JP3664486B1 - Rotary valve drive unit - Google Patents
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Abstract
【課題】 入力制限値を越える入力が付加されるとき、入力の伝達を遮断するクラッチ機構を手動駆動源と歯車伝導機構との間に介挿して、入力制限値を越える力の伝達を阻止して、過大な力の付加による装置の損傷を防止する共に、入力が前記制限値以下の場合には力の伝達が自動的に復元し、弁の駆動を行い得るようにした動力伝達手段を提供せんとするものである。
【解決手段】 回転弁の弁駆動用手動アクチュエータのハンドル軸にクラッチ機構を介してハンドル車を取付け、所定値以上の入力がハンドル車を介して付加されるとき、クラッチ機構の連結が解除されて、入力がハンドル軸に伝達されないようにすると共に、入力値が所定値以下のとき、クラッチ機構は連結状態にあるようにしたことを特徴とし、クラッチ機構の断続は、バネの弾発力と両クラッチ部材の当接面に突設された突起の傾斜面による離脱力とのバランスによって行うようにする。
【選択図】 図１
PROBLEM TO BE SOLVED: To prevent transmission of force exceeding an input limit value by inserting a clutch mechanism for interrupting input transmission between a manual drive source and a gear transmission mechanism when an input exceeding an input limit value is applied. In addition to preventing damage to the device due to the addition of excessive force, power transmission means is provided that can automatically restore the force transmission and drive the valve when the input is below the limit value. It is something to be done.
A handle wheel is attached to a handle shaft of a manual actuator for driving a valve of a rotary valve via a clutch mechanism, and when an input of a predetermined value or more is applied via the handle wheel, the connection of the clutch mechanism is released. The clutch mechanism is connected when the input value is less than a predetermined value and the input / output is not transmitted to the handle shaft. This is performed by a balance with the detachment force due to the inclined surface of the protrusion protruding from the contact surface of the clutch member.
[Selection] Figure 1
Description
この発明は、回転弁の駆動装置に関し、更に詳しくは駆動力の伝達を断続するクラッチ機構を備え、一定値以上の駆動力が入力されたとき、駆動力の伝達を遮断して過大な入力による装置の損傷を防止するようにした駆動装置に関する。 The present invention relates to a drive device for a rotary valve, and more particularly, includes a clutch mechanism that intermittently transmits driving force, and when a driving force exceeding a certain value is input, the driving force is interrupted and an excessive input is applied. The present invention relates to a drive device that prevents damage to the device.
従来、バタフライ弁、ボール弁等の回転弁の駆動装置として、手動で回転されるハンドル車と弁棒との間にウォームとウォーム歯車からなる歯車伝導機構を介在させて、手動駆動力で弁棒を回動し、弁の開閉を行うようにした回転弁の駆動装置は公知であり、例えば特許第３０８１８２０号公報等に開示されている。 Conventionally, as a driving device for a rotary valve such as a butterfly valve or a ball valve, a manual transmission is used to interpose a gear transmission mechanism consisting of a worm and a worm gear between a manually rotated handle wheel and a valve stem, and a valve stem with a manual driving force. The rotary valve drive device that rotates the valve to open and close the valve is known, and is disclosed in, for example, Japanese Patent No. 3081820.
かかる公知の駆動装置にあっては、手動でもたらされる歯車伝導機構の出力トルクと歯車伝導機構から弁体駆動のために出力される弁駆動トルクがマッチングした状態で使用されるのが好ましいが、実際には歯車伝導機構への入力トルクが必要とされる弁駆動トルクよりも大きくなっているのが通常である。しかも、入力源が人力である手動装置では、入力トルクの大きさは、非常に大きな個人差を持っており、過大な力が付加されることがあった。このため、ハンドル車、歯車伝導機構、ケーシング等を含む駆動装置に損傷を与えるおそれがあった。 In such a known driving device, it is preferable that the output torque of the gear transmission mechanism manually provided and the valve driving torque output for driving the valve body from the gear transmission mechanism are matched, In practice, the input torque to the gear transmission mechanism is usually larger than the required valve drive torque. Moreover, in a manual device in which the input source is human power, the magnitude of the input torque has a very large individual difference, and an excessive force may be applied. For this reason, there is a risk of damage to the drive device including the handle wheel, the gear transmission mechanism, the casing, and the like.
特に、近年は省資源化、低コスト化等の要請に伴って、駆動装置の小型化や材料の不必要な強度の削減が図られ、駆動装置の出力限界値を出来る限り弁駆動トルクに近づけて使用するために、入力制限値を表記しているが、弁使用の現場では必ずしも入力制限値が遵守されるとは言い得ず、しばしば入力制限値を越えた駆動力が付加され、装置を破損する事故が発生している。 In particular, in recent years, with the demand for resource saving and cost reduction, the drive device has been reduced in size and the unnecessary strength of the material has been reduced, and the output limit value of the drive device has been made as close to the valve drive torque as possible. However, the input limit value cannot always be observed at the site where the valve is used, and a driving force exceeding the input limit value is often added to An accident that breaks has occurred.
この発明は、入力制限値を越える入力が付加されるとき、入力の伝達を遮断するクラッチ機構を手動駆動源と歯車伝導機構との間に介挿して、入力制限値を越える力の伝達を阻止して、過大な力の付加による装置の損傷を防止する共に、入力が前記制限値以下の場合には力の伝達が自動的に復元し、弁の駆動を行い得るようにした動力伝達手段を提供せんとするものである。 In the present invention, when an input exceeding the input limit value is applied, a clutch mechanism that interrupts input transmission is interposed between the manual drive source and the gear transmission mechanism to prevent transmission of force exceeding the input limit value. Power transmission means for preventing damage to the device due to excessive force application and for automatically restoring the force transmission when the input is less than the limit value so that the valve can be driven. It is to be provided.
本発明は、回転弁の弁駆動用手動アクチュエータのハンドル軸に回転方向を一体にして連結された従動側クラッチ部材と、ハンドル車を一体に有し従動側クラッチ部材に回転自在に遊挿される原動側クラッチ部材とでクラッチ機構を構成し、両クラッチ部材を実質的に円板形状に形成し、両クラッチ部材の当接面に互いに噛合する突起を突設し、該突起は円の中心(Ｏ)から放射状に延び上面(Ａ)を平坦とし両側面を傾斜面(Ｅ)とした中心円(ＤＣ)において断面台形を有しており、両クラッチ部材をバネで当接方向に弾発し、バネの弾発力と突起の傾斜角(α)による離脱力とのバランスによって、所定値以上の入力がハンドル車を介して付加されるときクラッチ機構の連結が解除され、逆に入力値が所定値以下のときバネの弾発力でクラッチ機構を連結状態に保持し、前記突起はその放射方向の長さの半分の位置を通る円を突起の中心円(ＤＣ)とし、突起の底面(Ｃ)から突起の高さと隙間(ε)の合計の少なくとも半分の位置と前記中心円(ＤＣ)との交点を通り底面(Ｃ)と平行な平面を中心平面(Ｂ)とし、該中心平面(Ｂ)を起点として上下に傾斜角(α)の傾斜面(Ｅ)を形成すると共に、中心円(ＤＣ)と中心平面(Ｂ)の交点から突起の外径(ＯＤ)側、内径(ＩＤ)側（長さ方向）に傾斜面(Ｅ)を突起の稜線角度(β)と平行に延長し、原動側及び従動側の突起の両傾斜面間及び上面間に隙間(ε)を設けたことを特徴とする。 The present invention relates to a driven side clutch member integrally connected to a handle shaft of a valve drive manual actuator of a rotary valve and a driving wheel integrally having a handle wheel and rotatably inserted into the driven side clutch member. constitute a clutch mechanism in the side clutch member, both clutches member formed in a substantially disk shape, projecting a projection that meshes with each other physician abutment surfaces of both clutch members, 該Tokki the center of the circle (O) has a trapezoidal cross section in the center circle (DC) extending radially from (O) and having a flat upper surface (A) and inclined surfaces (E) on both sides. , the balance between the separation force due to the resilient force of the spring and the collision force inclination angle (alpha), the input of more than Tokoro value is released coupling clutch mechanism when it is added via a hand wheel, the input value conversely The clutch mechanism is activated by the spring force of Held in sintered state, wherein the projection is a circle passing through the half the length of the radial direction centered yen projections (DC), height and gap of the protrusions from the bottom surface of the projection (C) Total of (epsilon) A plane that passes through the intersection of at least half the position and the center circle (DC) and is parallel to the bottom surface (C) is defined as a center plane (B), and the tilt angle (α) is tilted up and down from the center plane (B). The surface (E) is formed, and the inclined surface (E) is projected from the intersection of the center circle (DC) and the center plane (B) to the outer diameter (OD) side and inner diameter (ID) side (length direction) of the protrusion. And a gap (ε) between the inclined surfaces and the upper surface of the driving side and driven side projections .
バネ固定板を、Ｌ字状のスリットに係脱自在な角棒状連結部により従動側クラッチ部材に抜止状態で連結したことを特徴とする。 The spring fixing plate is connected to the driven-side clutch member in a locked state by a square bar-shaped connecting portion that is detachably engageable with the L-shaped slit .
本発明の回転弁の駆動装置によれば、手動ハンドル車と歯車伝導機構との間にクラッチ機構を介挿して、所定値以上の入力トルクを遮断し過大なトルクの伝導を防止してあるので、過大なトルクの付加による装置の損傷を防止することが出来ると共に、入力トルクが所定値以下に低下した場合には直ちにクラッチ機構を連結状態に自動的に復帰させて、駆動力の伝達を行うことが出来、クラッチ機構の作動に手間を必要とせず、しかも安全機構として利用することが出来る。更に、既設のハンドル車に代ってハンドル軸にこの発明のクラッチ機構を取付けるのみで、この発明を既設の回動弁に適用することが出来る。 According to the rotary valve drive device of the present invention, the clutch mechanism is interposed between the manual handle wheel and the gear transmission mechanism to cut off the input torque above a predetermined value and prevent excessive torque conduction. In addition, it is possible to prevent damage to the device due to the addition of excessive torque, and when the input torque drops below a predetermined value, the clutch mechanism is automatically returned to the connected state immediately to transmit the driving force. Therefore, the operation of the clutch mechanism does not require time and can be used as a safety mechanism. Furthermore, the present invention can be applied to the existing rotary valve only by attaching the clutch mechanism of the present invention to the handle shaft instead of the existing handle wheel.
この発明の好ましい実施の形態を、以下に詳細に説明する。この発明は、バタフライ弁、ボール弁等の回転する弁体を備えた回転弁のための手動の駆動装置に関するものであり、手動の入力を発生するハンドル車の如き手動回動手段と、該回動手段の駆動力を弁開閉用の弁棒に伝達するための歯車伝導機構等の動力伝導手段との間に、動力伝達を断続するクラッチ機構を配し、所定値以上の過大な駆動力が伝達されたとき、その伝達を遮断し、歯車伝導機構、ギアケース、ハンドル軸とハンドル車との連結部、弁棒と歯車伝導機構との連結部等の駆動力伝達機構部分の損傷を防止するようにしたことを特徴とする。又、該クラッチ機構は、入力が所定値以下に低下した場合、自動的に復元して駆動力の再接続が行われるようになっていることを特徴とする。更に、この発明の駆動装置は、既設のハンドル車に代ってハンドル軸に取付けることのみの簡単な変更で実現することが出来、特別な部品や器具、或いは工具を必要としないため、既に配管に取付けられている回動弁にも簡単に適用することが可能である。 Preferred embodiments of the present invention will be described in detail below. The present invention relates to a manual drive device for a rotary valve having a rotating valve element such as a butterfly valve, a ball valve, etc., and a manual rotation means such as a handle wheel for generating a manual input; A clutch mechanism for intermittently transmitting power is arranged between the power transmission means such as a gear transmission mechanism for transmitting the driving force of the moving means to the valve rod for opening and closing the valve, and an excessive driving force exceeding a predetermined value is provided. When transmitted, the transmission is cut off to prevent damage to the driving force transmission mechanism such as the gear transmission mechanism, the gear case, the connection portion between the handle shaft and the handle wheel, and the connection portion between the valve stem and the gear transmission mechanism. It is characterized by doing so. Further, the clutch mechanism is characterized in that when the input drops below a predetermined value, the clutch mechanism is automatically restored and the driving force is reconnected. Furthermore, the drive device of the present invention can be realized by a simple change by simply attaching to the handle shaft in place of the existing handle wheel, and does not require any special parts, tools or tools, so that the pipe is already installed. It is also possible to easily apply to a rotary valve attached to.
クラッチ機構は、原動側と従動側のクラッチ部材に回転軌跡に沿って配列され互いに噛合する少なくとも一つの突起を備えている。両クラッチ板は、常時当接する方向に弾発されると共に、前記突起の回転方向に面する面は所定の傾斜角αの斜面に形成されており、原動側クラッチ部材からの入力値が、所定値を越えるとき、傾斜角αによる離脱力がクラッチ部材への弾力的な押付け力よりも大きくなるため、突起の噛合いが解除され、駆動力伝達が遮断されるようになっている。又、入力がゼロ若しくは一定値以下に戻れば、弾発力でクラッチ部材が押付けられるため、突起の噛合が復元し、駆動力の伝達が復活する。すなわち、原動側に付加される入力が、一定値以上若しくは一定値以下において、クラッチが自動的に断続し、駆動力の伝達若しくはその遮断を行うことが出来る。前記傾斜角は、突起の回転方向の一側面だけに設けても良いが、両側面に形成することにより、正逆いずれの回転方向に対しても、前記クラッチの断続を行うことが可能となる。 The clutch mechanism includes at least one protrusion arranged on the driving side and the driven side clutch members along the rotation locus and meshing with each other. Both clutch plates are bulleted in a constantly contacting direction, and the surface facing the rotation direction of the projection is formed as an inclined surface having a predetermined inclination angle α, and an input value from the driving side clutch member is a predetermined value. When the value is exceeded, the detachment force due to the inclination angle α becomes larger than the elastic pressing force against the clutch member, so that the engagement of the protrusion is released and the driving force transmission is interrupted. Further, when the input returns to zero or below a certain value, the clutch member is pressed by the elastic force, so that the engagement of the protrusion is restored and the transmission of the driving force is restored. That is, when the input applied to the driving side is greater than or equal to a certain value or less than the certain value, the clutch is automatically engaged, and the driving force can be transmitted or disconnected. The angle of inclination may be provided only on one side of the rotation direction of the protrusion, but by forming it on both sides, the clutch can be engaged and disengaged in both the forward and reverse rotation directions. .
原動側のクラッチ部材は、ハンドル車と一体的になった略円盤状の部材からなり、歯車伝導機構の入力軸であるハンドル軸に回転自在に遊挿される。又、従動側のクラッチ部材は、ハンドル軸と一体的に回転するように結合される円盤状の部材であり、両クラッチ部材の対向する当接面に互いに噛合する突起が形成され、該突起の噛合若しくは離脱により両クラッチ部材の連結又は非連結が達成される。原動側と従動側のクラッチ部材は、両部材の間に張設されたバネの弾発力を受けて、常時は互いに当接する方向に付勢されており、これにより前記突起は噛合状態に偏位される。入力値が一定値を越えるとき、傾斜角αによる離脱力が発生し突起が傾斜に沿って滑り移動し、バネの弾発力に抗して噛合が解除され、両クラッチ部材は非連結状態に移行する。 The driving-side clutch member is a substantially disk-shaped member integrated with the handle wheel, and is rotatably inserted into the handle shaft that is the input shaft of the gear transmission mechanism. The clutch member on the driven side is a disk-like member that is coupled so as to rotate integrally with the handle shaft. Protrusions that mesh with each other are formed on opposing contact surfaces of both clutch members. The engagement or disengagement of both clutch members is achieved by meshing or disengaging. The driving-side and driven-side clutch members receive the elastic force of the spring stretched between the two members, and are normally biased in the direction in which they abut against each other. Be ranked. When the input value exceeds a certain value, a detachment force due to the inclination angle α is generated, the protrusion slides along the inclination, the meshing is released against the spring force of the spring, and both clutch members are disengaged. Transition.
図６〜８に示すように、突起は、ハンドル軸を中心とする円軌跡に沿って少なくとも一つ、好ましくは所定の角度θの間隔を置いて複数配列され、直径方向に一定の長さＬを有し、外周側は幅広く、内周側を狭くした台円錐形をなしている。図８を参照して、突起の側面、好ましくは両側面が、傾斜角αの斜面に形成される。突起の両側面に傾斜角を設ける場合、一方の傾斜角を他方のそれと異ならせることにより、回転方向に応じて入力値を異ならせることが可能なる。傾斜角αは、５〜４０゜とするのが好ましい。傾斜角が５゜よりも小さいと、離脱力が過小となって実質的に突起の離脱を達成することが不可能となり、クラッチ作用を得ることが出来ない。又、４０゜より大きいと、過大となって僅かな入力でも突起の離脱が行われてしまう不都合がある。突起の数Ｎは、１〜３０程度とし、突起の間隔角度θは、θ＝３６０／Ｎで与えられる。 As shown in FIGS. 6 to 8, at least one protrusion is arranged along a circular locus centering on the handle shaft, preferably at a predetermined angle θ, and has a certain length L in the diameter direction. The outer peripheral side is wide, and the inner peripheral side is narrow and has a trapezoidal shape. Referring to FIG. 8, the side surfaces, preferably both side surfaces, of the protrusion are formed on the inclined surface having the inclination angle α. When providing an inclination angle on both side surfaces of the protrusion, it is possible to make the input value different according to the rotation direction by making one inclination angle different from that of the other. The inclination angle α is preferably 5 to 40 °. If the inclination angle is less than 5 °, the detachment force becomes too small to substantially achieve the detachment of the protrusion, and the clutch action cannot be obtained. On the other hand, if the angle is larger than 40 °, there is an inconvenience that the protrusion is detached even if the input is small. The number N of protrusions is about 1 to 30, and the protrusion interval angle θ is given by θ = 360 / N.
原動側、従動側それぞれの突起の間隔Ｐは、突起の長さＬの中心を通る中心円の直径をＤＣとした場合、次式で与えられる。
Ｐ＝πＤＣ／２Ｎ
The distance P between the protrusions on the driving side and the driven side is given by the following equation when the diameter of the central circle passing through the center of the length L of the protrusion is DC.
P = πDC / 2N
図９，１０に示すように、原動側、従動側共に、等間隔で突起を配置し、突起の噛合、離脱を容易にするために、図８に図示する突起には隙間εを設ける。突起の幅をｂとするとき、該隙間εは、0.05〜0.3ｂ程度が好ましい。隙間εは、突起の傾斜面と上面に設ける。かくして、前記突起の間隔Ｐは、次式の値となる。
Ｐ＝２×（ｂ＋ε）
As shown in FIGS. 9 and 10, protrusions are arranged at equal intervals on both the driving side and the driven side, and a gap ε is provided in the protrusions shown in FIG. 8 in order to facilitate engagement and disengagement of the protrusions. When the width of the protrusion is b, the gap ε is preferably about 0.05 to 0.3b. The gap ε is provided on the inclined surface and the upper surface of the protrusion. Thus, the distance P between the protrusions is a value of the following formula.
P = 2 × (b + ε)
前記した突起の噛合い及び離脱を成立させるために、突起両側面の傾斜角αは、突起下端の円板上面から立ち上がるのではなく、突起の高さの１／２より上方の位置にある中心平面(図８参照)からそれぞれ上下に形成する。すなわち、このクラッチ機構は、隙間εを含む突起の高さの半分の中心平面上で噛み合う構成とする。従って、突起の両側面に形成する角度αの斜面は、中心平面上から上方(ｈ−ε)、下方(ｈ)(円盤の基板方向)に形成される。又、傾斜による側面の形状は、円板中心からの放射状ではなく、中心平面上の突起の稜線角度(β)と幅ｂで平行となる。 In order to establish the engagement and disengagement of the protrusion, the inclination angle α on both side faces of the protrusion is not raised from the upper surface of the disk at the lower end of the protrusion, but at the center above the height of the protrusion. They are formed vertically from the plane (see FIG. 8). That is, the clutch mechanism is configured to mesh on a central plane that is half the height of the protrusion including the gap ε. Therefore, the slopes of the angle α formed on both side surfaces of the protrusion are formed upward (h−ε) and downward (h) (in the direction of the disk substrate) from the center plane. Further, the shape of the side surface due to the inclination is not radial from the center of the disk, but is parallel with the ridge line angle (β) of the protrusion on the center plane and the width b.
すなわち、突起を間隔Ｐで配置し、突起の稜線の角度をβとする。突起は、厚み(高さ)を必要とするため、基準面が必要であり、ここでは突起の稜線を基準平面上に置き、この平面を前述した中心平面と称している。突起には、傾斜面が必要であるため、中心平面は、円板Ｃ上の高さ（＋ｈ）の位置に仮想する。従って、円板Ｃ面上は突起の麓に相当する。又、突起の上面を中心平面から（ｈ−ε）の位置とし、円板Ｃ上からは（２ｈ−ε）の位置となる。突起を形成する際、突起稜線角度βをどこにおくかで突起の幅（上面幅、麓幅）が異なってくる。例えば、上面にβを置くと、突起の麓は上面幅よりｂだけ広くなり、麓にβを置くと上面はｂだけ狭くなる。突起単独では、どこに基準を置いても可能であるが、円板Ｃ上に突起間隔角度θを維持しつつ配置するには、上面又は麓基準では不可能であるため、突起稜線の形成基準を中心平面とした。 That is, the protrusions are arranged at the interval P, and the angle of the ridge line of the protrusion is β . Since the protrusion requires thickness (height), a reference surface is required. Here, the ridge line of the protrusion is placed on the reference plane, and this plane is referred to as the above-described central plane. Since the protrusion requires an inclined surface, the center plane is virtually at a height (+ h) position on the disk C. Therefore, the surface of the disk C corresponds to a ridge of the protrusion. Further, the upper surface of the projection is at a position (h−ε) from the central plane, and from the disk C is at a position (2h−ε). When forming the protrusion, the width of the protrusion (upper surface width, heel width) varies depending on where the protrusion ridge line angle β is placed. For example, placing the β on the upper surface, the foot of the projection becomes large as b from the upper surface width, top placing the β at the foot is b only narrow. The projections alone, but where it is possible at a reference to, to place while maintaining the projection interval angle θ on a circle plate C are the possible with top or foot basis, the formation criterion projection ridge The center plane was used.
突起の傾斜角をα、入力制限値をＦ、必要とされるバネ押さえ力をＱとしたとき、クラッチの嵌合は次の関係となる。従って、押付けバネ力は、Ｑと同等に設定すればよいこととなる。そこで、入力値Ｆが大きくＦ１になると、式(１)より離脱方向力はＱ１となり、Ｆ１はＦより大きく、Ｑ１はＱより大きくなるため、クラッチは離脱する。又、逆に入力を止めるか(Ｆ＝０)、入力をＦより小さなＦ２にすれば、離脱方向力がＱより小さいＱ２となるため、クラッチはバネの弾発力で噛合状態に復元する。
Ｑ＝Ｆ・sin（α＋φ）・cos(α＋φ) −−−−（１）
Ｆ：制限入力値
Ｑ：離脱方向力
α：突起の傾斜角
φ：突起斜面の摩擦角
When the inclination angle of the protrusion is α, the input limit value is F, and the required spring pressing force is Q, the engagement of the clutch is as follows. Therefore, the pressing spring force may be set equal to Q. Therefore, when the input value F becomes large F 1, removing direction force from equation (1) is Q1 becomes, F 1 is larger than F, Q 1 is to become larger than Q, the clutch is disengaged. Conversely, if the input is stopped (F = 0) or the input is set to F 2 smaller than F, the disengagement direction force becomes Q 2 smaller than Q, so the clutch is restored to the meshing state by the spring force of the spring. To do.
Q = F · sin (α + φ) · cos (α + φ) ---- (1)
F: Limit input value Q: Removal direction force α: Protrusion inclination angle φ: Protrusion slope friction angle
図面はこの発明の駆動装置をバタフライ弁に適用した例を示すが、これに限られるものではなく、ボール弁等その他の回転弁、更にはその他の一般の弁の駆動装置の回転部にも同様に適用することが出来る。図において(１)は、バタフライ弁を示し、その弁棒(２)の外端に歯車伝導機構からなる手動のアクチュエータ(３)が連結される。該手動のアクチュエータ(３)は、弁棒(２)の外端に連結されたウォームホイール(４)と該ウォームホイール(４)に噛合するウォーム(５)とを含み、ウォーム(５)にハンドル軸(６)が結合される。アクチュエータ(３)のケーシングから外方に延び出したハンドル軸(６)にこの発明のクラッチ機構(８)を介してハンドル車（７）が取付けられる。 The drawings show an example in which the drive device of the present invention is applied to a butterfly valve. However, the present invention is not limited to this, and the same applies to other rotary valves such as a ball valve, and also to the rotary portion of other general valve drive devices. It can be applied to. In the figure, (1) shows a butterfly valve, and a manual actuator (3) comprising a gear transmission mechanism is connected to the outer end of the valve stem (2). The manual actuator (3) includes a worm wheel (4) connected to the outer end of the valve stem (2) and a worm (5) meshing with the worm wheel (4). The shaft (6) is connected. The handle wheel (7) is attached to the handle shaft (6) extending outward from the casing of the actuator (3) via the clutch mechanism (8) of the present invention.
クラッチ機構(８)は、原動側のクラッチ部材(９)と従動側のクラッチ部材(10)から構成され、両クラッチ部材(9)(10)は、実質的に円板状の部材からなり、当接自在である。両部材の当接面に、突起(11)が所定の間隔を置いて複数円軌跡に沿って配列されている。そして、突起(11)の噛合若しくは離脱によりクラッチ部材(９)(10)の連結若しくは非連結が達成され、クラッチ機構が断続する。 The clutch mechanism (8) includes a driving-side clutch member (9) and a driven-side clutch member (10), and both the clutch members (9) and (10) are substantially disc-shaped members. It can contact freely. On the contact surfaces of both members, the protrusions (11) are arranged along a plurality of circular trajectories at a predetermined interval. Then, the engagement or disengagement of the clutch members (9) and (10) is achieved by the engagement or disengagement of the protrusion (11), and the clutch mechanism is intermittently connected.
原動側クラッチ部材(９)には、ハンドル車(７)が一体に設けられており、カップ形状をなしていると共に、前後に貫通した案内筒(12)が中心に立設されている。従動側クラッチ部材は、その中心にハンドル軸(６)を挿入する軸挿入筒(13)が一体に立設されている。軸挿入筒(13)の外端部内面は、ハンドル軸(６)の角状部(14)が係入する角部に形成されており、角状部の係合により、従動側クラッチ部材(10)は、ハンドル軸(６)に回り止め状態で連結されることになる。又、軸挿入筒の外端部には、後述するバネ固定板(15)を抜止状態に連結するためのＬ字状のスリット(17)が形成されている。案内筒(12)は、軸挿入筒(13)の外周に回転自在に遊挿可能である。 The driving side clutch member (9) is integrally provided with a handle wheel (7), has a cup shape, and a guide cylinder (12) penetrating in the front-rear direction. The driven clutch member is integrally provided with a shaft insertion cylinder (13) for inserting the handle shaft (6) at the center thereof. The inner surface of the outer end portion of the shaft insertion cylinder (13) is formed at a corner portion where the corner portion (14) of the handle shaft (6) is engaged, and the driven side clutch member ( 10) is connected to the handle shaft 6 in a non-rotating state. In addition, an L-shaped slit (17) for connecting a spring fixing plate (15), which will be described later, to a retaining state is formed at the outer end of the shaft insertion cylinder. The guide tube (12) can be freely rotatably inserted into the outer periphery of the shaft insertion tube (13).
バネ固定板(15)は、実質的に円板形状をなし、中心にボルト挿入孔(16)が穿孔されると共に、内面中心から先端に角棒状の連結部(18)を横方向に延び出させた筒体が立設され、ボルト挿入孔(16)はこの連結部(18)を貫通している。(19)は、所定の弾発力を有すバネであり、コイルスプリングからなるが、これに限られない。バネ(19)は、両端に配される座金(20)を介して案内筒(12)に外挿され、カップ状の原動側クラッチ部材(９)の内奥で一端を受け止められ、他端をバネ固定板(15)で固定される。 The spring fixing plate (15) has a substantially disk shape, a bolt insertion hole (16) is drilled in the center, and a square bar-shaped connecting portion (18) extends laterally from the center of the inner surface to the tip. The cylindrical body is erected, and the bolt insertion hole (16) passes through the connecting portion (18). (19) is a spring having a predetermined resilience, which is a coil spring, but is not limited thereto. The spring (19) is extrapolated to the guide tube (12) via washers (20) arranged at both ends, and one end is received inside the cup-shaped driving side clutch member (9), and the other end is It is fixed with a spring fixing plate (15).
クラッチ機構(８)をハンドル軸(６)に取付けるには、先ず、原動側クラッチ部材(９)を、従動側クラッチ部材(10)の軸挿入筒(13)の外周に回動自在に遊挿して、両部材を組み合わせる。次いで、バネ(19)を前述したように、バネ固定板(15)でバネ(19)を圧縮しつつ、連結部(18)を従動側クラッチ部材(10)のＬ字状スリット(17)に係入して従動側クラッチ部材の軸挿入筒(13)に抜止状態で連結し、更にボルト挿入孔(16)から挿入した連結ボルト(21)をハンドル軸(６)の先端に螺合して締結する。かくして、ハンドル車(７)を含むクラッチ機構(８)はハンドル軸(６)に取付けられる。 In order to attach the clutch mechanism (8) to the handle shaft (6), first, the driving side clutch member (9) is loosely inserted into the outer periphery of the shaft insertion cylinder (13) of the driven side clutch member (10). Combine both parts. Next, as described above, while the spring (19) is compressed by the spring fixing plate (15), the connecting portion (18) is inserted into the L-shaped slit (17) of the driven clutch member (10). Engage it and connect it to the shaft insertion tube (13) of the driven clutch member in a locked state, and then screw the connecting bolt (21) inserted from the bolt insertion hole (16) into the tip of the handle shaft (6). Conclude. Thus, the clutch mechanism (8) including the handle wheel (7) is attached to the handle shaft (6).
ハンドル車(７)を所定の入力値以下の力で手動回転する場合、バネ(19)の弾発力が、原動側クラッチ部材(９)を従動側クラッチ部材(10)に向って押付け、互いに当接する方向に付勢されているため、両部材に形成された突起(11)は互いに噛合しており、ハンドル車の回転力は円滑にハンドル軸(６)を介してアクチュエータ(３)に伝達され、弁棒(２)が回転される。 When the handle wheel (7) is manually rotated with a force equal to or less than a predetermined input value, the spring force of the spring (19) pushes the driving side clutch member (9) toward the driven side clutch member (10) and Since the projections (11) formed on both members are engaged with each other because they are biased in the abutting direction, the rotational force of the handle wheel is smoothly transmitted to the actuator (3) via the handle shaft (6). The valve stem (2) is rotated.
所定の入力値以上の力でハンドル車(７)が回転されるとき、突起(11)の傾斜面による離脱力がバネの弾発力より大きくなるため、両クラッチ部材の突起(11)が離脱した状態となり、クラッチ部材(９)(10)は相対的に滑り動き、入力の伝達が遮断される。その後、入力が除かれ、或いは低下するとバネの弾発力を受けて突起が自動的に噛合状態に復帰し、入力の伝導が復元する。 When the handle wheel (7) is rotated with a force greater than a predetermined input value, the disengagement force due to the inclined surface of the protrusion (11) is greater than the spring force of the spring, so the protrusions (11) of both clutch members are disengaged. In this state, the clutch members (9) and (10) are relatively slid and the input transmission is interrupted. Thereafter, when the input is removed or lowered, the protrusion automatically returns to the meshing state due to the elastic force of the spring, and the conduction of the input is restored.
図示の実施例において、突起の傾斜角αは２０゜、突起の高さ１.２ｍｍ、中心平面の高さは底面より０.７５ｍｍ、突起の幅ｂは３.４８２mm、突起の数は１５であり、隙間εは０.３mmとした。 In the illustrated embodiment, the inclination angle α of the protrusion is 20 °, the height of the protrusion is 1.2 mm, the height of the central plane is 0.75 mm from the bottom , the width b of the protrusion is 3.482 mm, and the number of protrusions is 15. And the gap ε was set to 0.3 mm.
(１)バタフライ弁
(２)弁棒
(３)アクチュエータ
(４)ウォームホイール
(５)ウォーム
(６)ハンドル軸
(７)ハンドル車
(８)クラッチ機構
(９)原動側クラッチ部材
(10)従動側クラッチ部材
(11)突起
(12)案内筒
(13)軸挿入筒
(14)角部
(15)バネ固定板
(16)ボルト挿入孔
(17)Ｌ字状スリット
(18)角棒状連結部
(19)バネ
(20)座金
(21)ボルト
(1) Butterfly valve
(2) Valve stem
(3) Actuator
(4) Worm wheel
(5) Warm
(6) Handle shaft
(7) Steering wheel
(8) Clutch mechanism
(9) Driving side clutch member
(10) Drive side clutch member
(11) Protrusion
(12) Guide tube
(13) Shaft insertion tube
(14) Corner
(15) Spring fixing plate
(16) Bolt insertion hole
(17) L-shaped slit
(18) Square bar connection
(19) Spring
(20) Washer
(21) Bolt
Claims (2)
2. The drive device according to claim 1, wherein the spring fixing plate is connected to the driven clutch member in a non-removed state by a square bar-shaped connecting portion that is detachably engageable with the L-shaped slit .
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004042821A JP3664486B1 (en) | 2004-02-19 | 2004-02-19 | Rotary valve drive unit |
| CNB2004100694841A CN100351566C (en) | 2004-02-19 | 2004-06-24 | Drive device of rotary valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004042821A JP3664486B1 (en) | 2004-02-19 | 2004-02-19 | Rotary valve drive unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP3664486B1 true JP3664486B1 (en) | 2005-06-29 |
| JP2005233297A JP2005233297A (en) | 2005-09-02 |
Family
ID=34737335
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004042821A Expired - Fee Related JP3664486B1 (en) | 2004-02-19 | 2004-02-19 | Rotary valve drive unit |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3664486B1 (en) |
| CN (1) | CN100351566C (en) |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH04185982A (en) * | 1990-11-20 | 1992-07-02 | Kubota Corp | Open/close operating device for gate valve |
| JP3701385B2 (en) * | 1996-05-31 | 2005-09-28 | 株式会社不二工機 | Motorized valve |
| JP3081820B2 (en) * | 1997-09-26 | 2000-08-28 | 株式会社巴技術研究所 | Rotary valve drive |
| JP2002039432A (en) * | 2000-07-21 | 2002-02-06 | Kubota Corp | Opening and closing operation rod for valve |
| JP2002061668A (en) * | 2000-08-16 | 2002-02-28 | Kubota Corp | Valve operation cap with slip mechanism |
-
2004
- 2004-02-19 JP JP2004042821A patent/JP3664486B1/en not_active Expired - Fee Related
- 2004-06-24 CN CNB2004100694841A patent/CN100351566C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1657812A (en) | 2005-08-24 |
| CN100351566C (en) | 2007-11-28 |
| JP2005233297A (en) | 2005-09-02 |
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