従動側へのトルクの伝達はなくなり、
従動軸１４の回転は停止する。When the stopper lever is engaged with the check claw 40, the rotation of the stopper member 37 is stopped. Therefore, the locking end 43 of the coil spring 41 is also restrained. When the main driving wheel 31 is still rotated, the driven member 33 is locked by the locking end 43.
Although it is still slightly rotated due to the frictional force between the coil spring 41 and the tubular body 32 on the front side, the locking end 43 is restrained by the stopper member 37 as shown in FIG. The rotation of the member 33 acts on the locking end 42 in a direction that loosens the degree of contact of the coil spring 41 with the cylindrical body 32. Then, when the load on the driven side and the frictional force between the coil spring 41 and the inner peripheral surface of the cylindrical body 32 are balanced, the driving wheel 31 idles, and torque transmission to the driven side is stopped.
The rotation of the driven shaft 14 stops.
【００２２】ストッパ部材３７に設けた切欠３８の大き
さはストッパ部材３７の回転が停止した後主動輪３１が
空転するまでの従動部材３３の回転を許容する幅に若干
の余裕を持たせた大きさであればよい。ストッパ部材３
７に係止端４３の係合溝３９を複数設けたのは、係止端
４３と係止端４２の折り曲げ位置にコイルスプリング毎
にバラツキがあってもこれを吸収するためである。The size of the notch 38 provided in the stopper member 37 is such that a slight allowance is provided in the width that allows the driven member 33 to rotate until the main driving wheel 31 idles after the rotation of the stopper member 37 stops. All right. Stopper member 3
The plurality of engaging grooves 39 of the locking end 43 are provided in the table 7 in order to absorb the variation in the bending positions of the locking end 43 and the locking end 42 for each coil spring.
【００２３】主動輪３１から従動側へのトルク伝達時に
は、図３から明らかなように係止端４２はコイルスプリ
ング４１が益々筒体３２の内周面に圧接するようになる
方向から従動部材３３を押すので、コイルスプリング４
１の摩擦力は増大し、主動輪３１からの駆動力が従動部
材３３側に良好に伝達される。When torque is transmitted from the main driving wheel 31 to the driven side, as shown in FIG. 3, the locking end 42 is moved from the direction in which the coil spring 41 is pressed against the inner peripheral surface of the cylindrical body 32 more and more. Press, so coil spring 4
The frictional force of No. 1 increases, and the driving force from the main driving wheel 31 is satisfactorily transmitted to the driven member 33 side.
【００２４】また係止端４２には従来と異なり曲折部が
伸びる方向には負荷が作用しないから、常に確実に駆動
力の伝達が行える。このことは重要であり、従来の場合
には図９に示すように係止端２７ｂに全負荷がかかって
係止端２７ｂが伸びてしまうのを防止するため、コイル
スプリング２７を従動輪２３側にも巻きつけて負荷を分
担するようにしたが、本実施例では上記のように、負荷
を係止端４２を介してコイルスプリング４１本体側で素
直に受けるため、係止端４２に掛かる曲げ応力が最小限
となり、したがって本実施例では、コイルスプリング４
１は筒体３２にだけ内側から接触するように設ければよ
い。Further, unlike the prior art, no load is applied to the engaging end 42 in the direction in which the bent portion extends, so that the driving force can always be reliably transmitted. This is important, and in the conventional case, as shown in FIG. 9, in order to prevent the locking end 27b from being fully loaded and the locking end 27b extending, the coil spring 27 is attached to the driven wheel 23 side. Although the load is shared by winding it around, the load is directly received by the coil spring 41 main body side via the locking end 42 as described above in the present embodiment. The stress is minimized and therefore in this embodiment the coil spring 4
1 may be provided so as to contact only the cylindrical body 32 from the inside.
【００２５】これにより次のような効果を有する。すな
わち、コイルスプリング４１は筒体３２のみに接触する
ため、従来のように金属リング２２と従動輪２３の外径
を高精度に確保するような加工が必要でなく、コストの
低減化が図れる。筒体３２の内側にコイルスプリング４
１が入っている簡単な構造のため、空転時のトルクロス
による温度上昇があっても単一の筒体３２であるから、
従来のように従動輪２３と線膨張係数をあわせるための
金属リング２２を用いる必要はなく、合成樹脂製の主動
輪３１のままでよいから、コストの低減化が図れる。さ
らには、筒体３２を合成樹脂で形成するので、自己潤滑
性があり、潤滑油を用いなくとも異音の発生を防止で
き、また、筒体３２内周面の真円度や面精度がそれ程で
なくとも、筒体樹脂の弾性変形によりコイルスプリング
４１との密着度がよく、特に伝達トルクが上がるにつれ
て密着度がよくなるので、筒体３２の精度をそれ程気に
しなくともよく、コストの低減化が図れる。また固定部
材に金属板をプレス加工したものを用いることによって
コストの低減化が図れる。This has the following effects. That is, since the coil spring 41 contacts only the cylindrical body 32, it is not necessary to perform processing to secure the outer diameters of the metal ring 22 and the driven wheel 23 with high precision as in the conventional case, and the cost can be reduced. The coil spring 4 is provided inside the cylindrical body 32.
Because of the simple structure containing 1, even if there is a temperature rise due to torque loss during idling, it is a single cylinder 32,
It is not necessary to use the metal ring 22 for matching the linear expansion coefficient with the driven wheel 23 as in the conventional case, and the main driving wheel 31 made of synthetic resin may be used as it is, so that the cost can be reduced. Furthermore, since the cylindrical body 32 is formed of synthetic resin, it has self-lubricating properties, and it is possible to prevent abnormal noise from occurring without using lubricating oil, and the circularity and surface accuracy of the inner peripheral surface of the cylindrical body 32 are improved. Even if it is not so much, the degree of close contact with the coil spring 41 is good due to the elastic deformation of the cylindrical body resin, and the closeness of contact is especially improved as the transmission torque increases, so that the accuracy of the cylindrical body 32 does not have to be so important and the cost is reduced. Can be realized. Further, cost reduction can be achieved by using a press member made of a metal plate as the fixing member.
【００２６】[0026]
【発明の効果】本発明によれば、従動側の負荷を係止端
を介してコイルスプリング本体側で素直に受けるため、
係止端に掛かる曲げ応力が最小限となり、したがってコ
イルスプリングは筒体にだけ内側から接触するように設
ければよい。According to the present invention, since the load on the driven side is directly received by the coil spring body side via the locking end,
The bending stress applied to the locking end is minimized, and therefore the coil spring may be provided so as to contact only the cylindrical body from the inside.
【００２７】これにより次のような効果を有する。すな
わち、コイルスプリングは筒体のみに接触するため、従
来のように金属リングと従動輪の外径を高精度に確保す
るような加工が必要でなく、コストの低減化が図れる。
筒体の内側にコイルスプリングが入っている簡単な構造
のため、空転時のトルクロスによる温度上昇があっても
単一の筒体であるから、従来のように従動輪と線膨張係
数をあわせるための金属リングを用いる必要はなく、合
成樹脂製の主動輪のままでよいから、コストの低減化が
図れる。さらには、筒体を合成樹脂で形成するので、自
己潤滑性があり、潤滑油を用いなくとも異音の発生を防
止でき、また、筒体内周面の真円度や面精度がそれ程で
なくとも、筒体樹脂の弾性変形によりコイルスプリング
との密着度がよく、特に伝達トルクが上がるにつれて密
着度がよくなるので、筒体の精度をそれ程気にしなくと
もよく、コストの低減化が図れる。また固定部材に金属
板をプレス加工したものを用いることによってコストの
低減化が図れる。This has the following effects. That is, since the coil spring contacts only the cylindrical body, it is not necessary to perform processing to secure the outer diameters of the metal ring and the driven wheel with high precision as in the conventional case, and the cost can be reduced.
Due to the simple structure of the coil spring inside the cylinder, it is a single cylinder even if the temperature rises due to torque loss during idling. Since it is not necessary to use the metal ring described above and the main driving wheel made of synthetic resin can be used as it is, the cost can be reduced. Furthermore, since the cylinder is made of synthetic resin, it has self-lubricating properties and can prevent the generation of abnormal noise without the use of lubricating oil. Moreover, the roundness and surface accuracy of the cylinder inner surface are not so high. In addition, the degree of close contact with the coil spring is good due to the elastic deformation of the tubular resin, and the closeness of contact is particularly improved as the transmission torque increases, so that the accuracy of the tubular body does not have to be so important and the cost can be reduced. Further, cost reduction can be achieved by using a press member made of a metal plate as the fixing member.
【図１】スプリングクラッチの一例を示す側面断面図で
ある。FIG. 1 is a side sectional view showing an example of a spring clutch.
【図２】ストッパ部材と従動部材の関係を示す説明図で
ある。FIG. 2 is an explanatory diagram showing a relationship between a stopper member and a driven member.
【図３】コイルスプリングの係止端の係止関係を示す一
部破断断面図である。FIG. 3 is a partially cutaway sectional view showing a locking relationship of locking ends of a coil spring.
【図４】固定部材の正面図を示す。FIG. 4 shows a front view of a fixing member.
【図５】ナットの平面形状の説明図である。FIG. 5 is an explanatory diagram of a plane shape of a nut.
【図６】固定金具の展開図を示す。FIG. 6 shows a development view of a fixing bracket.
【図７】給紙装置の平面図である。FIG. 7 is a plan view of the sheet feeding device.
【図８】給紙装置の断面図である。FIG. 8 is a cross-sectional view of the sheet feeding device.
【図９】従来のスプリングクラッチの側面断面図であ
る。FIG. 9 is a side sectional view of a conventional spring clutch.
【図１０】コイルスプリングの巻き付き状態を示す説明
図である。FIG. 10 is an explanatory diagram showing a wound state of a coil spring.
【図１１】コイルスプリング線の傾き状態を示す説明図
である。FIG. 11 is an explanatory diagram showing a tilted state of a coil spring wire.
３０ スプリングクラッチ ３１ 主動輪 ３２ 筒体 ３３ 従動部材 ３５ 係入溝（係合部） ３６ 係止片 ３７ ストッパ部材 ３９ 係合溝（係合部） ４０ 逆止爪 ４１ コイルスプリング ４２ 係止端 ４３ 係止端 ４４ 固定部材 ４５ 固定金具 ４６ 対向片 ４７ 連結片 ４８ 軸孔 ５０ａ、５０ｂ 挾持部 ５１ 切欠（回転止め部） ５３ ナット 30 Spring Clutch 31 Main Wheel 32 Cylindrical Body 33 Follower Member 35 Engagement Groove (Engagement Part) 36 Engagement Piece 37 Stopper Member 39 Engagement Groove (Engagement Part) 40 Check Claw 41 Coil Spring 42 Engagement End 43 Engagement Toe 44 Fixing member 45 Fixing metal fitting 46 Opposing piece 47 Connecting piece 48 Shaft holes 50a, 50b Holding part 51 Notch (rotation stopping part) 53 Nut
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成６年３月１５日[Submission date] March 15, 1994
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】特許請求の範囲[Name of item to be amended] Claims
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【特許請求の範囲】[Claims]
【手続補正２】[Procedure Amendment 2]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１０[Correction target item name] 0010
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１０】[0010]
【課題を解決するための手段】本発明は上記目的を達成
するため次の構成を備える。すなわち、従動軸上に軸線
を中心として遊転自在に装着可能な、主動輪と、該主動
輪と一体的に主動輪と同軸に形成された筒体と、該筒体
の内側に、主動輪の回転方向と同一方向に巻かれると共
に、外周で筒体内周面に圧接するよう組み込まれ、両端
部が各々内方に曲折されて係止端に形成されたコイルス
プリングと、従動軸上に適宜固定部材により固定可能に
設けられ、前記コイルスプリングの一端側の係止端が係
入する係合部が形成された従動部材と、前記コイルスプ
リングの他端側の係止端が係入する係合部が形成され、
外部からの適宜なストッパ装置から前記主動輪に対する
回転停止を掛けられることが可能なストッパ部材とを具
備することを特徴としている。The present invention has the following constitution in order to achieve the above object. That is, a main driving wheel that can be mounted on the driven shaft so as to be freely rotatable about the axis, a cylindrical body integrally formed with the main driving wheel and coaxial with the main driving wheel, and a main driving wheel inside the cylindrical body. The coil spring is wound in the same direction as the rotation direction, and is assembled so as to make pressure contact with the inner peripheral surface of the cylinder at the outer circumference, and both ends are bent inward and the coil spring formed at the locking end and the driven shaft as appropriate. A follower member that is provided so as to be fixable by a fixing member and has an engaging portion into which a locking end on one end side of the coil spring is engaged, and a engaging member to which a locking end on the other end side of the coil spring is engaged. A joint is formed,
It is characterized by comprising a stopper member capable of stopping the rotation of the main driving wheel from an appropriate stopper device from the outside.
【手続補正３】[Procedure 3]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１２[Correction target item name] 0012
【補正方法】削除[Correction method] Delete
【手続補正４】[Procedure amendment 4]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００２７[Name of item to be corrected] 0027
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００２７】これにより次のような効果を有する。すな
わち、コイルスプリングは筒体のみに接触するため、従
来のように金属リングと従動輪の外径を高精度に確保す
るような加工が必要でなく、コストの低減化が図れる。
筒体の内側にコイルスプリングが入っている簡単な構造
のため、空転時のトルクロスによる温度上昇があっても
単一の筒体であるから、従来のように従動輪と線膨張係
数をあわせるための金属リングを用いる必要はなく、コ
ストの低減化が図れる。 This has the following effects. That is, since the coil spring contacts only the cylindrical body, it is not necessary to perform processing to secure the outer diameters of the metal ring and the driven wheel with high precision as in the conventional case, and the cost can be reduced.
Due to the simple structure of the coil spring inside the cylinder, it is a single cylinder even if the temperature rises due to torque loss during idling. It is necessary to use a metal ring instead, thereby is co <br/> reduction strike.
Claims (4)
装着可能な、合成樹脂製の主動輪と、 該主動輪と一体に合成樹脂で主動輪と同軸に形成された
筒体と、 該筒体の内側に、主動輪の回転方向と同一方向に巻かれ
ると共に、外周で筒体内周面に圧接するよう組み込ま
れ、両端部が各々内方に曲折されて係止端に形成された
コイルスプリングと、 従動軸上に適宜固定部材により固定可能に設けられ、前
記コイルスプリングの一端側の係止端が係入する係合部
が形成された従動部材と、 前記コイルスプリングの他端側の係止端が係入する係合
部が形成され、外部からの適宜なストッパ装置から前記
主動輪に対する回転停止を掛けられることが可能なスト
ッパ部材とを具備することを特徴とするスプリングクラ
ッチ。1. A main driving wheel made of synthetic resin, which can be mounted on a driven shaft so as to be freely rotatable around an axis, and a cylindrical body which is integrally formed with the main driving wheel and is coaxial with the main driving wheel. It was wound inside the cylinder in the same direction as the direction of rotation of the main drive wheel, and was assembled so as to make pressure contact with the peripheral surface of the cylinder at the outer periphery, and both ends were bent inward and formed at the locking ends. A coil spring, a driven member that is provided on the driven shaft so that it can be fixed by an appropriate fixing member, and an engaging portion into which a locking end on one end side of the coil spring engages is formed, and the other end side of the coil spring. And a stopper member capable of stopping rotation of the main driving wheel from an appropriate stopper device from the outside.
部材の端面に周方向に所定間隔をおいて設けられた複数
の係合溝であることを特徴とする請求項１記載のスプリ
ングクラッチ。2. The spring clutch according to claim 1, wherein the engaging portion of the stopper member is a plurality of engaging grooves provided on the end surface of the stopper member at predetermined intervals in the circumferential direction.
が粗巻きに形成されていることを特徴とする請求項１ま
たは２記載のスプリングクラッチ。3. The spring clutch according to claim 1, wherein a part or all of the coil spring is roughly wound.
コの字状をなし、 一対の対向片４６、４６には従動軸１４が差し渡し状に
挿通する軸孔４８、４８が形成され、 さらに一対の対向片４６、４６と連絡片４７とに亙って
両軸孔４８、４８を連絡する連絡孔４９が形成されるこ
とによって従動軸１４を挾む両側に一対の挾持部５０
ａ、５０ｂが形成され、 両対向片４６、４６には前記従動部材３３の係止片３６
が嵌入しうる回転止め部５１が形成された固定金具４５
と、 固定金具４５の両挾持部５０ａ、５０ｂ間に保持された
ナット５３とを有し、 該ナット５３に螺合される締めつけネジ５５により従動
軸１４を締めつけることを特徴とする請求項１、２また
は３記載のスプリングクラッチ。4. The fixing member 44 is formed by pressing a metal plate and has a U-shaped cross section in which a pair of facing pieces 46, 46 are connected by a connecting piece 47. A shaft hole 48, 48 through which the driven shaft 14 is passed is formed in the shaft 46, and a communication hole 49 for connecting the shaft holes 48, 48 through the pair of opposed pieces 46, 46 and the connection piece 47. Is formed, a pair of gripping portions 50 are provided on both sides of the driven shaft 14 so as to sandwich the driven shaft 14.
a and 50 b are formed, and the engaging pieces 36 of the driven member 33 are provided on the opposing pieces 46 and 46.
Fixing bracket 45 having a rotation stopper 51 into which the
And a nut 53 held between both holding parts 50a, 50b of the fixing bracket 45, and the driven shaft 14 is tightened by a tightening screw 55 screwed to the nut 53. The spring clutch described in 2 or 3.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23806193A JPH0791459A (en) | 1993-09-24 | 1993-09-24 | Spring clutch |
| AU76654/94A AU7665494A (en) | 1993-09-24 | 1994-09-16 | A spring clutch |
| PCT/JP1994/001535 WO1995008723A1 (en) | 1993-09-24 | 1994-09-16 | A spring clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23806193A JPH0791459A (en) | 1993-09-24 | 1993-09-24 | Spring clutch |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3802794A Division JPH0791460A (en) | 1994-03-09 | 1994-03-09 | Fixing mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0791459A true JPH0791459A (en) | 1995-04-04 |
Family
ID=17024577
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23806193A Pending JPH0791459A (en) | 1993-09-24 | 1993-09-24 | Spring clutch |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH0791459A (en) |
| AU (1) | AU7665494A (en) |
| WO (1) | WO1995008723A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6096817A (en) * | 1997-06-26 | 2000-08-01 | E. I. Du Pont De Nemours And Company | Mixtures of polyimides and elastomers |
| US6328008B1 (en) | 1999-08-03 | 2001-12-11 | Unisia Jecs Corporation | Valve timing control system for internal combustion engine |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6049772A (en) * | 1983-08-29 | 1985-03-19 | Toppan Printing Co Ltd | Packed product of unshelled shellfish |
| JPH0251760B2 (en) * | 1986-06-14 | 1990-11-08 | Reonaado Kurutsu Gmbh Unto Co |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2493721A (en) * | 1941-02-20 | 1950-01-03 | Chrysler Corp | Clutch |
| DE1042980B (en) * | 1957-02-02 | 1958-11-06 | Falz Und Heftmaschinenwerk Lei | Spring band friction clutch |
| FR1199370A (en) * | 1958-02-21 | 1959-12-14 | Curtiss Wright Corp | Refinements to Spring Coupling Mechanisms |
| US3410379A (en) * | 1966-06-01 | 1968-11-12 | Motorola Inc | Coil clutch with one-way brake |
| GB1251296A (en) * | 1968-03-02 | 1971-10-27 |
-
1993
- 1993-09-24 JP JP23806193A patent/JPH0791459A/en active Pending
-
1994
- 1994-09-16 WO PCT/JP1994/001535 patent/WO1995008723A1/en active Application Filing
- 1994-09-16 AU AU76654/94A patent/AU7665494A/en not_active Abandoned
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6049772A (en) * | 1983-08-29 | 1985-03-19 | Toppan Printing Co Ltd | Packed product of unshelled shellfish |
| JPH0251760B2 (en) * | 1986-06-14 | 1990-11-08 | Reonaado Kurutsu Gmbh Unto Co |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6096817A (en) * | 1997-06-26 | 2000-08-01 | E. I. Du Pont De Nemours And Company | Mixtures of polyimides and elastomers |
| US6328008B1 (en) | 1999-08-03 | 2001-12-11 | Unisia Jecs Corporation | Valve timing control system for internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| AU7665494A (en) | 1995-04-10 |
| WO1995008723A1 (en) | 1995-03-30 |
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