JPH07259876A - Power transmitting shaft coupling and power transmitting intermediate shaft - Google Patents

Abstract

PURPOSE:To improve smoothness of transmitting torque and durability by preventing generation of a noise, in a shaft connecting part of transmitting the torque, in this invention. CONSTITUTION:Protruding bodies 12a to 12c provided with gear teeth 28 and recessed parts 14a to 14c are provided in an end face of a coupling 10a connected to a shaft. Protruding bodies 16a to 16c having gear teeth 34 and recessed parts 18a to 18c are provided in also an end face of a coupling 10b connected to a mate shaft. The protruding body 12a of the coupling 10a is fitted to the recessed part 18c of the coupling 10b with a clearance provided, and the protruding body 12b is fitted to the recesed part 18a with a clearance provided. A belt 24 having gear teeth 26, meshed with the gear teeth 28, 34, is wound to peripheral surface of the engaged coupling 10a, 10b.

Description

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

【０００１】[0001]

【産業上の利用分野】本発明は、動力伝達用軸継ぎ手に
関し、特に軸回転時における振動及び伝達ロスの低減
と、継ぎ手の耐用年数を向上させる動力伝達用軸継ぎ手
及び動力伝達用中間軸に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission shaft joint, and more particularly to a power transmission shaft joint and a power transmission intermediate shaft for reducing vibration and transmission loss during shaft rotation and improving the service life of the joint. .

【０００２】[0002]

【従来技術】モータ等の機械的回転力を、他の回転軸等
に伝達させるために利用される動力伝達用軸継ぎ手の従
来例を図面を参照して説明する。図９、図１０は実公昭
５９−１９１４５９に開示されている考案の斜視図及び
横断面図である。駆動軸１００には、図示しないモータ
が連結されており、回転力が駆動軸１００に加えられ
る。2. Description of the Related Art A conventional example of a power transmission shaft coupling used for transmitting a mechanical rotational force of a motor or the like to another rotational shaft or the like will be described with reference to the drawings. 9 and 10 are a perspective view and a cross-sectional view of the device disclosed in Japanese Utility Model Publication No. 59-191459. A motor (not shown) is connected to the drive shaft 100, and a rotational force is applied to the drive shaft 100.

【０００３】この駆動軸１００の軸端面には、図９に示
されているように、直径方向に２等分され、Ｌ字型の連
結部を構成する切欠段部１１０が設けられている。駆動
軸１００の連結部と同じような連結部が設けられた中間
軸１０４が、この駆動軸１００に連結されている。そし
て、駆動軸１００と中間軸１０４の連結部分全体を覆う
ように、スライドリング１０６ａが巻装されている。As shown in FIG. 9, the shaft end surface of the drive shaft 100 is provided with a notch step portion 110 which is divided into two equal parts in the diameter direction and constitutes an L-shaped connecting portion. An intermediate shaft 104 provided with a connecting portion similar to the connecting portion of the drive shaft 100 is connected to the drive shaft 100. A slide ring 106a is wound so as to cover the entire connecting portion between the drive shaft 100 and the intermediate shaft 104.

【０００４】また、中間軸１０４の他端には、スライド
リング１０６ｂ及びＬ字型の連結部によって、回転軸１
０２が係合されており、これによって、駆動軸１００の
回転力が、中間軸１０４を介して、回転軸１０２に伝達
される。尚、駆動軸１００及び回転軸１０２それぞれ
の、中間軸１０４との連結部近傍には、段差１１２ａ、
１１２ｂが設けられているとともに、中間軸１０４にコ
イルばね１０８が巻装されている。このコイルばね１０
８によって、各スライドリング１０６ａ、１０６ｂが段
差１１２ａ、１１２ｂ方向に圧接される。At the other end of the intermediate shaft 104, a slide ring 106b and an L-shaped connecting portion are used to form the rotary shaft 1
02 is engaged, whereby the rotational force of the drive shaft 100 is transmitted to the rotary shaft 102 via the intermediate shaft 104. It should be noted that steps 112 a,
112b is provided, and the coil spring 108 is wound around the intermediate shaft 104. This coil spring 10
8, the slide rings 106a and 106b are pressed against each other in the direction of the steps 112a and 112b.

【０００５】これにより、各駆動軸１００及び回転軸１
０２と、中間軸１０４との各連結部分が、回転中に外れ
ることを防止される。逆に、各スライドリング１０６
ａ、１０６ｂを、コイルばね１０８の弾性力に抗して、
相対方向に押し込むことで、各軸連結部が露出し、容易
に中間軸１０４を駆動軸１００及び回転軸１０２から外
すことができる。この様に、従来の動力伝達用軸継ぎ手
は、軸の連結を容易に解除できるような、極めて簡単な
構造をしている。As a result, each drive shaft 100 and rotary shaft 1
02 and each connecting portion of the intermediate shaft 104 are prevented from coming off during rotation. Conversely, each slide ring 106
a and 106b against the elastic force of the coil spring 108,
By pushing in the relative direction, each shaft connecting portion is exposed, and the intermediate shaft 104 can be easily removed from the drive shaft 100 and the rotary shaft 102. Thus, the conventional power transmission shaft coupling has an extremely simple structure so that the shaft connection can be easily released.

【０００６】[0006]

【発明が解決しようとする課題】しかしながら、上記の
ような動力伝達用軸継ぎ手では、軸が高速回転や、間断
回転された際、色々な不都合を生じる虞がある。何故な
らば、各軸を機構的に連結する限り、駆動軸１００の回
転中心線と、中間軸１０４の回転中心線とを完全に一致
させることは不可能に近い。この為、駆動軸１００が高
速で回転された場合、上記回転中心線の不一致により、
中間軸１０４が偏心して回転されることになる。However, in the power transmission shaft coupling as described above, various inconveniences may occur when the shaft is rotated at high speed or intermittently rotated. Because, as long as the shafts are mechanically connected, it is almost impossible to completely match the rotation center line of the drive shaft 100 and the rotation center line of the intermediate shaft 104. Therefore, when the drive shaft 100 is rotated at a high speed, due to the disagreement of the rotation center lines,
The intermediate shaft 104 is eccentrically rotated.

【０００７】この偏心回転により、中間軸１０４は回転
円周方向への強い遠心力を受けることになり、駆動軸１
００と中間軸１０４との連結部分が外れやすくなる。さ
らに、スライドリング１０６ａが、コイルばね１０８の
弾性力低下により、駆動軸１００と中間軸１０４との連
結部分から自然にずれた場合、中間軸１０４が外れて飛
翔し、重大な事故を招くことになる。Due to this eccentric rotation, the intermediate shaft 104 receives a strong centrifugal force in the circumferential direction of rotation, and the drive shaft 1
The connecting portion between 00 and the intermediate shaft 104 is easily disengaged. Further, if the slide ring 106a naturally shifts from the connecting portion between the drive shaft 100 and the intermediate shaft 104 due to the decrease in the elastic force of the coil spring 108, the intermediate shaft 104 may fly off and cause a serious accident. Become.

【０００８】特に、駆動軸１００と中間軸１０４とが、
「へ」の字状態で連結されていた場合、高速回転の遠心
力によって、スライドリング１０６ａは、回転径外方
向、即ち連結部から外れる方向に力を受けることとな
り、コイルばね１０８の弾性力より遠心力が勝った場
合、スライドリング１０６ａは容易に、連結部分から外
れてしまう。つまり、上記従来の継ぎ手では、連結され
る軸同士の回転中心線がずれていた場合、軸を高速回転
させることができない。Particularly, the drive shaft 100 and the intermediate shaft 104 are
When the slide ring 106a is connected in the state of "he", the slide ring 106a receives a force in the outer radial direction of the rotation, that is, in the direction away from the connecting portion due to the centrifugal force of the high speed rotation, and the elastic force of the coil spring 108 causes When the centrifugal force is prevailing, the slide ring 106a easily comes off the connecting portion. That is, in the conventional joint described above, when the axes of rotation of the shafts to be coupled are deviated from each other, the shafts cannot be rotated at high speed.

【０００９】また、上記従来例の継ぎ手では、連結部を
密着させていることから、回転中の振動による金属体の
面当たりによって、大きな騒音を発生させる虞がある。
つまり、上記継ぎ手では静粛性を望めないことになる。
加えて、駆動軸の回転開始と停止とを間欠的、且つ急激
に行う用途においては、上記継ぎ手では不向きである。Further, in the joint of the above-mentioned conventional example, since the connecting portion is in close contact, there is a possibility that a large noise may be generated due to the surface contact of the metal body due to the vibration during rotation.
That is, the above-mentioned joint cannot be expected to be quiet.
In addition, the joint is not suitable for the purpose of intermittently and suddenly starting and stopping the rotation of the drive shaft.

【００１０】何故ならば、連結部に間隙が存在した場
合、駆動軸の回転開始に対して、その間隙を埋めるよう
に各軸の切欠段部同士が当たるまで、中間軸が回転せ
ず、回転力伝達にタイムラグを生じることになる。つま
り、駆動軸１００の回転が中間軸１０４へ良好に伝達さ
れない。この様に、従来の動力伝達用軸継ぎ手では様々
な問題を抱えている。Because, when there is a gap in the connecting portion, the intermediate shaft does not rotate until the notched step portions of the respective shafts come into contact with each other so as to fill the gap when the rotation of the drive shaft starts to rotate. There will be a time lag in power transmission. That is, the rotation of the drive shaft 100 is not satisfactorily transmitted to the intermediate shaft 104. As described above, the conventional power transmission shaft coupling has various problems.

【００１１】本発明は、上述した課題を解決するために
なされたものであり、静粛性及び耐久性が高く、且つ高
速回転に耐えうる動力伝達用軸継ぎ手及び動力伝達用中
間軸を提供することを目的とする。The present invention has been made to solve the above-mentioned problems, and provides a power transmission shaft coupling and a power transmission intermediate shaft which have high quietness and durability and can withstand high speed rotation. With the goal.

【００１２】[0012]

【課題を解決するための手段】上記目的を達成するため
に、本発明の第１の動力伝達用軸継ぎ手は、動力が伝達
される第１の継ぎ手の回転する端面より突出する少なく
とも２個の突部からなる第１係合手段と、この第１係合
手段から動力が伝達される第２の継ぎ手の回転する端面
に形成され、上記突部と嵌合する少なくとも２個の凹部
からなる第２係合手段と、上記第１係合手段と第２係合
手段との連結部分の外周に巻装されるベルト手段と、こ
のベルトと、上記第１、第２係合手段とを咬合させる咬
合手段とからなることを特徴とする。In order to achieve the above object, the first power transmission shaft joint of the present invention comprises at least two projecting from the rotating end face of the first power transmission joint. A first engaging means formed of a protrusion and at least two recesses formed on the rotating end surface of the second joint to which power is transmitted from the first engaging means and fitted into the protrusion. 2 engaging means, belt means wound around the outer periphery of the connecting portion between the first engaging means and the second engaging means, and the belt and the first and second engaging means engage with each other And an occlusal means.

【００１３】また、上記突部及び凹部は扇状であり、こ
の突部及び凹部の外形寸法が、上記第１係合手段及び第
２係合手段が上記ベルト手段によって嵌合された際、突
部と凹部同士及び突部同士の間に間隙を有するまたは有
しない寸法とする。Further, the projection and the recess are fan-shaped, and the outer dimensions of the projection and the recess are such that when the first engaging means and the second engaging means are fitted by the belt means. With or without a gap between the recesses and between the protrusions.

【００１４】さらにまた、上記咬合手段が、上記ベルト
手段の内周面及び上記第１、第２係合手段の外周面に均
等に設けられた軸線方向に伸びる微小凹凸とする。Furthermore, the engaging means is a fine unevenness extending in the axial direction which is evenly provided on the inner peripheral surface of the belt means and the outer peripheral surfaces of the first and second engaging means.

【００１５】本発明の第２の動力伝達用軸継ぎ手では、
上記第１の発明で用いる咬合手段を、上記第１係合手段
の突部と第２係合手段の突部との間隙をうめる、上記ベ
ルト手段の内周面に凸設した梁体としたことを特徴とす
る。In the second power transmission shaft coupling of the present invention,
The occlusal means used in the first aspect of the invention is a beam body projecting on the inner peripheral surface of the belt means, which fills the gap between the protrusion of the first engaging means and the protrusion of the second engaging means. It is characterized by

【００１６】本発明の第３の動力伝達用軸継ぎ手は、上
記第１、２係合手段の少なくとも一方の係合手段の基台
部にベルト車又は歯車を設けたことを特徴とする。A third power transmission shaft joint of the present invention is characterized in that a belt wheel or a gear is provided on a base portion of at least one of the first and second engaging means.

【００１７】本発明の第４の動力伝達用中間軸は、上記
第１、２係合手段の何れか一方の係合手段を軸両端それ
ぞれに直接形成し、２本の回転軸の間に介そうさせるこ
とを特徴とする。In the fourth power transmission intermediate shaft of the present invention, one of the first and second engaging means is directly formed at each end of the shaft, and is interposed between the two rotary shafts. It is characterized by doing so.

【００１８】本発明の第５の動力伝達用中間軸は、上記
第１、２係合手段の少なくとも一方の係合手段の基台部
にベルト車又は歯車を設けたことを特徴とする。A fifth power transmission intermediate shaft of the present invention is characterized in that a belt wheel or a gear is provided on a base portion of at least one of the first and second engaging means.

【００１９】[0019]

【作用】これにより、一方の軸の回転力は、その軸に巻
装されている弾性力を持ったベルトを介して他方の軸へ
と伝達される。つまり、一方の軸に設けられた突出体
と、相手軸の突出体との間に間隙があることで、一方の
軸の回転力は最初にベルトに伝達され、さらにベルトに
伝達された回転力が相手軸へと伝達される。また、この
ベルトには弾性力があるので、円滑に回転力が一方の軸
から他方の軸へ伝達される。加えて、軸の連結部同士が
直接当たることが無いので、回転中の連結部同士の当た
りによる騒音が発生しないとともに、連結部分の磨耗が
極めて少ないので、耐久性を向上させることができる。
さらに、複数個の突出体を持った連結部によって２つの
軸を係合させているので、仮に、ベルトが破損しても、
軸同士が直ちに外れることがない。As a result, the rotational force of one shaft is transmitted to the other shaft through the belt having the elastic force wound around the shaft. In other words, since there is a gap between the protrusion provided on one shaft and the protrusion on the other shaft, the rotational force of one shaft is first transmitted to the belt, and then the rotational force transmitted to the belt. Is transmitted to the other axis. Further, since this belt has an elastic force, the rotational force is smoothly transmitted from one shaft to the other shaft. In addition, since the connecting portions of the shaft do not directly contact each other, noise due to the contact between the rotating connecting portions does not occur, and wear of the connecting portions is extremely small, so that durability can be improved.
Further, since the two shafts are engaged by the connecting portion having a plurality of protrusions, even if the belt is damaged,
The axes do not come off immediately.

【００２０】[0020]

【実施例】図１は本発明の動力伝達用軸継ぎ手の構成を
示している。本発明の動力伝達用軸継ぎ手は、継ぎ手１
０ａと、この継ぎ手１０ａと対となる継ぎ手１０ｂ及
び、内周面にギヤ歯２６を備えるベルト２４とから構成
される。図２は、継ぎ手１０ａ、１０ｂ及びベルト２４
を組立てた際の、軸線方向の縦断面図を示す。図３は、
図２に於けるＩ−Ｉ断面図を示している。継ぎ手１０ａ
の端部には、軸線方向から眺めた場合、扇形をした凹み
部１４ａ、１４ｂ、１４ｃと、同じく扇形をした突出体
１２ａ、１２ｂ、１２ｃとが交互に形成されている。突
出体１２ａ〜１２ｃそれぞれの扇中心角２２ａ、２２
ｂ、２２ｃは、略等しいとともに、凹み部１４ａ〜１４
ｃも略等しい中心角を持つ。DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 shows the structure of a power transmission shaft coupling of the present invention. The power transmission shaft joint of the present invention is a joint 1.
0a, a joint 10b forming a pair with the joint 10a, and a belt 24 having gear teeth 26 on its inner peripheral surface. 2 shows the joints 10a, 10b and the belt 24.
FIG. 3 is a vertical cross-sectional view in the axial direction when the is assembled. Figure 3
FIG. 3 is a sectional view taken along line I-I in FIG. 2. Joint 10a
When viewed from the axial direction, fan-shaped recesses 14a, 14b, 14c and fan-shaped protrusions 12a, 12b, 12c are alternately formed at the ends of the. The fan central angles 22a and 22 of the protrusions 12a to 12c, respectively.
b and 22c are substantially equal, and the recessed portions 14a to 14c
c also has substantially the same central angle.

【００２１】これら各突出体１２ａ〜１２ｃそれぞれ
の、各面と面との境、つまり辺６２、６４は所定量の面
取りがなされている。さらに凹み部と突出部との面接触
部５８も所定量の丸みが付けられている。同じように、
継ぎ手１０ｂの端面にも、面取りがされ、略等しい中心
角を持つ突出体１６ａ、１６ｂ、１６ｃ及び、凹み部１
８ａ、１８ｂ、１８ｃが交互に配置形成されている。The boundaries between the surfaces of each of the protrusions 12a to 12c, that is, the sides 62 and 64 are chamfered by a predetermined amount. Further, the surface contact portion 58 between the recessed portion and the protruding portion is also rounded by a predetermined amount. Similarly,
The end faces of the joint 10b are also chamfered, and the protrusions 16a, 16b, 16c having substantially the same central angle and the recess 1 are formed.
8a, 18b and 18c are alternately arranged.

【００２２】この様な継ぎ手１０ａと継ぎ手１０ｂとが
係合されると、継ぎ手１０ａの凹み部１４ａ〜１４ｃ
に、継ぎ手１０ｂの突出体１６ａ〜１６ｃが挿入され
る。つまり、継ぎ手１０ｂの突出体１６ａは継ぎ手１０
ａの凹み部１４ａに、突出体１６ｂは継ぎ手１０ａの凹
み部１４ｂに、突出体１６ｃは継ぎ手１０ａの凹み部１
４ｃにそれぞれ嵌め込まれる。When the joint 10a and the joint 10b are engaged with each other, the recessed portions 14a to 14c of the joint 10a are engaged.
The protrusions 16a to 16c of the joint 10b are inserted into the. That is, the protrusion 16a of the joint 10b is
a, the protrusion 16b is in the recess 14b of the joint 10a, and the protrusion 16c is in the recess 1 of the joint 10a.
4c are fitted respectively.

【００２３】また、継ぎ手１０ｂと係合する継ぎ手１０
ａの外周面には、ベルト２４のギヤ歯２６と咬合するギ
ヤ歯２８が等間隔かつ連続的に設けられている。つま
り、各突出体１２ａ〜１２ｃ及び、凹み部１４ａ〜１４
ｃの底部外周面には、ベルト２４と咬合するギヤ歯２８
がそれぞれ設けられている。Further, the joint 10 that engages with the joint 10b.
Gear teeth 28 that mesh with the gear teeth 26 of the belt 24 are continuously provided at equal intervals on the outer peripheral surface of a. That is, each of the protrusions 12a to 12c and the recessed portions 14a to 14
Gear teeth 28 that mesh with the belt 24 are provided on the outer peripheral surface of the bottom of c.
Are provided respectively.

【００２４】このギヤ歯２８の端、即ち、継ぎ手１０ａ
の外周面中央には、ギヤ歯２８と接するフランジ３２ａ
が設けられている。このフランジ３２ａは、継ぎ手１０
ａとベルト２４とが組み立てられた際、継ぎ手の基台３
０ａ側に、ベルト２４が外れることを防止する。また、
継ぎ手１０ａの回転中心には、軸穴３８ａが継ぎ手１０
ａ全体を貫通するように設けられており、この軸穴３８
ａに回転軸３６ａが挿入される。The ends of the gear teeth 28, that is, the joint 10a
A flange 32a contacting the gear teeth 28 at the center of the outer peripheral surface of the
Is provided. This flange 32a is a joint 10
When a and the belt 24 are assembled, the joint base 3
The belt 24 is prevented from coming off on the 0a side. Also,
A shaft hole 38a is formed at the center of rotation of the joint 10a.
The shaft hole 38 is provided so as to pass through the entire a.
The rotary shaft 36a is inserted into a.

【００２５】この軸穴３８ａの一辺には、軸穴３８ａの
中心線と平行にキー溝５０ａが設けられている。このキ
ー溝５０ａには、軸穴３８ａに挿入される回転軸３６ａ
の外周面に突出するように設けられた長尺体のキー５４
ａが嵌合される。また、基台３０ａには、外周面からこ
のキー溝５０ａまで貫通するネジ穴５２ａと、このネジ
穴５２ａに対して９０度位置がずれたネジ穴５６ａとが
設けられている。このネジ穴５２ａ、５６ａには図示し
ないビスが螺合され、回転軸３６ａに継ぎ手１０ａを固
定することに用いられる。A key groove 50a is provided on one side of the shaft hole 38a in parallel with the center line of the shaft hole 38a. The rotary shaft 36a inserted into the shaft hole 38a is inserted into the key groove 50a.
Long key 54 provided so as to project on the outer peripheral surface of the
a is fitted. Further, the base 30a is provided with a screw hole 52a penetrating from the outer peripheral surface to the key groove 50a, and a screw hole 56a which is displaced by 90 degrees from the screw hole 52a. Screws (not shown) are screwed into the screw holes 52a and 56a, and are used to fix the joint 10a to the rotary shaft 36a.

【００２６】同じく、継ぎ手１０ｂにも、基台３０ｂ外
周面の略中央にフランジ３２ｂが設けられており、しか
も、突出体１６ａ〜１６ｃ及び凹み部１８ａ〜１８ｃの
外周面に、ベルト２４のギヤ歯と咬合するギヤ歯３４が
等間隔に設けられている。さらに継ぎ手１０ｂの回転中
心に、キー溝５０ｂを備える軸穴３８ｂが穿設されてお
り、この軸穴３８ｂに対して基台３０ｂの外周面から、
９０度間隔をあけた２つのネジ穴５２ｂ、５６ｂが設け
られている。Similarly, the joint 10b is also provided with a flange 32b substantially at the center of the outer peripheral surface of the base 30b, and the gear teeth of the belt 24 are provided on the outer peripheral surfaces of the protrusions 16a to 16c and the recessed portions 18a to 18c. Gear teeth 34 that mesh with are provided at equal intervals. Further, a shaft hole 38b having a key groove 50b is formed at the center of rotation of the joint 10b, and the shaft hole 38b is formed from the outer peripheral surface of the base 30b.
Two screw holes 52b and 56b are provided at intervals of 90 degrees.

【００２７】継ぎ手１０ａ、１０ｂの突出体１２ａ〜１
２ｃ、１６ａ〜１６ｃのギヤ歯２８、３４の形成された
外周面は、先端に向うほど全体の径がやや小さくなるテ
ーパー状になっている。これによりベルト２４の位置固
定を安定させることができる。このテーパー部分は突出
体１２ａ〜１２ｃ、１６ａ〜１６ｃの外周面全体または
先端側の半分（一部）に形成される。また、このテーパ
ー部分は突出体１２ａ〜１２ｃ、１６ａ〜１６ｃの中央
円周に沿って、いちばん膨らんだ樽型のようなものであ
ってもよい。Protrusions 12a-1 of the joints 10a, 10b
The outer peripheral surface on which the gear teeth 28, 34 of 2c, 16a to 16c are formed has a taper shape in which the overall diameter becomes slightly smaller toward the tip. This makes it possible to stabilize the position of the belt 24. The tapered portion is formed on the entire outer peripheral surface of the protrusions 12a to 12c and 16a to 16c or on the half (part) on the tip side. Further, the tapered portion may have a barrel shape that is the most expanded along the central circumference of the protrusions 12a to 12c and 16a to 16c.

【００２８】また、図３に示される様に、継ぎ手１０ａ
と継ぎ手１０ｂとが係合され、各突出体１２ａ、１２
ｂ、１２ｃと突出体１６ａ、１６ｂ、１６ｃとが交互に
嵌まり込んだ際、これら各突出体間にそれぞれ間隙２０
ａ〜２０ｆができるように、突出体１２ａ〜１２ｃ及び
突出体１６ａ〜１６ｃそれぞれの扇中心角は定められて
いる。なお、この間隙２０ａ〜２０ｆの寸法の下限は、
本例では継ぎ手外周長の２％であり、上限は１５％程度
である。好ましくは４％前後であるが、継ぎ手１０ａ、
１０ｂに設けられる突出体の数によって調整する。Further, as shown in FIG. 3, the joint 10a
And the joint 10b are engaged with each other, and the protrusions 12a, 12
When the protrusions 16b, 12c and the protrusions 16a, 16b, 16c are alternately fitted, a gap 20 is formed between these protrusions.
The fan central angles of the protrusions 12a to 12c and the protrusions 16a to 16c are determined so that a to 20f can be formed. The lower limit of the size of the gaps 20a to 20f is
In this example, the outer circumference of the joint is 2%, and the upper limit is about 15%. It is preferably around 4%, but the joint 10a,
It is adjusted according to the number of protrusions provided on 10b.

【００２９】つまり、本実施例では、継ぎ手の係合端部
に３個の突出体１２ａ、１２ｂ、１２ｃを設けたが、こ
れ以下の数、例えば、２個としてもよく、これ以上の
数、例えば、４個以上でもよく、その突出体の数量によ
って間隙２０ａ〜２０ｆの寸法を調整する。この間隙２
０ａ〜２０ｆは、継ぎ手外周長の１５％以上、例えば３
０％前後、さらには５０％前後でもよい。このように間
隙２０ａ〜２０ｆが大きいと、両継ぎ手１０ａ、１０ｂ
の軸中心が一致しないとき、この不一致すなわちずれ
を、この間隙２０ａ〜２０ｆが吸収することができる。That is, in the present embodiment, three protrusions 12a, 12b, 12c are provided at the engaging end of the joint, but the number may be less than this, for example, two, or more. For example, the number of protrusions may be four or more, and the dimensions of the gaps 20a to 20f are adjusted according to the number of the protrusions. This gap 2
0a to 20f is 15% or more of the outer circumference of the joint, for example, 3
It may be around 0%, or even around 50%. When the gaps 20a to 20f are large in this way, both joints 10a and 10b are connected.
When the axis centers of the two do not match, this gap or shift can be absorbed by the gaps 20a to 20f.

【００３０】各継ぎ手１０ａ、１０ｂが各回転軸３６
ａ、３６ｂに固定された後、継ぎ手同士を係合させて回
転軸３６ａ、３６ｂをカップリングさせた際、図２に示
す様に、対峙する突出体と凹み部との間に、間隙４８を
有する様にしても良いし、密着させても良い。この間隙
４８は各継ぎ手１０ａ、１０ｂの回転軸３６ａ、３６ｂ
への固定位置で調整できるが、間隙４８があれば、継ぎ
手１０ａ、１０ｂ同士が直接に接触することがなく、回
転中における騒音をより少なくすることができる。加え
て、回転軸３６ａ及び回転軸３６ｂの各回転中心線の整
合性が悪い場合、自ずと間隙４８を設けるように、各継
ぎ手１０ａ、１０ｂの回転軸３６ａ、３６ｂへの固定位
置を調整する必要がある。Each joint 10a, 10b is attached to each rotary shaft 36.
When the joints are engaged with each other and the rotating shafts 36a and 36b are coupled after being fixed to the a and 36b, as shown in FIG. 2, a gap 48 is formed between the confronting protrusion and the recess. It may be provided or may be closely attached. The gap 48 is formed by the rotating shafts 36a and 36b of the joints 10a and 10b.
However, if there is the gap 48, the joints 10a and 10b do not come into direct contact with each other, and noise during rotation can be further reduced. In addition, when the alignment of the rotation center lines of the rotary shaft 36a and the rotary shaft 36b is poor, it is necessary to adjust the fixing positions of the joints 10a and 10b to the rotary shafts 36a and 36b so as to automatically provide the gap 48. is there.

【００３１】また、回転軸に各継ぎ手１０ａ、１０ｂを
固定するには、他に、回転軸に各継ぎ手１０ａ、１０ｂ
を嵌め込み、各継ぎ手１０ａ、１０ｂの中心軸から外周
面にかけて長手方向に延びる切断隙間を形成し、この切
断隙間を連繋するボルトを締め付けることによって、回
転軸に各継ぎ手１０ａ、１０ｂ締め付け固定したりする
など他の種々の手段を講じることができる。In addition, in order to fix the joints 10a and 10b to the rotating shaft, in addition, the joints 10a and 10b to the rotating shaft.
Is fitted to form a cutting gap extending in the longitudinal direction from the central axis of each of the joints 10a and 10b to the outer peripheral surface, and bolts connecting the cutting gaps are tightened to fix the joints 10a and 10b to the rotary shaft. Various other means can be taken.

【００３２】尚、継ぎ手１０ａ、１０ｂの材質として
は、アルミダイキャスト、鋳鉄、鉄鋼等が用いられる。
ベルト２４は、弾性力があり、しかも引っ張り強度の高
い材料で形成されている。材料の一例としては、炭素繊
維やアラミド繊維を混入させた合成ゴム（スチレンブタ
ジエンゴム、ニトリルブタジエンゴム、クロロプレンゴ
ム、プチルゴム、イソプレンゴム等）等がある。また他
にチェーン、無端軌道タイプのような金属製であっても
よいが、弾力性のあるベルト２４に比較して、回転中に
発生する騒音は増加する。As the material of the joints 10a and 10b, aluminum die cast, cast iron, steel and the like are used.
The belt 24 is made of a material having elasticity and high tensile strength. Examples of the material include synthetic rubber (styrene-butadiene rubber, nitrile-butadiene rubber, chloroprene rubber, butyl rubber, isoprene rubber, etc.) in which carbon fibers or aramid fibers are mixed. Alternatively, a metal such as a chain or an endless track type may be used, but noise generated during rotation is increased as compared with the elastic belt 24.

【００３３】本実施例の作用について簡単に説明する。
各継ぎ手１０ａ、１０ｂが、それぞれの回転軸３６ａ、
３６ｂに嵌合された後、継ぎ手１０ａ、１０ｂが、対応
する突出体と凹み部とが対峙するように係合されるとと
もに、その係合部分の外周にベルト２４が巻装されて継
ぎ手１０ａ、１０ｂが連結される。そして、ネジ穴５２
ａ、５２ｂ、５６ａ、５６ｂそれぞれに螺合されたビス
によって、各継ぎ手１０ａ、１０ｂは回転軸３６ａ、３
６ｂに固定される。The operation of this embodiment will be briefly described.
Each joint 10a, 10b has a respective rotary shaft 36a,
After being fitted to the joint 36b, the joints 10a and 10b are engaged so that the corresponding projecting bodies and the recesses face each other, and the belt 24 is wound around the outer periphery of the engaging portion so that the joint 10a, 10b are connected. And the screw hole 52
The joints 10a and 10b are attached to the rotary shafts 36a and 3a by screws that are respectively screwed into a, 52b, 56a and 56b.
It is fixed to 6b.

【００３４】継ぎ手のカップリング終了後、一方の回転
軸、例えば回転軸３６ａから回転力が継ぎ手１０ａに加
えられる。この回転力は、継ぎ手１０ａのギヤ歯２８と
ベルト２４のギヤ歯２６との咬合によって、継ぎ手１０
ａに巻装されているベルト２４に伝達される。さらに、
ベルト２４のギヤ歯２６と継ぎ手１０ｂのギヤ歯３４と
が咬合されているので、ベルト２４に加えられた回転力
は継ぎ手１０ｂに伝達される。つまり、継ぎ手１０ａの
回転力は、弾性力を持ったベルト２４を介して間接的に
継ぎ手１０ｂに伝達され、継ぎ手１０ａから継ぎ手１０
ｂに、回転力が直接伝達されることがない。After the coupling of the joint is completed, a rotational force is applied to the joint 10a from one rotating shaft, for example, the rotating shaft 36a. This rotational force is generated by the engagement of the gear teeth 28 of the joint 10a and the gear teeth 26 of the belt 24 with each other.
It is transmitted to the belt 24 wound around a. further,
Since the gear teeth 26 of the belt 24 and the gear teeth 34 of the joint 10b are in mesh with each other, the rotational force applied to the belt 24 is transmitted to the joint 10b. That is, the rotational force of the joint 10a is indirectly transmitted to the joint 10b through the elastic belt 24, and the joint 10a moves to the joint 10a.
The rotational force is not directly transmitted to b.

【００３５】これは、継ぎ手１０ａ、１０ｂとベルト２
４とが、ギヤ歯２６、２８、３４によって咬合している
とともに、継ぎ手１０ａの各突出体１２ａ〜１２ｃと、
継ぎ手１０ｂの各突出体１６ａ〜１６ｃとの間に間隙２
０ａ〜２０ｆがあり、継ぎ手１０ａと継ぎ手１０ｂとが
直接接触していないことによる。しかも、回転力が弾性
力を持ったベルト２４を介して伝達されることと、金属
体である継ぎ手１０ａ、１０ｂ同士が直接に接触してい
ないことにより、軸の高速回転中に於いて、継ぎ手の金
属体同士が当たることで発生する騒音を防止するができ
る。This is the joint 10a, 10b and the belt 2
4 is engaged with the gear teeth 26, 28, 34, and each of the protrusions 12a to 12c of the joint 10a,
A gap 2 is formed between each of the protrusions 16a to 16c of the joint 10b.
0a to 20f, which is because the joint 10a and the joint 10b are not in direct contact with each other. In addition, since the rotational force is transmitted through the belt 24 having elastic force and the joints 10a and 10b, which are metal bodies, are not in direct contact with each other, the joints are rotated during high speed rotation of the shaft. It is possible to prevent the noise generated when the metal bodies of 2 are hit.

【００３６】加えて、継ぎ手同士が直接接触しないの
で、継ぎ手の金属疲労を減少させ、継ぎ手１０ａ、１０
ｂで構成するカップリングの耐久性を向上させることも
できる。また、回転力の伝達にベルト２４の弾性力を用
いるので、継ぎ手１０ａに繋がる回転軸を間欠的且つ急
激に回転、停止を繰り返させる場合等、回転力の急激な
増減に対して、慣性力によって発生するバックラッシュ
を極力小さくすることができる。つまり、ベルト２４が
ダンパーの働きをする。In addition, since the joints do not come into direct contact with each other, the metal fatigue of the joints is reduced, and the joints 10a, 10
The durability of the coupling formed by b can also be improved. Further, since the elastic force of the belt 24 is used for transmitting the rotational force, when the rotational shaft connected to the joint 10a is intermittently and abruptly rotated and stopped repeatedly, the inertia force can be applied to the sudden increase and decrease of the rotational force. The backlash that occurs can be minimized. That is, the belt 24 functions as a damper.

【００３７】また、突出体１２ａ〜１２ｃと、突出体１
６ａ〜１６ｃとの間に設けた間隙２０ａ〜２０ｆ及び、
ベルト２４の働きにより、継ぎ手１０ａの回転中心軸
と、継ぎ手１０ｂの回転中心軸とがずれたり、傾斜する
ミスアライメントに対しても、継ぎ手間の回転力伝達を
円滑に行うことができる。加えて、回転中に於いて、ベ
ルト２４が何らかの原因により破損しても、継ぎ手１０
ａ、１０ｂ同士の突出体が交互に係合した構造となって
いるので、軸同士の連結が完全に外れることを防止で
き、重大事故の発生を未然に防止できる。Further, the protrusions 12a to 12c and the protrusion 1
Gaps 20a to 20f provided between 6a to 16c and
By the action of the belt 24, the rotational force between the joints can be smoothly transmitted even when the rotational center axis of the joint 10a and the rotational center axis of the joint 10b are misaligned or tilted. In addition, even if the belt 24 is damaged due to some cause during rotation, the joint 10
Since the protrusions of a and 10b are alternately engaged with each other, it is possible to prevent the shafts from being completely disconnected from each other and prevent a serious accident from occurring.

【００３８】第２実施例について説明する。図４は、本
第２実施例で用いる継ぎ手１０ｂの外観図を示す。本第
２実施例では、各継ぎ手に設ける突出体を角錐状体にし
た。つまり、突出体１６ａ、１６ｂ、１６ｃの各半径方
向の面６６を傾斜させ、突出体の付け根から先端に向か
って先細りした構造とする。但し、ギヤ歯３４が設けら
れる外周面は、上記第１実施例と同じように、垂直とし
てある。また、突出体の内周面６８については、傾斜さ
せてもよいし、上記第１実施例と同じように垂直でも良
い。The second embodiment will be described. FIG. 4 is an external view of the joint 10b used in the second embodiment. In the second embodiment, the protrusion provided on each joint has a pyramidal shape. That is, the radial surfaces 66 of the protrusions 16a, 16b, and 16c are inclined so that the protrusions 16a, 16b, and 16c are tapered from the root to the tip. However, the outer peripheral surface on which the gear teeth 34 are provided is vertical as in the first embodiment. Further, the inner peripheral surface 68 of the projecting body may be inclined or may be vertical as in the first embodiment.

【００３９】この様な突出体１６ａ、１６ｂ、１６ｃを
持った継ぎ手１０ｂに嵌合する継ぎ手１０ａの各突出体
１２ａ、１２ｂ、１２ｃも同様の構造をしているものと
する。また、この様な継ぎ手１０ａ、１０ｂの嵌合状態
における、隣り合う突出体同士の隙間、例えば、継ぎ手
１０ａの突出体１２ａと、継ぎ手１０ｂの突出体１６ａ
との隙間を、上記第１実施例における間隙２０ａ〜２０
ｆより大きくさせても良いが、上記第１実施例とほぼ同
じとしても良い。この様に、本第２実施例においては、
各突出体を角錐体形状にすることで、継ぎ手同士を結合
させる際の、組立容易性を得ることができるとともに、
突出体の対衝撃性を高めることができる。It is assumed that the projections 12a, 12b, 12c of the joint 10a fitted into the joint 10b having the projections 16a, 16b, 16c have the same structure. Further, in such a fitting state of the joints 10a and 10b, a gap between adjacent protruding bodies, for example, the protruding body 12a of the joint 10a and the protruding body 16a of the joint 10b.
Are the gaps 20a to 20 in the first embodiment.
It may be larger than f, but may be substantially the same as that in the first embodiment. Thus, in the second embodiment,
By making each projecting body into a pyramidal shape, it is possible to obtain ease of assembly when joining the joints together,
The impact resistance of the protrusion can be improved.

【００４０】なお、上記第１実施例、第２実施例におい
て、各凹み部１４ａ〜１４ｃ、１８ａ〜１８ｃの底部外
周面に、突出体１２ａ等の外周面と同じギヤ歯２８、３
４を持つ扇部材７０を設けたが、フランジ３２ａ、３２
ｂまでの完全な凹みとしても良い。つまり、凹み部１４
ａ〜１４ｃ、１８ａ〜１８ｃをギヤ歯の無い完全な凹み
としても良い。他の点は上記第１実施例と同じである。In the first and second embodiments, the gear teeth 28, 3 which are the same as the outer peripheral surface of the protrusion 12a are formed on the outer peripheral surfaces of the bottoms of the recesses 14a-14c, 18a-18c.
Although the fan member 70 having the number 4 is provided, the flanges 32a, 32
It may be a complete depression up to b. That is, the recess 14
A to 14c and 18a to 18c may be formed as complete depressions without gear teeth. Other points are the same as in the first embodiment.

【００４１】次に第３実施例について説明する。図５
は、本実施例で用いる巻装帯４０の外観図を示してい
る。この巻装帯４０の円周部分には、継ぎ手１０ａ、１
０ｂの外周面を覆う帯４４が設けられている。また、中
央には、円柱状の充填体４２が設けられている。そし
て、充填体４２と帯４４とを繋ぐように、扇形をした梁
体４６が複数個設けられている。尚、巻装帯４０の材質
については、第１実施例と同じ様な弾性力のある材料と
する。Next, a third embodiment will be described. Figure 5
Shows an external view of the winding belt 40 used in this embodiment. On the circumference of the winding band 40, the joints 10a, 1
A band 44 is provided to cover the outer peripheral surface of 0b. Further, a columnar filling body 42 is provided in the center. A plurality of fan-shaped beam bodies 46 are provided so as to connect the filling body 42 and the band 44. The material of the winding belt 40 is the same elastic material as in the first embodiment.

【００４２】図６は、この巻装帯４０を用いて、対とな
る２つの継ぎ手を連結させた際の、軸径方向断面図を示
す。本実施例で用いる継ぎ手１０ａ、１０ｂの形状は、
上記第１実施例と略同じであり、凹み部と突出体とが円
周方向に交互に並ぶ様に設けられている。そして、継ぎ
手１０ａと継ぎ手１０ｂとが組み合わされたとき、各凹
み部に相手方継ぎ手の突出体が挿入される。ただし、継
ぎ手外周面と、帯４４の内周面とには、第１実施例のよ
うなギヤ歯が設けられていない。FIG. 6 shows a sectional view in the axial direction when two joints forming a pair are connected using this winding band 40. The shapes of the joints 10a and 10b used in this embodiment are
This is substantially the same as the first embodiment, and the recesses and the protrusions are provided so as to be alternately arranged in the circumferential direction. Then, when the joint 10a and the joint 10b are combined, the projection of the mating joint is inserted into each recess. However, the outer peripheral surface of the joint and the inner peripheral surface of the band 44 are not provided with gear teeth as in the first embodiment.

【００４３】本第３実施例における突出体間の間隙２０
ａ〜２０ｆは、第１実施例より広くなっており、これら
間隙２０ａ〜２０ｆに巻装帯４０の梁体４６が密着して
嵌め込まれる。さらに、カップリングされた継ぎ手１０
ａ、１０ｂのほぼ中央を充填体４２が占める。また、充
填体４２と各突出体との間に間隙４８ができるよう、充
填体４２の直径が定められている。この様な巻装帯４０
と、対となる２個の継ぎ手１０ａ、１０ｂとを用いて、
２つの軸を連結させた場合、継ぎ手間の回転力の伝達と
緩衝の役目は梁体４２が担うことになる。さらに、帯４
４は２つの継ぎ手が径方向に相対的にずれることを防止
する。The gap 20 between the protrusions in the third embodiment.
The widths a to 20f are wider than those in the first embodiment, and the beam body 46 of the winding band 40 is closely fitted into the gaps 20a to 20f. In addition, the coupling 10
The filling body 42 occupies substantially the center of a and 10b. Further, the diameter of the filling body 42 is determined so that a gap 48 is formed between the filling body 42 and each protrusion. Such a wrapping belt 40
And two joints 10a and 10b that form a pair,
When the two shafts are connected, the beam 42 serves to transmit and buffer the rotational force between the joints. In addition, obi 4
4 prevents the two joints from being displaced relative to each other in the radial direction.

【００４４】本第３実施例では、継ぎ手外周面と帯４４
の内周面にギヤ歯を設けなかったが、第１、２実施例と
同じようにギヤ歯を設けてもよい。さらに、本第２実施
例で用いる継ぎ手の突出体の数を３個に限定するもので
はなく、第１、２実施例と同じように、２個か又は４個
以上の突出体を備えるようにしても良い。他の点は上記
第１実施例または第２実施例と同じである。In the third embodiment, the outer peripheral surface of the joint and the belt 44 are arranged.
Although the gear teeth are not provided on the inner peripheral surface of the above, the gear teeth may be provided as in the first and second embodiments. Furthermore, the number of protrusions of the joint used in the second embodiment is not limited to three, and two or four or more protrusions may be provided as in the first and second embodiments. May be. The other points are the same as those of the first or second embodiment.

【００４５】次に、第４実施例について説明する。図７
は、本第４実施例で用いるベルト２４の外観図を示す。
この図に示すように、ベルト２４内周面に設けるギヤ歯
２６を螺旋状にする。Next, a fourth embodiment will be described. Figure 7
Shows an external view of the belt 24 used in the fourth embodiment.
As shown in this figure, the gear teeth 26 provided on the inner peripheral surface of the belt 24 are spirally formed.

【００４６】図８は、第５実施例を示す。両継ぎ手１０
ａ、１０ｂの先端の回転端面の中央は平坦で互いに当接
しあうようになっている。この当接面８２、８３の両端
には各突出体１２ａ、１２ｂ、１６ａ、１６ｂが蒲鉾型
に突出しており、継ぎ手１０ａ、１０ｂの側方は円形部
分が切欠された切欠部８０ａ、８０ｂ、８１ａ、８１ｂ
となっている。この切欠部８０ａ、８０ｂ、８１ａ、８
１ｂが、上記各凹み部１４ａ〜１４ｃ、１８ａ〜１８ｃ
と同じ働きをしており、この各切欠部８０ａ、８０ｂ、
８１ａ、８１ｂに上記各突出体１２ａ、１２ｂ、１６
ａ、１６ｂが嵌め込まれ、両継ぎ手１０ａ、１０ｂが連
結される。この場合、突出体間１２ａ、１２ｂ、１６
ａ、１６ｂの間隙もかなりある。FIG. 8 shows a fifth embodiment. Double joint 10
The centers of the rotating end faces at the tips of a and 10b are flat and are in contact with each other. Each of the protrusions 12a, 12b, 16a, 16b protrudes in a semi-cylindrical shape at both ends of the abutting surfaces 82, 83, and the joints 10a, 10b are provided with notches 80a, 80b, 81a at the sides of the joints. , 81b
Has become. The notches 80a, 80b, 81a, 8
1b is each of the recessed portions 14a to 14c, 18a to 18c
Has the same function as that of the cutouts 80a, 80b,
81a and 81b have the above-mentioned protrusions 12a, 12b and 16
a and 16b are fitted and both joints 10a and 10b are connected. In this case, between the protrusions 12a, 12b, 16
There is also a large gap between a and 16b.

【００４７】本考案は上記実施例に限定されず、本考案
の趣旨を逸脱しない範囲で種々変更可能である。例え
ば、上記第１、２、３実施例に於いて、２つの軸を連結
させるのに、各軸に継ぎ手１０ａ、１０ｂをビス止めし
て行ったが、この継ぎ手１０ａ、１０ｂ自体を回転軸の
端部に直接形成するようにしても良い。また、上記各実
施例に於いて、継ぎ手１０ａ、１０ｂとベルト２４とを
ギヤ歯２６、２８、３４によって咬合させたが、この咬
合させる手段を本発明はギヤ歯に限定するものでなく、
ギヤ歯２６よりやや大きめの咬合する凹凸であっても良
い。The present invention is not limited to the above embodiment, but various modifications can be made without departing from the spirit of the present invention. For example, in the first, second and third embodiments, the joints 10a and 10b are screwed to the respective shafts in order to connect the two shafts. It may be formed directly on the end portion. Further, in each of the above-mentioned embodiments, the joints 10a, 10b and the belt 24 are engaged with each other by the gear teeth 26, 28, 34. However, the means for engaging the joints is not limited to the gear teeth.
It may be a bite that is slightly larger than the gear tooth 26.

【００４８】さらに、上記各実施例においては、２本の
軸を連結させることのみについて説明してきたが、１本
の中間軸を用いて２本の軸を連結させる場合にも本発明
の継ぎ手を用いることができるのは言うまでもない。つ
まり、中間軸の両端に本発明の継ぎ手をビス止めする
か、直接設ける。そして、この中間軸で連結しようとす
る２本の軸の各端面に、この中間軸の一方の端に設けた
継ぎ手と嵌合する継ぎ手を設ける。そうして、この中間
軸によって２本の軸を連結させる。他の点は上記第１実
施例、第２実施例または第３実施例と同じである。Further, in each of the above embodiments, only the connection of the two shafts has been described. However, even when the two shafts are connected by using one intermediate shaft, the joint of the present invention is connected. It goes without saying that it can be used. That is, the joints of the present invention are screwed or directly provided on both ends of the intermediate shaft. Then, on each end face of the two shafts to be connected by the intermediate shaft, a joint that fits with the joint provided at one end of the intermediate shaft is provided. Then, the intermediate shaft connects the two shafts. The other points are the same as those of the above-mentioned first, second or third embodiment.

【００４９】また、上記第１、２実施例において、継ぎ
手１０ａ、１０ｂの各基台３０ａ、３０ｂ部分にプーリ
を設けても良い。このプーリにベルト２４と別体のベル
トを架け、継ぎ手１０ａ、１０ｂに加えられる回転力を
別の軸に伝達させる。この様にすることで、プーリを回
転軸に新たに設置する必要がなく、部品点数の削減、コ
ストの削減を図ることができる。なお、この基台３０
ａ、３０ｂに設けるプーリにギヤ歯を設けても良い。ま
た、上記各実施例に於いて、継ぎ手１０ａ、１０ｂの回
転軸３６ａ、３６ｂへの固定は、ビス止めとしたが、し
ばりどめとしても良い。In the first and second embodiments, pulleys may be provided on the bases 30a and 30b of the joints 10a and 10b. A belt separate from the belt 24 is hung on this pulley, and the rotational force applied to the joints 10a and 10b is transmitted to another shaft. By doing so, it is not necessary to newly install the pulley on the rotary shaft, and the number of parts and cost can be reduced. In addition, this base 30
Gear teeth may be provided on the pulleys provided on a and 30b. Further, in each of the above-described embodiments, the joints 10a and 10b are fixed to the rotating shafts 36a and 36b with screws, but they may be fixed with screws.

【００５０】[0050]

【発明の効果】以上詳述したように、本発明は、２つの
軸を連結させるのに、外周面にギヤ歯を備える複数個の
扇状突出体を端面に設けた継ぎ手を、その突出体同士が
間隙を持って互いに係合する様に嵌め込むとともに、こ
の継ぎ手の連結部外周に、緩衝の役目をする、内周面に
ギヤ歯備える弾性力を持ったベルトを咬合巻装させた。
従って、一方の軸の回転力は、ベルトを介して他方の軸
へと伝達されるので、軸同士の直接接触による回転中の
騒音を防止できるとともに、直接接触による金属疲労を
防止して耐久性を向上させることができる。さらに、本
発明によれば、巻装させたベルトにより、軸連結部分が
外れることがなく、伝達ロスの少ない静粛性の高い軸連
結手段を提供できるといった効果を呈する。加えて、基
台部にプーリを設け、このプーリに架けたベルトによっ
て、継ぎ手部分から直接他軸へ回転力を伝達させること
ができ、部品点数の削減を図ることができる。As described above in detail, according to the present invention, in order to connect two shafts, a joint having a plurality of fan-shaped protrusions provided with gear teeth on the outer peripheral surface is provided on the end face, and the protrusions are connected to each other. While fitting in such a manner that there was a gap therebetween, the belt having elastic force provided with gear teeth on the inner peripheral surface, which serves as a cushion, was occlusively wound around the outer periphery of the joint portion of this joint.
Therefore, since the rotational force of one shaft is transmitted to the other shaft via the belt, it is possible to prevent noise during rotation due to direct contact between the shafts and to prevent metal fatigue due to direct contact and durability. Can be improved. Further, according to the present invention, it is possible to provide the shaft coupling means that does not disengage the shaft coupling portion due to the wound belt and has a high quietness with less transmission loss. In addition, the base is provided with a pulley, and the belt hung on the pulley allows the rotational force to be directly transmitted from the joint portion to the other shaft, thereby reducing the number of parts.

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

【図１】第１実施例である動力伝達用軸継ぎ手各部材の
斜視図である。FIG. 1 is a perspective view of each member of a power transmission shaft coupling according to a first embodiment.

【図２】第１実施例である動力伝達用軸継ぎ手の軸線方
向縦断面図である。FIG. 2 is a longitudinal sectional view in the axial direction of the power transmission shaft coupling according to the first embodiment.

【図３】第１実施例である動力伝達用軸継ぎ手の軸径方
向水平断面図である。FIG. 3 is a horizontal cross-sectional view in the axial direction of the power transmission shaft coupling according to the first embodiment.

【図４】第２実施例である動力伝達用軸継ぎ手の斜視図
である。FIG. 4 is a perspective view of a power transmission shaft coupling according to a second embodiment.

【図５】第３実施例で用いる巻装帯４０の斜視図であ
る。FIG. 5 is a perspective view of a winding band 40 used in the third embodiment.

【図６】第３実施例である動力伝達用軸継ぎ手の軸径方
向水平断面図である。FIG. 6 is a horizontal cross-sectional view in the axial direction of a power transmission shaft coupling according to a third embodiment.

【図７】第４実施例で用いるベルト２４の外観図であ
る。FIG. 7 is an external view of the belt 24 used in the fourth embodiment.

【図８】第５実施例である動力伝達用軸継ぎ手の斜視図
である。FIG. 8 is a perspective view of a power transmission shaft coupling according to a fifth embodiment.

【図９】従来例の斜視図である。FIG. 9 is a perspective view of a conventional example.

【図１０】従来例の軸線方向縦断面図である。FIG. 10 is a longitudinal sectional view in the axial direction of a conventional example.

【符号の説明】[Explanation of symbols]

１０ａ、１０ｂ…継ぎ手、１２ａ、１２ｂ、１２ｃ…突
出体、１４ａ、１４ｂ、１４ｃ…凹み部、１６ａ、１６
ｂ、１６ｃ…突出体、１８ａ、１８ｂ、１８ｃ…凹み
部、２０ａ〜２０ｆ…間隙、２２ａ、２２ｂ、２２ｃ…
中心角、２４…ベルト、２６、２８…ギヤ歯、３０…基
台、３２ａ、３２ｂ…フランジ、３４…ギヤ歯、３６
ａ、３６ｂ…回転軸、３８ａ、３８ｂ…貫通孔、４０…
巻装帯、４２…充填体、４４…帯、４６…梁体、４８…
間隙、５０ａ、５０ｂ…キー溝、５２ａ、５２ｂ…ネジ
穴、５４ａ、５４ｂ…キー、５６ａ、５６ｂ…ネジ穴、
５８…面接触部、６２、６４…辺、６６…面、６８…内
周面、７０…扇部材10a, 10b ... Joint, 12a, 12b, 12c ... Projection body, 14a, 14b, 14c ... Recessed portion, 16a, 16
b, 16c ... Projection body, 18a, 18b, 18c ... Recessed portion, 20a-20f ... Gap, 22a, 22b, 22c ...
Central angle, 24 ... Belt, 26, 28 ... Gear teeth, 30 ... Base, 32a, 32b ... Flange, 34 ... Gear teeth, 36
a, 36b ... rotary shaft, 38a, 38b ... through hole, 40 ...
Winding belt, 42 ... filling body, 44 ... belt, 46 ... beam body, 48 ...
Gap, 50a, 50b ... Key groove, 52a, 52b ... Screw hole, 54a, 54b ... Key, 56a, 56b ... Screw hole,
58 ... Surface contact portion, 62, 64 ... Side, 66 ... Surface, 68 ... Inner peripheral surface, 70 ... Fan member

Claims (8)

【特許請求の範囲】[Claims] 【請求項１】動力が伝達される第１の継ぎ手の回転する
端面より突出する少なくとも２個の突部からなる第１係
合手段と、 この第１係合手段から動力が伝達される第２の継ぎ手の
回転する端面に形成され、上記突部と嵌合する少なくと
も２個の凹部からなる第２係合手段と、 上記第１係合手段と第２係合手段との連結部分の外周に
巻装されるベルト手段と、 このベルトと、上記第１、第２係合手段とを咬合させる
咬合手段とからなることを特徴とする動力伝達用軸継ぎ
手。Claim: What is claimed is: 1. A first engagement means comprising at least two protrusions projecting from a rotating end surface of a first joint to which power is transmitted, and a second engagement means to which power is transmitted from the first engagement means. A second engaging means formed on the rotating end surface of the joint of (1) and formed of at least two recesses that fit with the protrusion, and an outer periphery of a connecting portion of the first engaging means and the second engaging means. A power transmission shaft coupling, comprising: a belt means wound around the belt means; and an engaging means for engaging the belt with the first and second engaging means. 【請求項２】上記突部及び凹部は扇状であり、この突部
及び凹部の外形寸法が、上記第１係合手段及び第２係合
手段が上記ベルト手段によって嵌合された際、突部と凹
部同士及び突部同士の間に間隙を有するまたは有しない
寸法であることを特徴とする請求項１記載の動力伝達用
軸継ぎ手。2. The projection and the recess are fan-shaped, and the outer dimensions of the projection and the recess are such that when the first engaging means and the second engaging means are fitted by the belt means. The shaft coupling for power transmission according to claim 1, characterized in that it has a size with or without a gap between the recesses and between the projections. 【請求項３】上記咬合手段が、上記ベルト手段の内周面
及び上記第１、第２係合手段の外周面に均等に設けられ
た軸線方向に伸びる微小凹凸であることを特徴とする請
求項１又は２記載の動力伝達用軸継ぎ手。3. The occlusal means is a minute unevenness extending in the axial direction which is evenly provided on the inner peripheral surface of the belt means and the outer peripheral surfaces of the first and second engaging means. A shaft coupling for power transmission according to item 1 or 2. 【請求項４】上記咬合手段が、上記第１係合手段の突部
と第２係合手段の突部との間隙をうめる、上記ベルト手
段の内周面に凸設した梁体であることを特徴とする請求
項１又は２記載の動力伝達用軸継ぎ手。4. The occlusal means is a beam body projecting on the inner peripheral surface of the belt means for filling the gap between the projection of the first engaging means and the projection of the second engaging means. The shaft coupling for power transmission according to claim 1 or 2. 【請求項５】上記第１、２係合手段の少なくとも一方の
係合手段の基台部にベルト車又は歯車を設けたことを特
徴とする請求項１、２、３、又は４記載の動力伝達用軸
継ぎ手。5. The power according to claim 1, 2, 3, or 4, wherein a belt wheel or a gear is provided on a base portion of at least one of the first and second engaging means. Transmission shaft coupling. 【請求項６】上記第１、２係合手段の何れか一方の係合
手段を軸両端それぞれに直接形成し、２本の回転軸の間
に介そうさせることを特徴とする動力伝達用中間軸。6. An intermediate portion for power transmission, characterized in that either one of the first and second engaging means is directly formed on both ends of the shaft and is interposed between two rotary shafts. axis. 【請求項７】上記第１、２係合手段の少なくとも一方の
係合手段の基台部にベルト車又は歯車を設けたことを特
徴とする請求項６記載の動力伝達用中間軸。7. The intermediate shaft for power transmission according to claim 6, wherein a belt wheel or a gear is provided on a base portion of at least one of the first and second engaging means. 【請求項８】上記両継ぎ手の先端の回転端面の中央は平
坦で互いに当接しあい、両継ぎ手の上下より上記突部が
突出し、継ぎ手の側方は切欠されて切欠部となってお
り、この切欠部に上記各突部が嵌め込まれることを特徴
とする請求項１記載の動力伝達用軸継ぎ手。8. The center of the rotary end faces of the ends of the joints are flat and abut against each other, the projections project from the upper and lower sides of the joints, and the sides of the joints are notched to form notches. The power transmission shaft coupling according to claim 1, wherein each of the protrusions is fitted into the notch.