JP5499416B2 - C-ring belt clutch. - Google Patents

C-ring belt clutch. Download PDF

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JP5499416B2
JP5499416B2 JP2010030399A JP2010030399A JP5499416B2 JP 5499416 B2 JP5499416 B2 JP 5499416B2 JP 2010030399 A JP2010030399 A JP 2010030399A JP 2010030399 A JP2010030399 A JP 2010030399A JP 5499416 B2 JP5499416 B2 JP 5499416B2
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今戸啓二
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国立大学法人 大分大学
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本発明は、Ｃリング型ベルト式クラッチに関するものである。   The present invention relates to a C-ring type belt clutch.

ベルト式クラッチは一般にエンドレスベルトを原動軸に装着した駆動プーリと従動軸に装着した従動プーリにルーズにかけて、このプーリ間に進退プーリを設けてルーズ状のベルトにテンションを与えて従動プーリを回転させ、そのテンション解除によりもとのルーズ状に戻して従動プーリの回転を停止させるものがほとんどであり、構造的に複雑で且つベルトの緊張・弛緩による摩耗損傷が激しく早期に損傷し交換を余儀なくされるものが多い。 In general, a belt-type clutch is loosely applied to a drive pulley with an endless belt attached to a driving shaft and a driven pulley attached to a driven shaft, and an advancing / retreating pulley is provided between the pulleys to apply tension to the loose belt and rotate the driven pulley. In most cases, the tension is released to stop the rotation of the driven pulley by releasing the tension, which is structurally complex and wear damage due to the tension and relaxation of the belt is severely damaged and must be replaced early. There are many things.

本発明は、構造的に簡易堅牢で且つベルトの緊張・弛緩による摩耗損傷を防止しその寿命を長期にわたって維持するＣリング型ベルト式クラッチを提供するものである。   The present invention provides a C-ring type belt-type clutch that is structurally simple and robust, prevents wear damage due to belt tension and relaxation, and maintains its life for a long period of time.

本発明は上記目的を満足するＣリング型ベルト式クラッチであり、その特徴とするところは、次の(1)〜(２)にある。   The present invention is a C-ring belt type clutch that satisfies the above object, and the features thereof are the following (1) to (2).

(1)、原動軸に固定したパワーリング内の中央部に従動軸を位置させ、
パワーリング内周面と従動軸外周面間に回転伝達巻きベルトと同巻きベルトの巻内に摩擦Ｃリングを配置し、
前記回転伝達ベルトの先端部は摩擦Ｃリングに接続し、前記回転伝達ベルトの後端部をパワーリングに連結し、
前記摩擦Ｃリングは内周面長を前記従動軸の外周面長より短くし、巻きベルトの巻締めにより従動軸の外周面に沿って密着し、巻きベルトの巻締開放により離間可能にし、
前記従動軸のパワーリング外の外周部にその軸方向に平行移動して摩擦Ｃリングの側面に当接離間可能なスライダーを設けた
ことを特徴とするＣリング型ベルト式クラッチ。 (1) Position the driven shaft in the center of the power ring fixed to the driving shaft,
A friction C-ring is disposed between the inner periphery of the power ring and the outer periphery of the driven shaft and the rotation transmission winding belt and the winding belt.
The front end portion of the rotation transmission belt is connected to a friction C ring, the rear end portion of the rotation transmission belt is connected to a power ring,
The friction C-ring has an inner peripheral surface length shorter than an outer peripheral surface length of the driven shaft, closely contacts the outer peripheral surface of the driven shaft by winding the winding belt, and can be separated by releasing the winding belt.
A C-ring type belt-type clutch characterized in that a slider capable of abutting and separating from the side surface of the friction C-ring is provided on the outer peripheral portion of the driven shaft outside the power ring.

(2)、原動軸に固定したパワーリング内の中央部に従動軸を位置させ、
パワーリング周面と従動軸外周面間に回転伝達巻きベルトを、同巻きベルトの巻内に摩擦Ｃリングを各々配置し、
前記回転伝達ベルトはその先端部を摩擦Ｃリングに接続し後部側を複数に分岐してその各分岐端部をパワーリングに所定間隔を置いて連結し、
前記摩擦Ｃリングは内周面長を前記従動軸の外周面長より短くし且つ巻きベルトの巻締めにより従動軸の外周面に沿って密着すると共に巻きベルトの巻締開放により離間可能にし、
前記従動軸のパワーリング外の外周部にその軸方向に平行移動して摩擦Ｃリングの側面に当接離間可能にしたスライダーを設けた
ことを特徴とするＣリング型ベルト式クラッチ。 (2) Position the driven shaft in the center of the power ring fixed to the driving shaft,
A rotation transmission winding belt is disposed between the power ring peripheral surface and the driven shaft outer peripheral surface, and a friction C ring is disposed in the winding of the winding belt,
The rotation transmission belt has a front end connected to a friction C-ring, a rear side is branched into a plurality, and each branch end is connected to a power ring at a predetermined interval,
The friction C-ring has an inner peripheral surface length shorter than an outer peripheral surface length of the driven shaft, and is closely attached along the outer peripheral surface of the driven shaft by tightening of the winding belt, and can be separated by releasing the winding belt.
A C-ring type belt-type clutch characterized in that a slider is provided on the outer peripheral portion of the driven shaft outside the power ring so as to be able to abut on and separate from the side surface of the friction C-ring in the axial direction.

本発明のＣリング型ベルト式クラッチは、上記構成の如くコンパクトで簡易堅牢な構造にすることができる。
本発明のＣリング型ベルト式クラッチは、トリガ−ピンをＣ型をした開口部を有する前記摩擦Ｃリングに置換したものである。回転伝達ベルトの先端は摩擦Ｃリングに連結している。クラッチを連結する場合は，トリガ−ピンと同様にスライダ−を摩擦Ｃリングの側面に軽く接触させる。すると摩擦Ｃリングは、従動軸と同じ回転速度になろうとして瞬時に低速化し，その分、回転伝達ベルトを外周面に巻き付けて自己巻締め上げ状態になり摩擦Ｃリングは弾性変形する。これで摩擦Ｃリングの開口部は小さくなり、摩擦Ｃリングの内周面は従動軸の外周面に強く摩擦結合してトルクは従動軸に伝達される。パワ−リングの回転速度が従動軸の回転速度より遅くなれば、ベルト張力は消滅して、摩擦Ｃリングは弾性力のために開口部は広がり，クラッチが切断された状態になる。
この作用によりトルクを伝える摩擦部は、従動軸外周面と摩擦Ｃリング内周面との面接触部になるので、回転伝達ベルトは、摩擦Ｃリングの巻締め・巻解除の際の緊張・弛緩力を受けるのみで摩耗による損傷は殆ど無く回転伝達ベルトの寿命を長期にわたって維持できる。また回転伝達ベルトのパワ−リングと接合する後部側を複数に分岐して、その各分岐端部をパワーリング内周部に所定間隔を置いて連結することにより、パワ−リングと従動軸の軸芯間にオフセットがある場合でも、軸芯オフセットに伴う従動軸の軸速度の変動が平滑化されて高位に安定したトルク伝導が可能になる。 The C-ring type belt clutch of the present invention can have a compact, simple and robust structure as described above.
In the C-ring type belt clutch of the present invention, the trigger pin is replaced with the friction C-ring having a C-shaped opening. The tip of the rotation transmission belt is connected to the friction C ring. When the clutch is connected, the slider is brought into light contact with the side surface of the friction C-ring in the same manner as the trigger pin. Then, the friction C-ring is instantaneously reduced in speed to reach the same rotational speed as that of the driven shaft, and the rotation transmission belt is wound around the outer peripheral surface, and the friction C-ring is in a self-winding state, and the friction C-ring is elastically deformed. As a result, the opening of the friction C-ring is reduced, the inner peripheral surface of the friction C-ring is strongly frictionally coupled to the outer peripheral surface of the driven shaft, and torque is transmitted to the driven shaft. If the rotational speed of the power ring becomes slower than the rotational speed of the driven shaft, the belt tension disappears, and the friction C-ring opens due to the elastic force, and the clutch is disengaged.
Because of this action, the frictional portion that transmits torque becomes a surface contact portion between the outer peripheral surface of the driven shaft and the inner peripheral surface of the friction C-ring. Therefore, the rotation transmission belt is tensioned / relaxed when the friction C-ring is tightened / unrolled. It is possible to maintain the life of the rotation transmission belt for a long time with almost no damage due to wear only by receiving a force. Further, the rear side of the rotation transmission belt joined to the power ring is branched into a plurality of parts, and each branch end is connected to the inner peripheral part of the power ring at a predetermined interval, so that the power ring and the driven shaft are connected. Even when there is an offset between the cores, fluctuations in the shaft speed of the driven shaft caused by the shaft core offset are smoothed, and stable torque transmission at a high level is possible.

本発明の実施例１の概略を示す斜視説明図である。It is a perspective explanatory view showing the outline of Example 1 of the present invention. 実施例１の要部の側断面説明図(1)でありクラッチを切った状態を示し、(1)の矢視Ａ−Ａからの切断面説明図(2)を示す。It is side sectional explanatory drawing (1) of the principal part of Example 1, shows the state which disconnected the clutch, and shows cut surface explanatory drawing (2) from arrow AA of (1). 実施例１の要部の側断面説明図(1)でありクラッチを入れた状態を示し、(1)の矢視Ｂ−Ｂからの切断面説明図(2)を示す。It is side sectional explanatory drawing (1) of the principal part of Example 1, shows the state which put the clutch, and shows cut surface explanatory drawing (2) from arrow BB of (1). 本発明の実施例2の要部の切断面説明図であり、クラッチを切った状態を(1)に示し、クラッチを入れた状態を(2)に示す。FIG. 6 is a cross-sectional explanatory view of a main part of Embodiment 2 of the present invention, in which a state where the clutch is disengaged is shown in (1), and a state where the clutch is engaged is shown in (2). 本発明の実施例１と実施例２における従動軸の一回転中の軸の角度変化を示すグラフ。The graph which shows the angle change of the axis | shaft in one rotation of the driven shaft in Example 1 and Example 2 of this invention.

本発明を実施するための最良の形態は以下に示す実施例により詳細に説明する。 The best mode for carrying out the present invention will be described in detail with reference to the following examples.

実施例１のＣリング型ベルト式クラッチを、図１、図２(1)、(2)及び図３(1)、(2)に示す。
図１は本発明の実施例１の概略を示す斜視説明図であり、図２(1)は、実施例１の要部の側断面説明図でありクラッチを切った状態を示し、図２(2)は、図２(1)の矢視Ａ−Ａからの切断面説明図を示す。
図３(1)は、図２の状態からクラッチを入れた状態の側断面説明図であり、図３(2)は、図３(1)の矢視Ｂ−Ｂからの切断面説明図を示す。
図１〜図３において、実施例１のＣリング型ベルト式クラッチは、原動軸100と従動軸200間に、原動軸100と一体的に連結した筒状のパワーリング300と、回転伝達巻きベルト400と、ベルト400幅より大きい幅にした摩擦Ｃリング500と、スライダー600とからなる。 The C-ring belt type clutch of Example 1 is shown in FIGS. 1, 2 (1), 2 and 3 (1), 3 (2).
FIG. 1 is a perspective explanatory view showing an outline of the first embodiment of the present invention, and FIG. 2 (1) is a side sectional explanatory view of a main part of the first embodiment, showing a state in which the clutch is disengaged. 2) shows a cut surface explanatory view taken along the line AA in FIG.
3 (1) is a side cross-sectional explanatory view of the state where the clutch is engaged from the state of FIG. 2, and FIG. 3 (2) is a cross-sectional explanatory view taken along the line BB in FIG. 3 (1). Show.
1 to 3, the C-ring type belt clutch of the first embodiment includes a cylindrical power ring 300 integrally connected to the driving shaft 100 between the driving shaft 100 and the driven shaft 200, and a rotation transmission winding belt. 400, a friction C-ring 500 having a width larger than the width of the belt 400, and a slider 600.

回転伝達巻きベルト400は、パワーリング300の周面と摩擦Ｃリング500の外周面との間に配置し、先端部401は摩擦Ｃリング500の外周面に接続し後端部402をパワーリング300の周面に連結する。
摩擦Ｃリング500は、開口部を有するＣ型で回転伝達巻きベルト400と従動軸200外周面間に配置し、内周面長を前記従動軸の外周面長より短くして、巻きベルトの巻締めにより従動軸の外周面に沿って弾性変形することで強く密着して摩擦結合し、巻きベルトの巻締開放により弾性力にて離間可能にしてある。
スライダ−600は前記従動軸200のパワーリング300外の外周部に、その軸方向にのみ平行移動可能に設け図示していないがソレノイド機構やピストンシリンダー機構等の適宜なスライド駆動装置により摩擦Ｃリング500の側面に当接・離間可能にしてある。 The rotation transmission winding belt 400 is disposed between the peripheral surface of the power ring 300 and the outer peripheral surface of the friction C ring 500, the front end 401 is connected to the outer peripheral surface of the friction C ring 500, and the rear end 402 is connected to the power ring 300. Connect to the peripheral surface.
The friction C-ring 500 is a C-shape having an opening, and is disposed between the rotation transmission winding belt 400 and the outer peripheral surface of the driven shaft 200. The inner peripheral surface length is shorter than the outer peripheral surface length of the driven shaft, and the winding of the winding belt is performed. By tightening and elastically deforming along the outer peripheral surface of the driven shaft, it tightly adheres and frictionally couples, and the winding belt can be separated by elastic force by releasing the winding.
The slider 600 is provided on the outer peripheral portion of the driven shaft 200 outside the power ring 300 so as to be movable only in the axial direction. Although not shown, a friction C ring is provided by an appropriate slide driving device such as a solenoid mechanism or a piston cylinder mechanism. The side surface of 500 can be contacted and separated.

以上の構成により、図２(1)、(2)のクラッチを切った状態からクラッチを入れる（連結する）場合は，図3(1)、(2)に示す如く、スライド駆動装置によりスライダ−600を摩擦Ｃリング500の側面に軽く接触させる。すると摩擦Ｃリング500は、従動軸200と同じ回転速度になろうとして瞬時に低速化し，その分、回転伝達ベルト400を外周面に巻き付けて自己巻締め上げ状態になり摩擦Ｃリングは従動軸を締め付けるように弾性変形する。これで摩擦Ｃリング500の開口部は小さくなって摩擦Ｃリングの内周面を従動軸200の外周面に強く密着して摩擦接合されることでトルクを従動軸200に伝達し従動軸200を回転させる。クラッチの接合が一旦完了すれば、スライダ−600を摩擦Cリング500から離間させてもベルト張力の作用している限りクラッチが切れることはない。一方、パワ−リングの回転速度が従動軸の回転速度より遅くなれば、ベルト張力は消滅して、図２(1)、(2)に示す如く、摩擦Ｃリング500は弾性力により開口部が広がり復元して摩擦Ｃリング500と従動軸200との摩擦接合は解除されて、クラッチが切れた状態になる。 With the above configuration, when the clutch is engaged (coupled) from the clutch disengaged state shown in FIGS. 2 (1) and 2 (2), as shown in FIGS. 3 (1) and 3 (2), the slider is driven by the slide drive device. Lightly touch 600 to the side of the friction C-ring 500. Then, the friction C-ring 500 is instantaneously reduced in speed to reach the same rotational speed as that of the driven shaft 200, and the rotation transmission belt 400 is wound around the outer peripheral surface, and the self-clamping state is reached. Elastically deforms to tighten. As a result, the opening of the friction C-ring 500 becomes smaller, and the inner surface of the friction C-ring is in close contact with the outer surface of the driven shaft 200 and is friction-bonded, thereby transmitting torque to the driven shaft 200 and driving the driven shaft 200. Rotate. Once the engagement of the clutch is completed, even if the slider 600 is separated from the friction C-ring 500, the clutch will not be disconnected as long as the belt tension is applied. On the other hand, if the rotational speed of the power ring becomes lower than the rotational speed of the driven shaft, the belt tension disappears and the friction C-ring 500 has an opening due to the elastic force as shown in FIGS. The frictional connection between the friction C-ring 500 and the driven shaft 200 is released by spreading and the clutch is disengaged.

実施例2のＣリング型ベルト式クラッチを図４(1)、(2)に示す。図４(1)はクラッチを切った状態を示し、図４(２)はクラッチが接合された状態を示す。
図４(1)、(2)において、実施例2のＣリング型ベルト式クラッチは、前記実施例１の回転伝達ベルト400を変形した例であり、共通構成部分は同一符号を付してそれらの説明は省略する。
実施例2のＣリング型ベルト式クラッチにおける回転伝達ベルト400は、先端部401を摩擦Ｃリング500の外周面に接続し、後部側を複数に分岐して本例は双尾型に分岐してその各分岐端部402a、402bをパワーリング300の外周部に、ここでは180度の間隔を置いて連結する。
これで、パワ−リング300と従動軸200の軸芯間にオフセットがある場合でも、軸芯オフセットに伴う従動軸200の軸速度の変動が平滑化されて高位に安定したトルク伝導が可能になる。 A C-ring belt type clutch of Example 2 is shown in FIGS. 4 (1) and 4 (2). FIG. 4 (1) shows a state where the clutch is disengaged, and FIG. 4 (2) shows a state where the clutch is engaged.
4 (1) and 4 (2), the C-ring belt type clutch of the second embodiment is an example in which the rotation transmission belt 400 of the first embodiment is modified, and the common components are denoted by the same reference numerals. Description of is omitted.
In the rotation transmission belt 400 in the C-ring type belt clutch of the second embodiment, the front end portion 401 is connected to the outer peripheral surface of the friction C-ring 500, the rear side is branched into a plurality, and this example is branched into a twin tail type. The branch end portions 402a and 402b are connected to the outer peripheral portion of the power ring 300 with an interval of 180 degrees here.
Thus, even when there is an offset between the shaft center of the power ring 300 and the driven shaft 200, the fluctuation of the shaft speed of the driven shaft 200 due to the shaft core offset is smoothed and stable torque conduction at a high level is possible. .

図５に実施例2の双尾型の回転伝達ベルト400と実施例１の単尾型の回転伝達ベルト400による従動軸200の一回転中の従動軸の角度変化を示す。これは従動軸直径30mm、パワ−リング300の外径89mm、軸芯オフセットは8mmとかなり大きなオフセットで実験した結果を示しており、通常の軸継ぎ手では接合することはまず不可能である。一方、このような状態でも本発明のベルト式クラッチではトルク伝達可能であり、本例の双尾型の回転伝達ベルト400を使った場合の従動軸200の回転角度の変化曲線Ｗは、実施例１での単尾型の回転伝達ベルト400による従動軸200の回転角度の変化曲線Ｓと比較して、回転速度が一定であることを示す一点鎖線からの偏差の小さくなっていることが分かる。尚、従動軸200の回転角度を時間で微分した回転角速度で比較しても同様な評価結果が得られる。 FIG. 5 shows a change in the angle of the driven shaft during one rotation of the driven shaft 200 by the double-tailed rotation transmission belt 400 of the second embodiment and the single-tail rotation transmission belt 400 of the first embodiment. This shows the results of experiments with a relatively large offset of a driven shaft diameter of 30 mm, an outer diameter of the power ring 300 of 89 mm, and a shaft center offset of 8 mm. It is impossible to join with a normal shaft joint. On the other hand, even in such a state, the belt type clutch of the present invention can transmit torque, and the change curve W of the rotational angle of the driven shaft 200 when the twin-tail type rotation transmission belt 400 of this example is used is shown in FIG. Compared with the change curve S of the rotation angle of the driven shaft 200 by the single tail type rotation transmission belt 400 at 1, the deviation from the one-dot chain line indicating that the rotation speed is constant is smaller. A similar evaluation result can be obtained by comparing the rotational angle of the driven shaft 200 with a rotational angular velocity obtained by differentiating with time.

本発明のＣリング型ベルト式クラッチは、上記構成の如くコンパクトで簡易堅牢な構造であり、ベルトの緊張・弛緩による摩耗損傷を防止しその寿命を長期にわたって維持するもので、あらゆるベルト式駆動伝達装置に適用することができ、この種の産業に貢献すること多大なものがある。 The C-ring type belt clutch of the present invention has a compact, simple and robust structure as described above, prevents wear damage due to belt tension and relaxation, and maintains its life for a long time. There is a great deal that can be applied to equipment and contribute to this kind of industry.

100：原動軸
200：従動軸
300：パワーリング
400：回転伝達巻きベルト
401：ベルト先端部
402、402a、402b：ベルト後端部
500：摩擦Ｃリング
600：スライダー 100: Driving shaft
200: Driven shaft
300: Power ring
400: Rotation transmission winding belt
401: Belt tip
402, 402a, 402b: Belt rear end
500: Friction C-ring
600: Slider

Claims (2)

原動軸に固定したパワーリング内の中央部に従動軸を位置させ、パワーリング周面と従動軸外周面間に回転伝達巻きベルトを、同巻きベルトの巻内に摩擦Ｃリングを各々配置し、前記回転伝達ベルトはその先端部を摩擦Ｃリングの一端に接続し後端部をパワーリングに連結し、摩擦Ｃリングは内周面長を前記従動軸の外周面長さより短くし且つ巻きベルトの巻締めにより従動軸の外周面に沿って密着すると共に巻きベルトの巻締開放により離間可能にし、前記従動軸のパワーリング外の外周部に、その軸方向に平行移動して摩擦Ｃリングの側面に当接離間可能なスライダーを設け、前記スライダーが前記摩擦Ｃリングの側面に当接すると前記巻きベルトが巻締することを特徴とするＣリング型ベルト式クラッチ。 The driven shaft is positioned in the center of the power ring fixed to the driving shaft, the rotation transmission winding belt is disposed between the power ring peripheral surface and the driven shaft outer peripheral surface, and the friction C ring is disposed in the winding of the winding belt, the rotation transmission belt is connected to the power ring rear portion connected to the tip end of the friction C-ring, friction C ring inner peripheral face length of and wound belt made shorter than the outer peripheral surface length of said driven shaft It is closely attached along the outer peripheral surface of the driven shaft by winding, and can be separated by releasing the winding of the winding belt, and is moved parallel to the axial direction to the outer peripheral portion of the driven shaft outside the power ring. A C-ring type belt-type clutch characterized in that a slider that can be contacted and separated is provided, and the winding belt is tightened when the slider contacts the side surface of the friction C-ring .
「原動軸に固定したパワーリング内の中央部に従動軸を位置させ、パワーリング周面と従動軸外周面間に回転伝達巻きベルトを、同巻きベルトの巻内に摩擦Ｃリングを各々配置し、前記回転伝達ベルトは先端部を摩擦Ｃリングに接続し、後部側を複数に分岐してその各分岐端部をパワーリングに所定間隔を置いて連結し、前記摩擦Ｃリングは内周面長を前記従動軸の外周面長さより短くし且つ巻きベルトの巻締めにより従動軸の外周面に沿って密着すると共に巻きベルトの巻締開放により離間可能にし、前記従動軸のパワーリング外の外周部に、その軸方向に平行移動して摩擦Ｃリングの側面に当接離間可能なスライダーを設け、前記スライダーが前記摩擦Ｃリングの側面に当接すると前記巻きベルトが巻締することを特徴とするＣリング型ベルト式クラッチ。



"Positions the driven shaft in the center of the power ring fixed to the drive shaft, the rotation transmitting wound belt between the power-rings peripheral surface and the driven shaft outer peripheral surface, respectively disposed friction C-ring in the winding of the winding belt The rotation transmission belt has a front end connected to a friction C-ring, a rear side is branched into a plurality, and each branch end is connected to a power ring at a predetermined interval, and the friction C-ring has an inner peripheral surface. the length to allow separated by seaming opening of winding the belt with close contact along the outer peripheral surface of the driven shaft by tightening the shortened and wound-out belt from the outer peripheral surface length of said driven shaft, outside the power ring of the driven shaft Provided on the outer peripheral portion is a slider that can move in parallel with the axial direction of the friction C-ring and contact with and separate from the side surface of the friction C-ring, and the winding belt is wound when the slider contacts the side surface of the friction C-ring. C ring type Belt clutch.


JP2010030399A 2010-02-15 2010-02-15 C-ring belt clutch. Expired - Fee Related JP5499416B2 (en)

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CN105298796B (en) * 2014-06-23 2017-11-21 珠海格力节能环保制冷技术研究中心有限公司 The manufacture method of anti-attrition part in piston compressor and the piston compressor

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