JP2005226712A - Valve element of butterfly valve - Google Patents
Valve element of butterfly valve Download PDFInfo
- Publication number
- JP2005226712A JP2005226712A JP2004035038A JP2004035038A JP2005226712A JP 2005226712 A JP2005226712 A JP 2005226712A JP 2004035038 A JP2004035038 A JP 2004035038A JP 2004035038 A JP2004035038 A JP 2004035038A JP 2005226712 A JP2005226712 A JP 2005226712A
- Authority
- JP
- Japan
- Prior art keywords
- valve body
- axis
- valve
- outer peripheral
- width
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 40
- 239000002994 raw material Substances 0.000 abstract description 2
- 239000012530 fluid Substances 0.000 description 23
- 238000007789 sealing Methods 0.000 description 9
- 238000003754 machining Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000007423 decrease Effects 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
Images
Landscapes
- Lift Valve (AREA)
Abstract
Description
この発明は、流体が流過する管路を開閉するためのバタフライ弁の弁体に関する。 The present invention relates to a valve body of a butterfly valve for opening and closing a pipeline through which a fluid flows.
従来、種々の流体が流過する管路を開閉し、若しくは流量制御するバタフライ弁は公知である。バタフライ弁は、円筒状の弁本体内に円板状の弁体を回動自在に軸支し、該弁体の回動軸を弁本体外に延び出させてアクチュエータに連結し駆動回転するようになっている。弁体重量を低減させつつ、流体抵抗を減少させるには、弁体の厚みを薄くすることになるが、薄くするに伴って弁体強度が低下してくる問題があり、又、弁体外周面を球体の一部をもって形成するには、精度の高い加工機械により高い加工精度を要すると共に、加工工数が多くなっている。更に、弁体はコストダウンを図ることが強く要望されている。 Conventionally, butterfly valves for opening and closing pipes through which various fluids flow or for controlling the flow rate are known. The butterfly valve pivotally supports a disc-shaped valve body in a cylindrical valve body, and extends the rotation shaft of the valve body to the outside of the valve body so as to be connected to an actuator for driving rotation. It has become. To reduce fluid resistance while reducing the weight of the valve body, the thickness of the valve body must be reduced. However, there is a problem that the strength of the valve body decreases as the thickness decreases, and the outer periphery of the valve body In order to form a surface with a part of a sphere, high processing accuracy is required by a high-precision processing machine, and the number of processing steps is increased. Further, there is a strong demand for reducing the cost of the valve body.
重量低減を図るため、弁体を平板をベース形状とし、その外表面に強度向上のための盛り肉部を持たせ、ボス部を太くしたものが知られている。流体抵抗を減らす目的からすると平板の厚みは薄いほど有利であるが、圧力流体を閉止する際に働く流体の推力に抗してその変形を防止するには、所要の厚みを必要とする。そこで、かかる平板状の弁体の強度補強を図るために、ボス部に補強板を取り付けた構造が、実用新案登録第２５２３９４８号公報に開示されている。流体圧力は、弁体の受圧面積全体に作用し、その推力は弁体中央部ではＸ軸、Ｙ軸方向に等分に働くが、この公知の弁体ではＸ軸上に作用する応力に対する補強に過ぎず、実際に働くＹ軸方向の力に対しては何ら効果を発揮していない問題がある。又、弁体の外円周縁部の形状を工夫して、弁体外円周縁部がシートリングに当接する際、ある開度以下では弁体とシートリングが同時に接触するようにした構造が、実公平４-２９１６４号公報に開示されている。しかしながら、この構造では、弁体外円周縁部が厚肉となり重量が増加すると共に、弁体中央部の強度が不十分となるおそれがあった。 In order to reduce the weight, there is known a valve body having a flat plate as a base shape, an outer surface having a built-up portion for improving strength, and a thickened boss portion. For the purpose of reducing the fluid resistance, the thinner the flat plate, the more advantageous. However, a required thickness is required to prevent the deformation against the thrust of the fluid acting when closing the pressure fluid. Therefore, in order to reinforce the strength of such a flat valve body, a structure in which a reinforcing plate is attached to a boss portion is disclosed in Japanese Utility Model Registration No. 2523948. The fluid pressure acts on the entire pressure receiving area of the valve body, and its thrust acts equally in the X-axis and Y-axis directions at the center of the valve body, but with this known valve body, reinforcement against stress acting on the X-axis. However, there is a problem that no effect is exerted on the force in the Y-axis direction that actually works. In addition, the shape of the outer peripheral edge of the valve body has been devised so that when the outer peripheral edge of the valve body comes into contact with the seat ring, the valve body and the seat ring are in contact with each other at a certain degree of opening or less. This is disclosed in Japanese Patent Publication No. 4-29164. However, with this structure, the outer peripheral edge of the valve body is thick and the weight increases, and the strength of the central part of the valve body may be insufficient.
本発明者は先に、弁体の厚みを減少させるために、Ｙ軸に沿って中心部を最も大きな厚みの峰部に形成し、該峰部から弁軸線と直交する側縁に向って表裏両面を斜面とした斜板を素材とし、これを円形状に形成して弁体を得ると共に、弁体の表面に流体の流過方向にほぼ並行に延びるリブを設けて強度を向上させる構造を提案した。しかしながら、かかる弁体の外周面を球形状から円筒形状に形成した場合、外周面の厚み(エッジ厚)が、弁軸の中心において直交するＸ軸(３時方向)から、Ｙ軸(１２時方向)に行くに従って増加して、弁棒を挿着するボス部近傍のエッジ厚が最も大きくなり、球面形状に比して弁体の径寸法が大きくなるため、弁体の回動時にエッジ幅の大きな部分(ボス部近傍)ではシートリングの摩耗が増加し、破損や亀裂のおそれがあった。又、弁体の駆動トルクが増大する問題もあった。 In order to reduce the thickness of the valve body, the inventor first formed a central portion along the Y-axis into a ridge portion having the largest thickness, and the front and back faces from the ridge portion toward the side edge perpendicular to the valve axis. A structure that uses a swash plate with slopes on both sides as a raw material to obtain a valve body by forming it in a circular shape, and improves the strength by providing ribs that extend substantially parallel to the fluid flow direction on the surface of the valve body Proposed. However, when the outer peripheral surface of the valve body is formed from a spherical shape to a cylindrical shape, the thickness (edge thickness) of the outer peripheral surface changes from the X axis (3 o'clock direction) orthogonal to the center of the valve shaft to the Y axis (12 o'clock). The edge thickness in the vicinity of the boss where the valve stem is inserted is the largest, and the diameter of the valve body is larger than that of the spherical shape. In a large part (near the boss part), the wear of the seat ring increased, and there was a risk of breakage or cracking. There is also a problem that the driving torque of the valve body increases.
この発明はＹ軸に沿って中心部を最も大きな厚みの峰部に形成し、該峰部から弁軸線と直交する側縁に向って表裏両面を斜面とした斜板を素材とし、これを円形状に形成した弁体において、弁体外周面の厚み(エッジ厚)がＸ軸からＹ軸に行くに従って増大してくるのを防止し、エッジ厚の増大によってもたらされる前記した問題点を解決せんとするものである。 The present invention uses a swash plate that has a central portion along the Y-axis as a ridge having the largest thickness, and that has a slope on both front and back sides from the ridge toward the side edge perpendicular to the valve axis. In the valve body formed in the shape, the thickness of the outer periphery of the valve body (edge thickness) is prevented from increasing from the X axis to the Y axis, and the above-mentioned problems caused by the increase in the edge thickness cannot be solved. It is what.
本発明は、弁体のＹ軸中心部を最も高い峰部とし、弁体の表裏両面を該峰部から側縁に向って同じ角度の斜面に形成し、弁体のＹ軸方向上下に弁棒穴用ボス部を設け、弁体の外周面を円筒形状に形成すると共に、弁体の外周縁両側に勾配を設け、該勾配の大きさをＸ軸からＹ軸に向って連続的に大きく形成して、シートリングと接触する弁体外周面の幅を同一寸法幅としたことを特徴とする。 In the present invention, the central part of the valve body in the Y-axis is the highest peak, and both front and back surfaces of the valve body are formed on the inclined surfaces at the same angle from the peak to the side edge. A rod hole boss is provided, the outer peripheral surface of the valve body is formed in a cylindrical shape, and gradients are provided on both sides of the outer peripheral edge of the valve body, and the magnitude of the gradient continuously increases from the X axis to the Y axis. The width of the outer peripheral surface of the valve body that is formed and is in contact with the seat ring has the same width.
本発明のバタフライ弁の弁体によれば、弁体外周面のエッジの幅をＸ軸位置からＹ軸方向に向って同じ幅寸法に形成してあるので、弁体とシートリングの接触面圧がボス部を除いてシートリングの全周面において等しくなり、弁開閉トルクを減少させることが出来る。又、同一のエッジ幅の形成は、弁体の外周縁両側を斜面に切除して勾配を付すことによってエッジ幅を前記のように同じ寸法としているが、この勾配はＸ軸位置において最も小さくＹ軸に行くに従って増大し、ボス部近傍が最も大きな勾配となる。かかる勾配を付すことにより球面形状に比して弁体の径寸法がボス部近傍で最も大きくなるのを回避することが出来、これによって、図１５に示すように弁体の駆動トルクを特に弁開放初期において大きく減少させることが出来、シートリングの摩耗を減少させ、亀裂や破損の発生を防止することが出来る。 According to the valve body of the butterfly valve of the present invention, since the width of the edge of the outer peripheral surface of the valve body is formed in the same width dimension from the X-axis position toward the Y-axis direction, the contact surface pressure between the valve body and the seat ring However, the valve opening / closing torque can be reduced because the seating ring is equal over the entire circumference of the seat ring except for the boss. In addition, the same edge width is formed by cutting off both sides of the outer peripheral edge of the valve body into slopes to give the same edge width as described above, but this slope is the smallest at the X-axis position. It increases as it goes to the axis, and the vicinity of the boss portion has the largest gradient. By providing such a gradient, it is possible to avoid that the diameter of the valve body becomes the largest in the vicinity of the boss portion compared to the spherical shape, and thereby the driving torque of the valve body is particularly reduced as shown in FIG. It can be greatly reduced in the initial stage of opening, reducing the wear of the seat ring and preventing the occurrence of cracks and breakage.
弁体外周面のエッジ幅は、２〜４mm、好ましくは３mm程度とし、狭い幅でシートリング内周面に接触するので、シートリングの摩耗を減少させうることは勿論、図１６に示すようにシール特性も向上させることが出来た。従来、一般的にはシール特性は、シール面積に関連しシール面積が少なくなるとシール特性は低下し、流体の漏れが発生するおそれがあると考えられていたが、本発明のように弁体外周面の幅を全周にわたって等しい幅とし、しかもその幅を２〜４mmと小さな寸法にしたところ、逆にシール性が向上することが見出された。 The edge width of the outer peripheral surface of the valve body is 2 to 4 mm, preferably about 3 mm, and it contacts the inner peripheral surface of the seat ring with a narrow width, so that wear of the seat ring can be reduced, as shown in FIG. The sealing characteristics could also be improved. Conventionally, it has been generally considered that the sealing characteristics are related to the sealing area, and if the sealing area is reduced, the sealing characteristics are deteriorated and there is a risk of fluid leakage. It has been found that when the width of the surface is made equal over the entire circumference and the width is made as small as 2 to 4 mm, the sealing performance is improved.
又、上下ボス部近傍を大きな勾配としたので、図１７に示すように弁全開時の流量特性を向上させることが出来る。更に、微少開度においても、ボス部近傍の勾配が弁の開放に寄与し、微少開度から流量を得ることが出来るため、コントロール性にすぐれた弁を提供することが出来る。 Further, since the vicinity of the upper and lower bosses has a large gradient, the flow characteristics when the valve is fully opened can be improved as shown in FIG. Furthermore, even at a very small opening, the gradient in the vicinity of the boss part contributes to the opening of the valve, and a flow rate can be obtained from the very small opening, so that a valve with excellent controllability can be provided.
更に、この発明によれば、弁体のベース円板の肉厚を極限まで薄くすることが出来、弁体全体の重量を軽減させて軽量化を図ることが可能となる。又、管内の流速分布は、管中央部が最速で、管壁に近づくにしたがって管壁との摩擦により低下するが、横リブと角度θの傾斜とにより、管壁部分の低速流体を管中央部の高速流体に吸引させて加速させ、全体の流体抵抗を減少し、流量の増加を図ることができる。更に、アンバランストルクの発生を抑制することが可能となる。 Furthermore, according to the present invention, the thickness of the base disc of the valve body can be reduced to the utmost limit, and the weight of the entire valve body can be reduced and the weight can be reduced. Also, the flow velocity distribution in the pipe is the fastest at the center of the pipe and decreases due to friction with the pipe wall as it approaches the pipe wall. The high-speed fluid in the part is sucked and accelerated to reduce the overall fluid resistance and increase the flow rate. Furthermore, generation of unbalance torque can be suppressed.
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、シートリングと接触する弁体の外周面を、球形ではなく円筒形状に形成すると共に、その幅をＸ軸位置からＹ軸方向に向かって同じ幅寸法に形成したことを特徴とする。弁体は、表裏両面をＹ軸に沿った中心部の厚みを最も高い峰部に形成し、該峰部からＸ軸方向に同一角度で傾斜した斜板からなる素材で形成し、該斜板を円形状に成形し、外周縁の両側にＸ軸からＹ軸方向に行くに従って勾配が大きくなる斜面に形成して、前記外周面の幅が等しくなるようにした。この発明の弁体は、バルブの口径が小口径（５０mm未満）から中口径（５０〜２００mm程度）のバタフライ弁に特に適するものであり、この場合の弁体外周面の幅は、２〜４mmが好ましく、最も好ましくは３mmとする。 Preferred embodiments of the present invention will be described in detail below. The present invention is characterized in that the outer peripheral surface of the valve body that contacts the seat ring is formed in a cylindrical shape instead of a spherical shape, and its width is formed in the same width dimension from the X-axis position toward the Y-axis direction. . The valve body is formed of a material composed of a swash plate that has both the front and back surfaces at the peak portion having the highest thickness along the Y axis and is inclined at the same angle in the X axis direction from the peak portion. Was formed into a slope whose slope increases in the direction from the X-axis to the Y-axis on both sides of the outer peripheral edge so that the width of the outer peripheral surface becomes equal. The valve body according to the present invention is particularly suitable for a butterfly valve having a small diameter (less than 50 mm) to a medium diameter (about 50 to 200 mm). In this case, the width of the outer peripheral surface of the valve body is 2 to 4 mm. And most preferably 3 mm.
弁体外周面の幅は、口径の大きさとはほとんど関連性がなく、小口径から中口径までほぼ同一の幅で良かった。外周面の幅が４mmよりも大きいと、特にボス部近傍における径寸法が大きくなりシートリングへの食い込みが生じて、シートリングの摩耗、亀裂、破損を招来するおそれがあると共に、弁体駆動トルクも増加する。弁体の幅が２mmより小さくなると、シートリングへの食い込みが大きくなり過ぎるおそれがある。弁体の外周面の幅を同一とするための勾配の形成は、機械加工によっても可能であるが、鋳型成型により形成するのが好ましい。 The width of the outer peripheral surface of the valve body was almost unrelated to the size of the caliber, and was almost the same width from the small caliber to the medium caliber. If the width of the outer peripheral surface is larger than 4 mm, the diameter in the vicinity of the boss part will increase and the seat ring may bite, causing the seat ring to wear, crack or break, and the valve body drive torque. Will also increase. If the width of the valve body is smaller than 2 mm, the bite into the seat ring may become too large. The formation of the gradient for making the width of the outer peripheral surface of the valve body the same is possible by machining, but is preferably formed by molding.
弁体のＹ軸方向上下には、弁棒穴用ボス部が外方に膨出して設けられ、弁体のノズル側表面にボス部から二次側方向に延びる複数の横リブを、又弁体のオリフィス側裏面にＹ軸を中心に１８０゜回転させたボス部から一次側方向に延びる複数の横リブをそれぞれ設けて、リブにより弁体の強度を向上させて弁体の厚みを低減し軽量化を図りうるようにすると共に、流体抵抗を減少させて流量の増加をもたらし得るようにし、更にノズル側とオリフィス側の流速差を減少させて弁体に負荷されるアンバランストルクを抑制する。 Above and below the valve body in the Y-axis direction, valve stem hole bosses bulge outward, and a plurality of lateral ribs extending in the secondary direction from the boss part are provided on the nozzle side surface of the valve body. A plurality of lateral ribs extending in the primary direction from the bosses rotated 180 ° around the Y axis are provided on the back side of the orifice side of the body to improve the strength of the valve body and reduce the thickness of the valve body. The weight can be reduced, the fluid resistance can be reduced to increase the flow rate, and the flow velocity difference between the nozzle side and the orifice side can be reduced to suppress the unbalance torque applied to the valve body. .
Ｙ軸方向の上下に配されたボス部は、縦リブで連結されると共に、ノズル側表面及びオリフィス側裏面の横リブは、縦リブを起点として中央部の横リブはＸ軸方向に、その上下に位置する横リブは中央部の横リブに平行若しくは外周縁に行くに従って若干の角度で近接するように配設される。更に、横リブは、好ましくは弁体の中心平面に対して高さが低くなるような傾斜角が付けられている。又、弁体を構成する円形板は、前述したようにその表面がＹ軸を頂点としＺ軸に対して傾斜する傾斜面に形成されており、Ｙ軸上に弁棒穴用ボス部及び横リブが設けられている。 The bosses arranged above and below in the Y-axis direction are connected by vertical ribs, and the horizontal ribs on the nozzle side surface and the orifice side back surface start from the vertical ribs and the central horizontal ribs in the X-axis direction. The horizontal ribs positioned above and below are arranged so as to be close to each other at a slight angle in parallel to the central horizontal rib or toward the outer peripheral edge. Further, the lateral rib is preferably inclined so that its height is lower than the central plane of the valve body. Further, as described above, the surface of the circular plate constituting the valve body is formed on an inclined surface with the Y axis as the apex and inclined with respect to the Z axis. Ribs are provided.
図１〜１４を参照して、(10)は中心形バタフライ弁の弁体であり、円板形状をベースとし、図６に示すようにＹ軸を中心にＺ軸に対して角度αの傾斜表面を有している。この角度αは、図６〜８に示す断面Ａ−Ａ’、Ｂ−Ｂ’及びＣ−Ｃ’のいずれの部分においても同じ角度である。すなわち、弁体(10)は、その表裏両面がＹ軸を頂点する斜板に形成されている。Ｙ軸上の上下に上下弁棒穴(11)(12)を形成するための上下弁棒穴用ボス部(13)(14)が設けられ、両ボス部は縦リブで連結される。尚、本明細書においてＹ軸は、弁体の回転中心軸である弁軸をいい、Ｘ軸は弁体の中心においてＹ軸と直交する軸をいい、Ｚ軸はＸ軸と直交しＹ軸と平行な弁体の平面中心を通る軸をいう。 1 to 14, (10) is a valve body of a central butterfly valve, which is based on a disk shape and is inclined at an angle α with respect to the Z axis with respect to the Y axis as shown in FIG. Has a surface. This angle α is the same angle in any part of the cross sections A-A ′, B-B ′ and C-C ′ shown in FIGS. That is, the valve body (10) is formed as a swash plate whose front and back surfaces are apex of the Y axis. Upper and lower valve stem hole boss portions (13) and (14) for forming upper and lower valve stem holes (11) and (12) are provided on the upper and lower sides of the Y axis, and both boss portions are connected by vertical ribs. In this specification, the Y axis refers to the valve axis that is the rotation center axis of the valve element, the X axis refers to the axis that is orthogonal to the Y axis at the center of the valve element, and the Z axis is orthogonal to the X axis and the Y axis. An axis that passes through the plane center of the valve body in parallel.
図３，４及び図１０〜１２を参照して、シートリングの内周面に接触してシール性を発揮する弁体(10)の外周面(15)は、球面形状ではなく、円筒面形状に形成されると共に、Ｘ軸位置（図５Ｄ−Ｄ’線部分)から、前記ボス部(13)(14)近傍(図５Ｆ−Ｆ’線部分)まで、同一の幅寸法に形成される。そして、かかる外周面の幅を同一寸法とするために、弁体の外周円の両側には勾配(16)が形成される。この勾配(16)をＸ軸位置において最小とし、ボス部近傍において最大となるような連続した斜面をもって形成することにより、外周面(15)の幅をボス部を除いて全周に亘って同一の幅とすることが可能となる。かかる外周面の勾配を作るための斜面の加工は、機械加工によって形成しても良いが、鋳型成型により形成するのが好ましい。外周面の円筒形状の形成は、機械加工により形成するが、この場合に球面加工をする場合のような精密加工を要しないため、加工コストを低減することが出来る。
3 and 4 and FIGS. 10 to 12, the outer peripheral surface (15) of the valve element (10) that contacts the inner peripheral surface of the seat ring and exhibits sealing performance is not a spherical shape but a cylindrical surface shape. And the same width dimension from the X-axis position (line part D-D 'in FIG. 5) to the vicinity of the
弁体外周面の幅は、２〜４mmが好ましく、最も好ましくは３mmとする。弁体外周面の幅は、口径の大きさとはほとんど関連性がなく、小口径から中口径までほぼ同一の幅とすることが出来る。外周面の幅が４mmよりも大きいと、特にボス部近傍における径寸法が大きくなりシートリングへの食い込みが生じて、シートリングの摩耗、亀裂、破損を招来するおそれがあると共に、弁体駆動トルクも増加する。弁体の幅が２mmより小さくなると、シートリングへの食い込みが大きくなり過ぎるおそれがある。これにより、図１５に示すように弁体の駆動トルクを特に弁開放初期において大きく減少させることが出来、シートリングの摩耗を減少させ、亀裂や破損の発生を防止することが出来る。 The width of the outer peripheral surface of the valve body is preferably 2 to 4 mm, and most preferably 3 mm. The width of the outer peripheral surface of the valve body is almost unrelated to the size of the diameter, and can be made substantially the same width from the small diameter to the medium diameter. If the width of the outer peripheral surface is larger than 4 mm, the diameter in the vicinity of the boss part will increase and the seat ring may bite, causing the seat ring to wear, crack or break, and the valve body drive torque. Will also increase. If the width of the valve body is smaller than 2 mm, the bite into the seat ring may become too large. As a result, as shown in FIG. 15, the driving torque of the valve body can be greatly reduced, particularly in the initial stage of opening the valve, so that the wear of the seat ring can be reduced and the occurrence of cracks and breakage can be prevented.
又、図１６に示すようにシール特性も向上させることが出来た。又、上下ボス部近傍を大きな勾配としたので、図１７に示すように弁全開時の流量特性を向上させることが出来た。更に、微少開度においても、ボス部近傍の勾配が弁の早期開放に寄与し、微少開度から流量を得ることが出来るため、コントロール性にすぐれた弁を提供するが出来た。尚、図１５〜１７において従来品は外周面を球面形状とした点を除いては、本発明の実施例の図面に示されるようなリブを３本有した構造のものである。又、２５０Ａ、３００Ａは弁の口径を示し、２５０Ａは、口径２５０mm、３００Ａは口径３００mmの弁である。 Also, as shown in FIG. 16, the sealing characteristics could be improved. Further, since the vicinity of the upper and lower bosses has a large gradient, the flow rate characteristics when the valve is fully opened can be improved as shown in FIG. Furthermore, even at a very small opening, the gradient near the boss contributes to early opening of the valve, and the flow rate can be obtained from the very small opening, so that a valve with excellent controllability can be provided. 15 to 17, the conventional product has a structure having three ribs as shown in the drawings of the embodiment of the present invention, except that the outer peripheral surface has a spherical shape. Further, 250A and 300A indicate the diameters of the valves, 250A is a valve having a diameter of 250 mm, and 300A is a valve having a diameter of 300 mm.
図１，３，６に示すように上部弁棒穴(11)の内周面は平行な平面(11a)が形成されており、弁棒先端の平行面と係止して、回り止め連結されるようになっている。下部弁棒穴(12)は、断面円形であり下部弁棒が遊挿される。上部弁棒穴に回り止め状態で装着された弁棒は、バタフライ弁の弁軸筒を上方に延び出して、外端に所望の駆動用アクチュエータが接続される。 As shown in FIGS. 1, 3 and 6, the inner peripheral surface of the upper valve stem hole (11) is formed with a parallel plane (11 a). It has become so. The lower valve stem hole (12) has a circular cross section and the lower valve stem is loosely inserted. The valve stem mounted in the upper valve stem hole in a non-rotating state extends upward from the valve stem of the butterfly valve, and a desired drive actuator is connected to the outer end.
弁体(10)のノズル側表面に、複数の横リブ(17a)(17b)(17c)が形成される。横リブは、弁体表面から一定の高さを有して、前記縦リブ(18)を起点として二次側方向にＸ軸と略平行に延びており、弁体表面近傍を流れる流体は、横リブでその方向が制御される。図示の実施例において横リブは３本形成され、中央の横リブ(17b)はＸ軸に沿って平行に延びており、その上下の横リブ(17a)(17c)は、Ｘ軸に対して中央の横リブ(17b)に徐々に近接するような傾斜が付けられている。又、各横リブの表面は、二次側に向って高さが低くなるように形成されている。 A plurality of lateral ribs (17a), (17b) and (17c) are formed on the nozzle side surface of the valve body (10). The lateral rib has a certain height from the valve body surface, extends substantially parallel to the X axis in the secondary direction starting from the longitudinal rib (18), and the fluid flowing in the vicinity of the valve body surface is The direction is controlled by the lateral rib. In the illustrated embodiment, three lateral ribs are formed, the central lateral rib (17b) extends in parallel along the X axis, and the upper and lower lateral ribs (17a) and (17c) are arranged with respect to the X axis. It is inclined so as to gradually approach the central lateral rib (17b). Moreover, the surface of each horizontal rib is formed so that height may become low toward a secondary side.
弁体のオリフィス側である裏面にも、弁軸Ｙを中心に180゜回転した状態で前記ノズル側表面と同一の３本の横リブ(19)が、縦リブ(18)を起点として一次側方向に形成されている。尚、弁体の表面、裏面は、閉弁時に一次側に対面している面を表面、二次側に対面している面を裏面とし、ノズル側とは、弁体開弁時に二次側に回動する弁体の半分部分(図５において右側半分)をいい、オリフィス側とは、一次側方向に回動する弁体の半分部分(図５において左側半分)をいう。 The same three horizontal ribs (19) as the nozzle side surface in the state rotated 180 ° around the valve shaft Y on the back side, which is the orifice side of the valve body, are the primary side starting from the vertical rib (18). Is formed in the direction. The front and back surfaces of the valve body are the surface facing the primary side when the valve is closed, the front surface is the surface facing the secondary side, and the nozzle side is the secondary side when the valve body is opened. The half of the valve body that rotates in the right direction (right half in FIG. 5) refers to the half of the valve body that rotates in the primary direction (the left half in FIG. 5).
ノズル側表面の３本の横リブ(17)は、一定の高さを有していることにより、弁体表面近傍を流れる流体は、これらの横リブ(17)で方向を制御される。中央の横リブ(17b)は、管内の最大流速部分に位置し最大流速を二分し、且その流速を加速する。中央の横リブ(17b)の上下に配置された横リブ(17a)(17c)は、中央の横リブ(17b)に向かう傾斜が付けられているため、管壁近傍の低速領域の流体を中央の横リブ(17b)に向かわせ、該横リブ(17b)によって加速された流速に引き込まれる状態でその速度を増加させる。流体に対しては、上下弁棒穴用ボス部(13)(14)が流路抵抗となり、ボス部に衝突した流体はボスの二次側で渦を発生させ、流体抵抗を更に増加させる。これに対して、３本の横リブ(17)はボス部の二次側に発生する渦に対して整流効果を発揮し、渦の発生を低減させる。結果として、本発明の横リブは、管内流速を弁体近傍で分断し、整流し、管壁の流体抵抗、弁体表面の流体抵抗を、リブ部が持つ流れ方向制御により補完し、弁全体の流体抵抗を減じる効果を有する。 Since the three lateral ribs (17) on the nozzle side surface have a certain height, the direction of the fluid flowing in the vicinity of the valve body surface is controlled by these lateral ribs (17). The central lateral rib (17b) is located in the maximum flow velocity portion in the pipe, bisects the maximum flow velocity, and accelerates the flow velocity. The lateral ribs (17a) and (17c) arranged above and below the central lateral rib (17b) are inclined toward the central lateral rib (17b). Toward the horizontal rib (17b), and the speed is increased while being drawn into the flow velocity accelerated by the horizontal rib (17b). For the fluid, the upper and lower valve stem hole bosses (13) and (14) provide flow resistance, and the fluid colliding with the boss generates vortices on the secondary side of the boss, further increasing the fluid resistance. On the other hand, the three lateral ribs (17) exert a rectifying effect on the vortex generated on the secondary side of the boss portion, and reduce the generation of the vortex. As a result, the lateral rib of the present invention divides and rectifies the flow velocity in the pipe in the vicinity of the valve body, complements the fluid resistance of the pipe wall and the fluid resistance of the valve body surface by the flow direction control of the rib part, It has the effect of reducing the fluid resistance.
弁体を平板で構成した場合、必要な肉厚は計算で求めることが可能であり、弁体中心部が最も発生応力が高く、その応力に相応する肉厚が必要となる。本発明では、上下弁棒穴用ボス部(13)(14)を出来るだけ長くすることにより、ボス部の断面係数を増加し、弁体中央部の肉厚を減じる作用をする。縦リブ(18)の存在は、かかるボス部の作用を助長することが出来る。又、弁体の表裏面の３本の横リブは、Ｙ軸方向での強度保証として機能させることが出来、平板の肉厚を減じる作用を果たす。かくして、上下弁棒穴用ボス部(13)(14)、縦リブ(18)、横リブ(17)(19)を配することにより、高強度で最軽量の弁体を実現することが出来た。 When the valve body is formed of a flat plate, the necessary wall thickness can be obtained by calculation. The generated stress is highest in the central part of the valve body, and the wall thickness corresponding to the stress is required. In the present invention, the boss portions (13) and (14) for the upper and lower valve stem holes are made as long as possible, thereby increasing the section modulus of the boss portion and reducing the thickness of the central portion of the valve body. The presence of the longitudinal rib (18) can promote the action of the boss portion. Further, the three lateral ribs on the front and back surfaces of the valve body can function as guaranteeing the strength in the Y-axis direction, and serve to reduce the thickness of the flat plate. Thus, by arranging the upper and lower valve stem hole bosses (13) and (14), vertical ribs (18), and horizontal ribs (17) and (19), it is possible to realize the strongest and lightest valve body. It was.
リブを設けることにより、バタフライバルブ全開時の流路面積は減少する。このことは、弁体自身の流体抵抗が増加することを意味しており、結果として全開時のバルブ抵抗を増加させている。しかし、バルブ全開時の流体抵抗は、弁体の投影面積のみならず、弁体に設けられたボス部及び円板の外周先端部にある段差の後流部に発生するカルマン渦により、投影面積以上の流体抵抗が生ずる。本発明の弁体は、横リブ等の存在により投影面積自体は、リブなし弁体に比して増加しているが、ボス部に設けた横リブが前述したような整流効果を発揮し、管中央部の流量を増加させるため、結果としてリブによる投影面積の増加による悪影響を相殺することが出来る。 By providing the rib, the flow path area when the butterfly valve is fully opened is reduced. This means that the fluid resistance of the valve body itself increases, and as a result, the valve resistance when fully opened is increased. However, the fluid resistance when the valve is fully opened is not only due to the projected area of the valve body, but also due to the Karman vortex generated at the boss part provided on the valve body and the wake part of the step at the outer peripheral tip of the disc. The above fluid resistance occurs. In the valve body of the present invention, the projected area itself is increased as compared with the valve body without ribs due to the presence of the lateral ribs, etc., but the lateral ribs provided in the boss portion exert the rectifying effect as described above, Since the flow rate in the central portion of the tube is increased, the adverse effects due to the increase in the projected area due to the ribs can be offset as a result.
(10)弁体
(11)上部弁棒穴
(12)下部弁棒穴
(13)上部ボス部
(14)下部ボス部
(15)弁体外周面
(16)勾配
(17)横リブ
(18)縦リブ
(19)横リブ
(10) Valve body
(11) Upper valve stem hole
(12) Lower valve stem hole
(13) Upper boss
(14) Lower boss
(15) Valve body outer peripheral surface
(16) Gradient
(17) Horizontal rib
(18) Vertical rib
(19) Horizontal rib
Claims (1)
The central part of the valve body in the Y-axis is the highest peak, and both front and back surfaces of the valve body are formed on the inclined surface at the same angle from the peak to the side edge. A part is provided, and the outer peripheral surface of the valve body is formed in a cylindrical shape, and a gradient is provided on both sides of the outer peripheral edge of the valve body, and the magnitude of the gradient is continuously increased from the X axis to the Y axis. A valve body of a butterfly valve characterized in that the width of the outer peripheral surface of the valve body in contact with the seat ring has the same width.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004035038A JP3676795B1 (en) | 2004-02-12 | 2004-02-12 | Butterfly valve disc |
| CNB2004100490083A CN100343559C (en) | 2004-02-12 | 2004-06-14 | Valve body of butterfly valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004035038A JP3676795B1 (en) | 2004-02-12 | 2004-02-12 | Butterfly valve disc |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP3676795B1 JP3676795B1 (en) | 2005-07-27 |
| JP2005226712A true JP2005226712A (en) | 2005-08-25 |
Family
ID=34824342
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2004035038A Expired - Lifetime JP3676795B1 (en) | 2004-02-12 | 2004-02-12 | Butterfly valve disc |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP3676795B1 (en) |
| CN (1) | CN100343559C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020175673A1 (en) * | 2019-02-28 | 2020-09-03 | 株式会社キッツ | Valve body of double eccentric butterfly valve, and double eccentric butterfly valve |
| JP2020139584A (en) * | 2019-02-28 | 2020-09-03 | 株式会社キッツ | Valve body of double-eccentric type butterfly valve and double-eccentric type butterfly valve |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4036469A (en) * | 1975-05-09 | 1977-07-19 | Milwaukee Valve Company, Inc. | Butterfly valve |
| US4243203A (en) * | 1979-07-20 | 1981-01-06 | Mack Lawrence W | Butterfly valve |
| JPS59153769U (en) * | 1983-03-31 | 1984-10-15 | 積水化学工業株式会社 | butterfly valve valve body |
| JPS61105373A (en) * | 1984-10-29 | 1986-05-23 | Toshiba Corp | Butterfly valve |
| JP3356511B2 (en) * | 1993-12-01 | 2002-12-16 | 株式会社オーケーエム | Butterfly valve |
| JPH1047497A (en) * | 1996-07-31 | 1998-02-20 | Kubota Corp | Butterfly valve |
| JP3423202B2 (en) * | 1997-12-10 | 2003-07-07 | 株式会社クボタ | Powder shut-off valve device |
-
2004
- 2004-02-12 JP JP2004035038A patent/JP3676795B1/en not_active Expired - Lifetime
- 2004-06-14 CN CNB2004100490083A patent/CN100343559C/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2020175673A1 (en) * | 2019-02-28 | 2020-09-03 | 株式会社キッツ | Valve body of double eccentric butterfly valve, and double eccentric butterfly valve |
| JP2020139584A (en) * | 2019-02-28 | 2020-09-03 | 株式会社キッツ | Valve body of double-eccentric type butterfly valve and double-eccentric type butterfly valve |
| JP7248287B2 (en) | 2019-02-28 | 2023-03-29 | 株式会社キッツ | Disc of double eccentric butterfly valve and double eccentric butterfly valve |
| US11703129B2 (en) | 2019-02-28 | 2023-07-18 | Kitz Corporation | Valve disk of double eccentric butterfly valve, and double eccentric butterfly valve |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100343559C (en) | 2007-10-17 |
| CN1654864A (en) | 2005-08-17 |
| JP3676795B1 (en) | 2005-07-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP3708538B1 (en) | Triple eccentric butterfly valve | |
| EP1588082B1 (en) | Butterfly valve | |
| JP3621216B2 (en) | Turbine nozzle | |
| JP2007127191A (en) | Butterfly valve | |
| CN112088270A (en) | Valve and closure member | |
| JP3676785B2 (en) | Butterfly valve disc | |
| KR101476518B1 (en) | Valve element of butterfly valve | |
| JP6880004B2 (en) | Valves for internal combustion engines with guide vanes for coolant | |
| JP6744441B1 (en) | Eccentric rotary valve | |
| JP3676795B1 (en) | Butterfly valve disc | |
| JP7209966B2 (en) | butterfly valve for water | |
| JP2003097732A (en) | Butterfly valve | |
| JP3709196B1 (en) | Triple eccentric butterfly valve and valve body | |
| US20210301933A1 (en) | Mixer faucet | |
| EP4112976A1 (en) | Butterfly valve with quintuple offset structure | |
| CN110741194B (en) | Filling valve with main valve | |
| JP4086495B2 (en) | Butterfly valve with constant flow rate filling function | |
| JP3675288B2 (en) | Control butterfly valve | |
| JP5171920B2 (en) | Butterfly valve | |
| JP3689329B2 (en) | Low noise butterfly valve | |
| JP5685444B2 (en) | Butterfly valve with water filling function | |
| JP2020139583A (en) | Valve body of double-eccentric type butterfly valve and double-eccentric type butterfly valve | |
| JP3623708B2 (en) | Butterfly valve seat ring | |
| JP2007154786A (en) | Francis turbine runner and hydraulic machine | |
| KR100870921B1 (en) | Butterfly valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| TRDD | Decision of grant or rejection written | ||
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20050428 |
|
| R150 | Certificate of patent or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 Ref document number: 3676795 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20080513 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110513 Year of fee payment: 6 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20110513 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20140513 Year of fee payment: 9 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| EXPY | Cancellation because of completion of term |