JPH06249257A - Intermittent clutch - Google Patents
Intermittent clutchInfo
- Publication number
- JPH06249257A JPH06249257A JP3826393A JP3826393A JPH06249257A JP H06249257 A JPH06249257 A JP H06249257A JP 3826393 A JP3826393 A JP 3826393A JP 3826393 A JP3826393 A JP 3826393A JP H06249257 A JPH06249257 A JP H06249257A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- pin
- coil spring
- shaft
- fitted
- 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
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Transmission Devices (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、駆動側の回転を、回
転と停止が一定のパターンで繰り返すように従動側に伝
達する間欠クラッチに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an intermittent clutch for transmitting rotation on a driving side to a driven side such that rotation and stop are repeated in a fixed pattern.
【０００２】[0002]
【従来の技術】紙幣支払い機やカードを利用する販売機
等の送り機構には、一方向への間欠回転をする軸が必要
になる。一般にこのような回転軸を得るには、図４及び
図５に示すようにクランク機構とワンウェイクラッチを
組合せた構造のものが利用されている。2. Description of the Related Art A feed mechanism such as a bill payment machine or a vending machine using a card requires a shaft that rotates intermittently in one direction. Generally, in order to obtain such a rotary shaft, a structure in which a crank mechanism and a one-way clutch are combined as shown in FIGS. 4 and 5 is used.
【０００３】この構造のものは、駆動側円板３１と従動
側円板３２を、クランク軸３３と軸受３４、３５を用い
て連結し、従動側円板３２と回転軸３８を、それぞれ逆
方向の回転に対してロックするワンウェイクラッチ３
６、３７を介して連結している。In this structure, the drive side disk 31 and the driven side disk 32 are connected by using the crankshaft 33 and the bearings 34 and 35, and the driven side disk 32 and the rotary shaft 38 are respectively in opposite directions. One-way clutch 3 that locks against rotation
They are connected via 6, 37.
【０００４】上記の方式では、駆動側円板３１が回転す
ると、クランク軸３３の動きによって従動側円板３２が
正逆方向に揺動し、その揺動の動きを各ワンウェイクラ
ッチ３６、３７で切換えて、回転軸３８に一方向の間欠
回転を行わせる。In the above-mentioned method, when the drive side disc 31 rotates, the driven side disc 32 swings in the forward and reverse directions due to the movement of the crankshaft 33, and the one-way clutches 36 and 37 perform the swinging movement. The rotation shaft 38 is switched to cause intermittent rotation in one direction.
【０００５】[0005]
【発明が解決しようとする課題】しかし、上記の構造に
おいては、確かに回転軸３８を間欠回転させることがで
きるが、クランク軸の他に複数のワンウェイクラッチや
軸受等を用いる必要があるために、構造が複雑になり、
小形化が難しい問題がある。However, in the above structure, although the rotary shaft 38 can certainly be intermittently rotated, it is necessary to use a plurality of one-way clutches and bearings in addition to the crankshaft. , The structure becomes complicated,
There is a problem that miniaturization is difficult.
【０００６】また、高速回転になると、クランクの往復
運動に伴う振動が発生し、騒音問題等が生じやすい不具
合がある。Further, when the rotation speed is high, there is a problem that vibrations are generated due to the reciprocating motion of the crank and noise problems are likely to occur.
【０００７】そこで、この発明は、上記の問題を解決
し、クランク機構をなくしてコンパクトな形状で高速回
転を可能とする間欠クラッチを提供することを目的とし
ている。SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide an intermittent clutch which solves the above-mentioned problems and which is capable of high-speed rotation in a compact shape without a crank mechanism.
【０００８】[0008]
【課題を解決するための手段】上記の課題を解決するた
め、この発明は、軸に第１部材と第２部材を回転可能に
取付け、その第１及び第２部材を、両者間で回転差がで
きるように駆動部材に連結し、上記第１部材に対して第
２部材とは反対側の軸の周面に、軸と一体に回転する第
３部材を取付け、上記第１部材に軸の軸線方向に移動可
能なピンを取付け、そのピンと対向するカム部材を第２
部材に取付け、上記第１部材に設けた外径面に、一端が
第３部材に固定したコイルバネを微少なすきまをもって
嵌合させ、上記カム部材に上記ピンが軸線方向に嵌まり
込む凹部を設け、この凹部にピンが嵌まり込んだときピ
ンとコイルバネが離れ、凹部からピンが抜け出たときピ
ンがコイルバネの端部を押圧して縮径させ、コイルバネ
が第１部材の外径面に締り込むように構成したのであ
る。In order to solve the above-mentioned problems, the present invention rotatably mounts a first member and a second member on a shaft, and the first and second members are provided with a rotation difference between them. Is connected to a driving member so that the first member can be rotated integrally with a third member that rotates integrally with the first member. A pin that is movable in the axial direction is attached, and a second cam member that faces the pin is attached.
A coil spring having one end fixed to the third member is fitted to the outer diameter surface of the first member, which is attached to the member, with a minute gap, and the cam member is provided with a recess into which the pin is fitted in the axial direction. , When the pin fits into this recess, the pin and coil spring separate, and when the pin comes out of the recess, the pin presses the end of the coil spring to reduce the diameter, and the coil spring tightens on the outer diameter surface of the first member. It was configured into.
【０００９】また、この発明の第２の手段は、上記第１
部材と第２部材を、駆動歯車と同時に噛み合う歯車で形
成し、その両歯車の歯数を異ならせて第１部材と第２部
材間に回転差ができるようにしたのである。The second means of the present invention is based on the first means.
The member and the second member are formed by gears that mesh with the drive gear at the same time, and the number of teeth of both gears is made different so that a rotation difference can be made between the first member and the second member.
【００１０】さらに、第３の手段は、上記第２部材とカ
ム部材を軸の軸線方向に移動可能に取付け、その第２部
材とカム部材の間に弾性部材を組込んだ構造を採用した
のである。Further, the third means adopts a structure in which the second member and the cam member are attached so as to be movable in the axial direction of the shaft, and an elastic member is incorporated between the second member and the cam member. is there.
【００１１】[0011]
【作用】上記の構造においては、第１部材と第２部材が
回転差をもって回転すると、ピンとカム部材の間で回転
差が生じる。いま、ピンがカム部材の凹部に嵌まり込ん
だ状態で、第１部材と第２部材が回転すると、ピンとカ
ム板の位置がずれてピンが凹部から抜け出し、コイルバ
ネを縮径して第１部材に締り込ませる。これにより、コ
イルバネを介して第３部材が第１部材と共回りし、軸を
回転される。In the above structure, when the first member and the second member rotate with a rotation difference, a rotation difference occurs between the pin and the cam member. Now, when the first member and the second member rotate while the pin is fitted in the recess of the cam member, the position of the pin and the cam plate shifts, the pin comes out of the recess, and the coil spring is contracted to reduce the diameter of the first member. Lock it in. As a result, the third member rotates together with the first member via the coil spring, and the shaft is rotated.
【００１２】さらに、第１部材と第２部材の回転が続く
と、ピンが再び凹部に入り込み、第２部材側に移動す
る。これにより、コイルバネの縮径が戻り、コイルバネ
と第１部材の間にすきまができて第１部材が第３部材に
対し空回りするため、軸の回転が停止する。上記のよう
な作用が繰り返されることにより、軸は第１部材の回転
方向に間欠回転を行う。Further, when the rotation of the first member and the second member continues, the pin re-enters the recess and moves toward the second member. As a result, the reduced diameter of the coil spring returns, and a gap is created between the coil spring and the first member, and the first member idles with respect to the third member, so that the rotation of the shaft is stopped. By repeating the above operation, the shaft performs intermittent rotation in the rotation direction of the first member.
【００１３】また、発明の第２の手段では、駆動歯車が
第１部材と第２部材を同時に回転させると、歯数の少な
い側の部材が他方に対して速く回転し、両者の間に回転
差が生じる。Further, in the second means of the invention, when the drive gear rotates the first member and the second member at the same time, the member having the smaller number of teeth rotates faster than the other member and rotates between them. There is a difference.
【００１４】一方、第３の手段においては、弾性部材が
カム板に軸線方向の荷重を与え、カム部材とピンの間の
遊びを無くす。また、コイルバネやピンに一定以上の力
が加わると、弾性部材が変形し、コイルバネに加わる荷
重を規制する。On the other hand, in the third means, the elastic member applies an axial load to the cam plate to eliminate the play between the cam member and the pin. Further, when a certain amount of force is applied to the coil spring or the pin, the elastic member is deformed and the load applied to the coil spring is regulated.
【００１５】[0015]
【実施例】図１乃至図３は実施例の間欠クラッチを示し
ている。図において、１は従動軸であり、この従動軸１
の周面に、第１歯車２と第２歯車３、及び第３部材とし
てのばねケース４が隣接して取付けられている。1 to 3 show an intermittent clutch according to an embodiment. In the figure, 1 is a driven shaft, and this driven shaft 1
The first gear 2, the second gear 3, and the spring case 4 as the third member are mounted adjacent to the peripheral surface of the.
【００１６】上記ばねケース４は、内径が従動軸１に対
してすきま嵌めされるが、内周側に設けたキー溝５に従
動軸１に圧入されたピン６が嵌合することにより、従動
軸１と一体に回転する。また、ばねケース４は、一方の
端面にボス７を備え、そのボス７の外周に、円形の外径
面８が形成されている。Although the inner diameter of the spring case 4 is closely fitted to the driven shaft 1, the key case 5 provided on the inner peripheral side of the spring case 4 is fitted with a pin 6 press-fitted into the driven shaft 1 so as to be driven. It rotates together with the shaft 1. Further, the spring case 4 is provided with a boss 7 on one end surface thereof, and a circular outer diameter surface 8 is formed on the outer periphery of the boss 7.
【００１７】上記第１歯車２は、内径部分が従動軸１に
すきま嵌めによって回転可能に取付けられ、外周に歯数
Ｚ1 のギヤ歯９が形成されている。また、この第１歯車
２の端面には、ばねケース４に向かって突出するボス１
０が設けられ、そのボス１０の外周に、円形の外径面１
１が形成されている。An inner diameter portion of the first gear 2 is rotatably attached to the driven shaft 1 by a clearance fit, and gear teeth 9 having the number of teeth Z 1 are formed on the outer circumference. The end surface of the first gear 2 has a boss 1 protruding toward the spring case 4.
0 is provided on the outer circumference of the boss 10 and has a circular outer surface 1
1 is formed.
【００１８】この第１歯車２の外径面１１と上記ばねケ
ース４の外径面８は、ほぼ同じ直径で形成され、その両
外径面８、１１にまたがるようにコイルばね１２が組込
まれている。The outer diameter surface 11 of the first gear 2 and the outer diameter surface 8 of the spring case 4 are formed to have substantially the same diameter, and the coil spring 12 is incorporated so as to straddle both outer diameter surfaces 8 and 11. ing.
【００１９】このコイルばね１２は、小径部１３と大径
部１４の２つの内径を持ち、その小径部１３がばねケー
ス４の外径面８に締まり嵌めされて一体に固定されてい
る。また、コイルばね１２の大径部１４は、第１歯車２
の外径面１１の外側に嵌合しており、ばねの自然状態で
は、コイルばね１２の内径と外径面１１との間にすきま
１５が設けられている。The coil spring 12 has two inner diameters, a small diameter portion 13 and a large diameter portion 14, and the small diameter portion 13 is tightly fitted to the outer diameter surface 8 of the spring case 4 and fixed integrally. Further, the large diameter portion 14 of the coil spring 12 is
Is fitted to the outside of the outer diameter surface 11, and in the natural state of the spring, a clearance 15 is provided between the inner diameter of the coil spring 12 and the outer diameter surface 11.
【００２０】また、上記第１歯車２には、コイルばね１
２の小径部１３の平均径をＰ、Ｃ、Ｄとして第１歯車２
を軸線方向に貫通する複数個の貫通孔１６が形成され、
その各貫通孔１６に、それぞれピン１７が移動可能に挿
入されている。The first gear 2 has a coil spring 1
Assuming that the average diameter of the small diameter portion 13 of 2 is P, C, D, the first gear 2
A plurality of through holes 16 penetrating in the axial direction are formed,
A pin 17 is movably inserted into each of the through holes 16.
【００２１】上記第２歯車３は、内径部分が従動軸１に
すきま嵌めにより回転可能に取付けられ、外周に歯数Ｚ
2 のギヤ歯１８が形成されている。このギヤ歯１８は、
外径寸法が第１歯車２のギヤ歯９と同一に形成されてい
るが、歯数は互いに異なる（Ｚ1 ≠Ｚ2 ）ように設定さ
れている。The second gear 3 has an inner diameter portion rotatably attached to the driven shaft 1 by a clearance fit, and has a number of teeth Z on the outer circumference.
Two gear teeth 18 are formed. This gear tooth 18
The outer diameter is formed to be the same as the gear teeth 9 of the first gear 2, but the number of teeth is set to be different (Z 1 ≠ Z 2 ).
【００２２】また、第２歯車３の第１歯車２と向かい合
う端面には、リング状の溝１９が形成され、その溝１９
に、第１歯車２の端面から突出した突起２０と、ピン１
７の端部とが嵌まり込んでいる。A ring-shaped groove 19 is formed on the end surface of the second gear 3 facing the first gear 2, and the groove 19 is formed.
The protrusion 20 protruding from the end face of the first gear 2 and the pin 1
The end of 7 is fitted.
【００２３】上記溝１９は、外周部に軸線方向に延びる
複数の切欠き２１を備えており、その溝１９の奥側に、
カム板２２と、波型ばね２３が組込まれている。The groove 19 is provided with a plurality of notches 21 extending in the axial direction on the outer peripheral portion, and on the inner side of the groove 19,
A cam plate 22 and a wave spring 23 are incorporated.
【００２４】上記カム板２２は、内径部が従動軸１に対
してすきま嵌めされ、外径部に、上記溝１９の切欠き２
１に嵌合する複数の突起２４が設けられており、その突
起２４と切欠き２１の案内により回転不能で軸方向にだ
け移動が可能になっている。An inner diameter portion of the cam plate 22 is closely fitted to the driven shaft 1, and a notch 2 of the groove 19 is formed in an outer diameter portion.
1 is provided with a plurality of protrusions 24, and the protrusions 24 and the notches 21 guide them so that they cannot rotate but can move only in the axial direction.
【００２５】また、カム板２２のピン１７に対向する端
面２５には、ピン１７が軸線方向に嵌まり込む複数個の
凹部２６が形成されている。この凹部２６は、ピン１７
の出没を案内する円錐状のテーパ面２７をもち、その個
数はピン１７と同数か、その正数倍で設定される。Further, a plurality of recesses 26 into which the pins 17 are fitted in the axial direction are formed on the end surface 25 of the cam plate 22 facing the pins 17. The recess 26 is formed by the pin 17
It has a conical taper surface 27 for guiding the appearance and disappearance, and the number thereof is set to the same number as the pin 17 or a positive multiple thereof.
【００２６】上記波型ばね２３は、カム板２２に対して
スラスト荷重を与えるものであり、図２のようにカム板
２２の端面２５にピン１７が当接した状態で、カム板２
２をピン１７に押し付けて両者が密着するように付勢す
る。一方、図１のようにカム板２２の凹所２６にピン１
７が嵌まり込んだ状態では、ピン１７の他端とコイルば
ね１２の端部とが離れるように設定されている。The corrugated spring 23 applies a thrust load to the cam plate 22, and when the pin 17 is in contact with the end surface 25 of the cam plate 22 as shown in FIG.
2 is pressed against the pin 17 and urged so that they are in close contact with each other. On the other hand, as shown in FIG. 1, the pin 1 is inserted into the recess 26 of the cam plate 22.
The other end of the pin 17 and the end of the coil spring 12 are set apart from each other when the pin 7 is fitted.
【００２７】なお、図１において、２８は従動軸１に嵌
合された止め輪であり、この止め輪２８が第２歯車３と
ばねケース４の軸線方向の寸法変化を規制している。ま
た、この止め輪２８の装着状態では、ばねケース４と第
１歯車２及び第２歯車３の間には軸方向にわずかなすき
まから与えられており、第１歯車２と第２歯車３は自由
に相対回転できるようになっている。In FIG. 1, 28 is a retaining ring fitted to the driven shaft 1, and this retaining ring 28 regulates the dimensional change of the second gear 3 and the spring case 4 in the axial direction. In addition, when the retaining ring 28 is attached, a slight clearance is provided between the spring case 4 and the first gear 2 and the second gear 3 in the axial direction, and the first gear 2 and the second gear 3 are separated from each other. It can be rotated relative to each other.
【００２８】また、２９は、外部の動力源によって回転
駆動される駆動歯車であり、この駆動歯車２９は、外周
に歯数Ｚ3 のギヤ歯を有し、そのギヤ歯が第１歯車２と
第２歯車３とに同時に噛み合っている。Further, 29 is a drive gear which is rotationally driven by an external power source, and this drive gear 29 has gear teeth of the number of teeth Z 3 on the outer periphery, and the gear teeth are the same as those of the first gear 2. It meshes with the second gear 3 at the same time.
【００２９】この実施例の間欠クラッチは上記のような
構造であり、次に作用を説明する。The intermittent clutch of this embodiment has the structure as described above, and its operation will be described below.
【００３０】図１は間欠クラッチのＯＦＦの状態を示
す。この状態では、駆動歯車２９が回転すると、第１歯
車２及び第２歯車３が回転するが、ある時間の間は、そ
の回転力がばねケース４に伝わらず、従動軸１は回転し
ない。FIG. 1 shows the intermittent clutch in the OFF state. In this state, when the drive gear 29 rotates, the first gear 2 and the second gear 3 rotate, but for a certain time, the rotational force is not transmitted to the spring case 4, and the driven shaft 1 does not rotate.
【００３１】しかし、一定の時間が経過すると、第１歯
車２の歯数Ｚ1 と第２歯車３の歯数Ｚ2 が異なっている
ため、それぞれの回転数には差が生じる。[0031] However, after a certain amount of time, the number of teeth the first gear 2 Z 1 that the number of teeth Z 2 of the second gear 3 are different, a difference occurs in the respective rotational speed.
【００３２】例えば、駆動歯車２９の回転数をＮ3 とす
ると、第１歯車２および第２歯車３の回転数Ｎ1 とＮ2
の差ΔＮ（＝Ｎ2 −Ｎ1 ）は、 ΔＮ＝（Ｎ3 ×Ｚ3 ）×（Ｚ2 −Ｚ1 ）／（Ｚ1 ×
Ｚ2 ） となる。いま、Ｎ3 ＝２００ｒｐｍ、Ｚ3 ＝Ｚ1 ＝５０
枚、Ｚ2 ＝４９枚とすると、ΔＮ＝−４．０８２ｒｐｍ
となり、第１歯車２と第２歯車３は約１５秒間で１回転
の相対回転をすることになる。For example, assuming that the rotation speed of the drive gear 29 is N 3 , the rotation speeds N 1 and N 2 of the first gear 2 and the second gear 3 are the same.
Difference ΔN (= N 2 −N 1 ) is ΔN = (N 3 × Z 3 ) × (Z 2 −Z 1 ) / (Z 1 ×
Z 2 ). Now, N 3 = 200 rpm, Z 3 = Z 1 = 50
And Z 2 = 49, ΔN = −4.082 rpm
Therefore, the first gear 2 and the second gear 3 make one relative rotation in about 15 seconds.
【００３３】このように第１歯車２と第２歯車３が相対
回転すると、カム板２２の凹部２６とピン１７の位置が
ずれ、凹部２６からピン１７が押し出される。この場
合、ピン１７の数を２個、凹部２６の数を６個とする
と、上記の計算例においては、ピン１７は約１５秒の間
に６回（２．５秒に１回）の割合で凹部２６から押し出
されることになる。When the first gear 2 and the second gear 3 rotate relative to each other in this way, the recesses 26 of the cam plate 22 and the pins 17 are displaced, and the pins 17 are pushed out from the recesses 26. In this case, assuming that the number of the pins 17 is two and the number of the recesses 26 is six, in the above calculation example, the pin 17 has a rate of 6 times (once every 2.5 seconds) in about 15 seconds. Then, it is pushed out from the recess 26.
【００３４】ピン１７が凹部２６から押し出されると、
ピン１７のもう一方の端部はコイルばね１２と接触を始
め、さらに第１歯車２と第２歯車３の差動回転が進む
と、ピン１７がコイルばね１２を強く押し付ける。な
お、この押し付けにおいて、ピン１７やコイルばね１２
に一定以上の力が加わると、波型ばね２３が撓み、コイ
ルばね１２を押し付ける最大荷重が規制される。When the pin 17 is pushed out of the recess 26,
The other end of the pin 17 starts contact with the coil spring 12, and when the differential rotation of the first gear 2 and the second gear 3 further proceeds, the pin 17 strongly presses the coil spring 12. In this pressing, the pin 17 and the coil spring 12
When a force above a certain level is applied to the wave spring 23, the wave spring 23 bends and the maximum load for pressing the coil spring 12 is restricted.
【００３５】上記の場合、コイルばね１２の巻き方向を
左向きとし、第１歯車２の回転方向をばねケース４に向
かって右回転とすれば、コイルばね１２の端面はピン１
７との摩擦力で捩じりトルクを受け、直径が小さくなる
作用を受ける。このため、第１歯車２の回転が続くと、
コイルばね１２の大径部１４は縮径して図２に示すよう
に第１歯車２の外径面１１に密着する。In the above case, if the winding direction of the coil spring 12 is leftward and the rotation direction of the first gear 2 is rightward toward the spring case 4, the end surface of the coil spring 12 is pin 1.
Due to the frictional force with 7, the torsional torque is applied and the diameter is reduced. Therefore, if the rotation of the first gear 2 continues,
The large-diameter portion 14 of the coil spring 12 is reduced in diameter and comes into close contact with the outer diameter surface 11 of the first gear 2 as shown in FIG.
【００３６】この状態から、第１歯車２が回転を続ける
と、コイルばね１２は、両端部の内径が第１歯車２の外
径面１１とばねケース４の外径面８に密着しているた
め、従動軸１に負荷が加わった場合、セルフロックす
る。すなわち、クラッチとして作用し、従動軸１に回転
を伝える。When the first gear 2 continues to rotate from this state, the inner diameters of both ends of the coil spring 12 are in close contact with the outer diameter surface 11 of the first gear 2 and the outer diameter surface 8 of the spring case 4. Therefore, when a load is applied to the driven shaft 1, the driven shaft 1 is self-locked. That is, it acts as a clutch and transmits rotation to the driven shaft 1.
【００３７】一方、上記の状態から、さらに第１歯車２
の回転が続き、ピン１７と凹部２６の位置が一致する
と、ピン１７が凹部２６に嵌まり込み、コイルばね１２
の端面を押すことができなくなる。このため、コイルば
ね１２の大径部１４は図１の状態に戻り、クラッチとし
ての機能を失う。On the other hand, from the above state, the first gear 2
When the position of the pin 17 and the position of the recess 26 coincide with each other, the pin 17 fits into the recess 26, and the coil spring 12
It becomes impossible to push the end face of. Therefore, the large diameter portion 14 of the coil spring 12 returns to the state shown in FIG. 1 and loses the function as a clutch.
【００３８】また、さらに第１歯車１の回転が続くと、
再び図２の状態に戻り、クラッチとして作用する。この
ように空転状態とクラッチの作用状態を繰り返すことに
より、従動軸１の回転と停止が一定のパターンで繰返さ
れ、間欠回転が行われる。When the first gear 1 continues to rotate,
It returns to the state of FIG. 2 again and acts as a clutch. By repeating the idling state and the operating state of the clutch in this way, the rotation and stop of the driven shaft 1 are repeated in a fixed pattern, and intermittent rotation is performed.
【００３９】なお、上記の例において、空転時間とクラ
ッチとして機能する時間の比率は、カム板２２に設ける
凹部２６の数や円周方向の間隔を変えることにより任意
に設定することができる。In the above example, the ratio of the idling time to the time of functioning as a clutch can be arbitrarily set by changing the number of recesses 26 provided in the cam plate 22 or the interval in the circumferential direction.
【００４０】[0040]
【効果】以上のように、この発明は、第１部材と第２部
材間の差動回転とコイルばねの縮径とにより、軸に対す
るクラッチ機能状態と空転状態を制御するので、クラン
ク機構やワンウェイクラッチのような複雑な構造をもつ
必要がなく、コンパクトな形状で一方向の間欠回転をす
る回転を得ることができる。As described above, according to the present invention, the clutch function state and the idling state with respect to the shaft are controlled by the differential rotation between the first member and the second member and the diameter reduction of the coil spring. It is not necessary to have a complicated structure such as a clutch, and it is possible to obtain a rotation that makes intermittent rotation in one direction with a compact shape.
【００４１】また、クランク機能を持たないため、振動
発生の要因がなく、安定した高速回転を可能とする利点
がある。Further, since there is no crank function, there is an advantage that there is no factor of vibration generation and stable high speed rotation is possible.
【図１】実施例の間欠クラッチを示す断面図FIG. 1 is a sectional view showing an intermittent clutch according to an embodiment.
【図２】同上の作用状態を示す断面図FIG. 2 is a sectional view showing an operating state of the above.
【図３】同上の分解斜視図FIG. 3 is an exploded perspective view of the above.
【図４】従来例を示す正面図FIG. 4 is a front view showing a conventional example.
【図５】同上の側面図FIG. 5 is a side view of the above.
１ 従動軸 ２ 第１歯車 ３ 第２歯車 ４ ばねケース ８ 外径面 １１ 外径面 １２ コイルばね １７ ピン ２２ カム板 ２３ 波型ばね ２６ 凹部 ２９ 駆動歯車 1 Driven Shaft 2 First Gear 3 Second Gear 4 Spring Case 8 Outer Diameter Surface 11 Outer Diameter Surface 12 Coil Spring 17 Pin 22 Cam Plate 23 Wave Spring 26 Recess 29 Drive Gear
Claims (3)
付け、その第１及び第２部材を、両者間で回転差ができ
るように駆動部材に連結し、上記第１部材に対して第２
部材とは反対側の軸の周面に、軸と一体に回転する第３
部材を取付け、上記第１部材に軸の軸線方向に移動可能
なピンを取付け、そのピンと対向するカム部材を第２部
材に取付け、上記第１部材に設けた外径面に、一端が第
３部材に固定したコイルバネを微少なすきまをもって嵌
合させ、上記カム部材に上記ピンが軸線方向に嵌まり込
む凹部を設け、この凹部にピンが嵌まり込んだときピン
とコイルバネが離れ、上記凹部からピンが抜け出たとき
ピンがコイルバネを押圧して縮径させ、コイルバネが第
１部材の外径面に締り込むように構成した間欠クラッ
チ。1. A first member and a second member are rotatably attached to a shaft, and the first and second members are connected to a drive member so that a rotational difference between the first and second members can be provided between the first member and the second member. Second
On the peripheral surface of the shaft on the side opposite to the member, a third unit that rotates integrally with the shaft
A member is attached, a pin movable in the axial direction of the shaft is attached to the first member, a cam member facing the pin is attached to the second member, and an outer diameter surface provided on the first member has a third end at the third end. The coil spring fixed to the member is fitted with a slight clearance, and the cam member is provided with a recessed portion into which the pin is fitted in the axial direction. An intermittent clutch configured such that when the pin comes out, the pin presses the coil spring to reduce its diameter, and the coil spring is tightened into the outer diameter surface of the first member.
同時に噛み合う歯車で形成し、その両歯車の歯数を異な
らせて第１部材と第２部材間に回転差ができるようにな
した請求項１に記載の間欠クラッチ。2. The first member and the second member are formed by gears that mesh with the drive gear at the same time, and the number of teeth of both gears is made different so that a rotation difference can be generated between the first member and the second member. The intermittent clutch according to claim 1.
に移動可能に取付け、その第２部材とカム部材の間に弾
性部材を組込んだ請求項１又は２に記載の間欠クラッ
チ。3. The intermittent clutch according to claim 1, wherein the second member and the cam member are attached so as to be movable in the axial direction of the shaft, and an elastic member is incorporated between the second member and the cam member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3826393A JPH06249257A (en) | 1993-02-26 | 1993-02-26 | Intermittent clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3826393A JPH06249257A (en) | 1993-02-26 | 1993-02-26 | Intermittent clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH06249257A true JPH06249257A (en) | 1994-09-06 |
Family
ID=12520440
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3826393A Pending JPH06249257A (en) | 1993-02-26 | 1993-02-26 | Intermittent clutch |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06249257A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0961046A1 (en) * | 1998-05-26 | 1999-12-01 | Electrowatt Technology Innovation AG | Driving device for a positioning element |
-
1993
- 1993-02-26 JP JP3826393A patent/JPH06249257A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0961046A1 (en) * | 1998-05-26 | 1999-12-01 | Electrowatt Technology Innovation AG | Driving device for a positioning element |
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