JPH0776589B2 - Check valve - Google Patents
Check valveInfo
- Publication number
- JPH0776589B2 JPH0776589B2 JP4313182A JP31318292A JPH0776589B2 JP H0776589 B2 JPH0776589 B2 JP H0776589B2 JP 4313182 A JP4313182 A JP 4313182A JP 31318292 A JP31318292 A JP 31318292A JP H0776589 B2 JPH0776589 B2 JP H0776589B2
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- valve
- moving valve
- moving
- check valve
- 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.)
- Expired - Fee Related
Links
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- Check Valves (AREA)
- Details Of Valves (AREA)
Description
【０００１】[0001]
【産業上の利用分野】本発明は、サージング現象の発生
を極力防止して的確に流体の流出・遮断を自動制御する
ことができるチェックバルブに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a check valve which can prevent the occurrence of a surging phenomenon as much as possible and can automatically and accurately control the outflow and interruption of a fluid.
【０００２】[0002]
【従来の技術】例えば、鋼材の水冷用スプレー装置など
においては図５に示されるように、被冷却体である鋼材
３０を冷却水ヘッダー３１に多数個配列したスプレーノ
ズル３２により冷却するが、冷却水の供給・停止を１個
のバルブ３３で行うため、各スプレーノズル３２の応答
性を良くする目的で各供給管３４内に冷却水の流出・遮
断を該冷却水の圧力変化によって自動制御できるチェッ
クバルブを内蔵させておく場合がある。このようなチェ
ックバルブとしては、図６や図７に示されるような流路
１内に常時はスプリング２により弁座３に押しつけられ
て閉状態をなすが所定値以上の流体の押圧力により移動
して開状態となる移動弁４を配置したものが種々提案さ
れ、実用に供されている。2. Description of the Related Art For example, in a water-cooling spray device for steel materials, as shown in FIG. 5, a steel material 30 to be cooled is cooled by a spray nozzle 32 in which a large number of steel materials 30 are arranged in a cooling water header 31. Since water is supplied / stopped by one valve 33, the outflow / interruption of cooling water in each supply pipe 34 can be automatically controlled by the pressure change of the cooling water for the purpose of improving the responsiveness of each spray nozzle 32. A check valve may be built in. Such a check valve is normally closed by being pressed against the valve seat 3 by the spring 2 in the flow path 1 as shown in FIGS. 6 and 7, but is moved by the pressing force of the fluid of a predetermined value or more. Various arrangements of the moving valve 4 which is then opened have been proposed and put to practical use.
【０００３】ところが、従来のこの種チェックバルブに
おいては、サージング現象によるスプレーノズル３２の
噴霧状態に乱れを発生させるという問題点があった。即
ち、原理的にはチェックバルブにＰ1 なる圧力の流体を
入口より導入した場合、流体圧力によって移動弁４が押
されて該押圧力がスプリング２の弾発力を上回った時に
弁座３との間に隙間を形成して流体を出口側へ流出させ
るのであるが、移動弁４の動きにつれて該移動弁４と弁
座３との開口面積が増え、流入量が一定であればバルブ
前後の流体圧力損失（Ｐ1 −Ｐ2 ）が減少する。一方、
入口の流体圧力Ｐ1 が十分に大きくて移動弁４がストッ
パー５に突き当たれば、流体の入口から出口に到る流路
形状が一定になるため出口からは安定して流体が流出す
ることとなる。しかるに、前記移動弁４が弁座３との間
に隙間を形成して流体の流出を開始してからストッパー
５に突き当たるまでの間は、流体圧力が移動弁４を動か
そうとする力とそれを戻そうとするスプリング２の弾発
力との釣り合いの状態となり、この場合、流体はいわゆ
る脈動流れとなりサージング現象を発生する。この結
果、チェックバルブの下流に装着したスプレーノズル３
２の噴霧状態に乱れを発生させることとなり、該スプレ
ーノズル３２の噴射拡がり角度、流量、粒子径分布など
が不安定となって均一な冷却を行うことができないとい
う問題点や、スプレーノズル３２の寿命を著しく短くす
るという問題点があった。However, the conventional check valve of this type has a problem that the spraying state of the spray nozzle 32 is disturbed due to a surging phenomenon. That is, in principle, when a fluid having a pressure of P 1 is introduced into the check valve from the inlet, when the moving valve 4 is pushed by the fluid pressure and the pushing force exceeds the elastic force of the spring 2, the valve seat 3 A fluid is discharged to the outlet side by forming a gap between them, but the opening area between the moving valve 4 and the valve seat 3 increases as the moving valve 4 moves, and if the amount of inflow is constant, it is fluid pressure loss (P 1 -P 2) is reduced. on the other hand,
If the fluid pressure P 1 at the inlet is sufficiently large and the moving valve 4 hits the stopper 5, the shape of the flow passage from the fluid inlet to the outlet becomes constant, so that the fluid stably flows out from the outlet. Become. However, from the time when the moving valve 4 forms a gap between the moving valve 4 and the valve seat 3 to start flowing out of the fluid until it abuts against the stopper 5, the fluid pressure and the force for moving the moving valve 4 Is in a state of balance with the elastic force of the spring 2 that tries to return the fluid. In this case, the fluid becomes a so-called pulsating flow and a surging phenomenon occurs. As a result, the spray nozzle 3 installed downstream of the check valve
As a result, the spray state of No. 2 will be disturbed, and the spray divergence angle, flow rate, particle size distribution, etc. of the spray nozzle 32 will become unstable and uniform cooling cannot be performed. There is a problem that the life is remarkably shortened.
【０００４】[0004]
【発明が解決しようとする課題】本発明は上記のような
従来の問題点を解決して、サージング現象の発生を極力
防止して的確に流体の流出・遮断を自動制御することが
できる構造が簡単で安価なチェックバルブを提供するこ
とを目的として完成されたものである。SUMMARY OF THE INVENTION The present invention has a structure that solves the above-mentioned conventional problems, prevents the occurrence of a surging phenomenon as much as possible, and can automatically control the outflow / interruption of a fluid accurately. It was completed for the purpose of providing a simple and inexpensive check valve.
【０００５】[0005]
【課題を解決するための手段】上記の課題を解決するた
めになされた本発明のチェックバルブは、流路内に常時
はスプリングにより弁座に押し付けられて閉状態をなす
が所定値以上の流体の押圧力により移動して開状態とな
る移動弁を配置したチェックバルブにおいて、前記移動
弁にこれと一体に移動する流体制御用オリフィスを取付
け、該流体制御用オリフィスには前記移動弁が全開され
た時における移動弁と弁座間の開口面積よりも開孔面積
の合計が小さい流体流入孔を設けたことを特徴とするも
のである。SUMMARY OF THE INVENTION The check valve of the present invention, which has been made to solve the above-mentioned problems, has a fluid which has a predetermined value or more in a flow passage and is normally pressed against a valve seat by a spring. In a check valve in which a moving valve that moves by the pressing force of 1 to be placed in an open state is arranged, a fluid control orifice that moves integrally with the moving valve is attached, and the moving valve is fully opened in the fluid control orifice. It is characterized in that a fluid inflow hole having a total opening area smaller than the opening area between the moving valve and the valve seat at the time of opening is provided.
【０００６】[0006]
【実施例】次に、本発明を図示の実施例に基づいて詳細
に説明する。図１は本発明に係るチェックバルブの一例
を示すもので、図中１は流路であり、該流路１内には常
時はスプリング２の弾発力で弁座３に押し付けられて閉
状態をなすが所定値以上の流体の押圧力により移動して
開状態となる移動弁４が配置されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will now be described in detail with reference to the illustrated embodiments. FIG. 1 shows an example of a check valve according to the present invention. In the figure, reference numeral 1 denotes a flow passage, and the flow passage 1 is normally pressed by a resilient force of a spring 2 against a valve seat 3 to be in a closed state. A moving valve 4 is arranged which is moved to an open state by a pressing force of a fluid having a predetermined value or more.
【０００７】前記の移動弁４には流路の入口側方向にロ
ッド６が突設され、その先端部には移動弁４と一体に移
動可能な流体制御用オリフィス７がボルト等により取付
けられており、この流体制御用オリフィス７には図３に
示すように、適数個の流体流入孔８が設けられている。
この流体流入孔８はその開孔面積の合計が前記移動弁４
の全開時における移動弁４と弁座３との間の開口面積よ
りも小さくなるよう設計されており、その形状や個数等
についてはその範囲内において任意に変更できるもので
ある。The moving valve 4 is provided with a rod 6 projecting toward the inlet side of the flow path, and a fluid control orifice 7 movable integrally with the moving valve 4 is attached to the tip of the rod 6 by a bolt or the like. The fluid control orifice 7 is provided with an appropriate number of fluid inflow holes 8 as shown in FIG.
The total area of the fluid inflow holes 8 is equal to that of the moving valve 4
Is designed to be smaller than the opening area between the moving valve 4 and the valve seat 3 when fully opened, and the shape, the number, and the like can be arbitrarily changed within the range.
【０００８】なお、前記流体制御用オリフィス７の周縁
部には出口側方向に向かう円筒状の筒部９が延設されて
おり、該筒部９の端縁部が前記流路１内に形成されたス
トッパー５と当接して移動弁４のストロークを一定量と
することにより、全開時における移動弁４と弁座３間の
開口面積を所定のものとなるよう構成されている。ま
た、筒部９内には前記したスプリング２が装着されてい
てこのスプリング２が流体制御用オリフィス７とストッ
パー５との間に弾発力を付与することにより、移動弁４
を常に一定の力で弁座３に押し付けるよう構成されてい
る。A cylindrical tubular portion 9 extending toward the outlet side is provided at the peripheral portion of the fluid control orifice 7, and the end portion of the tubular portion 9 is formed in the flow passage 1. The opening area between the moving valve 4 and the valve seat 3 at the time of fully opening is set to a predetermined value by abutting the stopper 5 so that the stroke of the moving valve 4 becomes a constant amount. In addition, the above-mentioned spring 2 is mounted in the cylindrical portion 9, and the spring 2 applies an elastic force between the fluid control orifice 7 and the stopper 5, whereby the moving valve 4
Is always pressed against the valve seat 3 with a constant force.
【０００９】[0009]
【作用】このように構成されたものにおいては、入口側
に圧力Ｐ1 の流体が導入されると、弁座３の付近におい
て流体圧力Ｐ1 が作用し、その力がスプリング２の弾発
力を超えた場合に移動弁４を出口側へ移動させて移動弁
４と弁座３との間に隙間を形成して流体を出口側へ導
き、その後はストッパー５で位置決めされるまで移動弁
４を移動し、全開状態となった後は一定の流路を形成し
て流体を出口側へ流出させるという基本的な作用は従来
のこの種チェックバルブと同様であるが、本発明におい
ては移動弁４が全開状態となるまでの流体流路が定まら
ないことによるサージング現象の発生流量域を極めて狭
めることができるものである。In the structure thus constructed, when the fluid having the pressure P 1 is introduced into the inlet side, the fluid pressure P 1 acts in the vicinity of the valve seat 3, and the force is the elastic force of the spring 2. When it exceeds the limit, the moving valve 4 is moved to the outlet side to form a gap between the moving valve 4 and the valve seat 3 to guide the fluid to the outlet side, and thereafter, the moving valve 4 is moved until it is positioned by the stopper 5. The basic action of forming a constant flow path and allowing the fluid to flow out to the outlet side after moving to the fully open state is the same as that of the conventional check valve of this type, but in the present invention, the moving valve is used. It is possible to extremely narrow the flow rate region in which the surging phenomenon occurs because the fluid flow path until 4 is fully opened is not determined.
【００１０】今、流体制御用オリフィスがないと仮定す
ると、流体入口圧力Ｐ1 により移動弁４を左方に押す力
がスプリング２の弾発力を上回った時、移動弁４と弁座
３との間に隙間が生じ流体が出口側へ流れ始め、流体の
圧力Ｐ1 が上昇するにつれて流路形状が一定の場合は流
量は増加し、その部分の圧力損失は大きくなるが、前記
移動弁４の移動に従って弁座３との間の隙間も拡大する
ために弁座３付近の圧力損失が減少し、入口の流体圧力
の上昇は緩和されることとなる。この場合の流体入口圧
力と移動弁４と弁座３との隙間を通る流体流量との関係
を示すと図４の曲線Ａ（破線）として表されるように、
流体流量の増加に伴う流体入口圧力の上昇は緩やかであ
る。そして、流体流量がＱ2 に達した時に移動弁４がス
トッパー５に突き当たって一定の流路が形成されること
となり、それ以後の流量域ではサージング現象の発生は
なくなる。一方、流体制御用オリフィスを有する場合の
オリフィス流体入口圧力と流体流量との関係は図４の曲
線Ｂ（一点鎖線）のように表される。即ち、前記流体制
御用オリフィス７には開孔面積の合計が前記移動弁４の
全開時における移動弁４と弁座３との間の開口面積より
も小さい流体流入孔８が設けられているために、流量増
加に対する圧力の上昇率は曲線Ａよりも急になり、流体
流量がＱ1 に達した時点で移動弁４がストッパー５に突
き当たって一定の流路が形成されることとなる。そし
て、本発明においては曲線Ａと曲線Ｂとの交点Ｓにおけ
る流量をＱ0 とすると、流体流量が０〜Ｑ0 間では移動
弁４と弁座３との隙間の抵抗が流体制御用オリフィス７
の抵抗よりも大きいために全体としての流体入口圧力と
流体流量との関係は曲線Ａに従い、交点Ｓ以降について
は逆に流体制御用オリフィス７の抵抗の方が大きくなっ
て全体としての流体入口圧力と流体流量との関係は曲線
Ｂに従うこととなる。つまり、流体流路が定まらないこ
とによるサージング現象の発生流量域を従来の０〜Ｑ2
から０〜Ｑ1 にまで狭めることになる。Assuming that there is no fluid control orifice, when the force for pushing the moving valve 4 to the left by the fluid inlet pressure P 1 exceeds the elastic force of the spring 2, the moving valve 4 and the valve seat 3 A gap is created between the two, and the fluid begins to flow toward the outlet side, and as the fluid pressure P 1 rises, the flow rate increases if the flow path shape is constant, and the pressure loss in that portion increases, but the moving valve 4 As a result, the gap between the valve seat 3 and the valve seat 3 also increases, so that the pressure loss near the valve seat 3 decreases and the increase in the fluid pressure at the inlet is alleviated. The relationship between the fluid inlet pressure and the fluid flow rate passing through the gap between the movable valve 4 and the valve seat 3 in this case is shown by a curve A (broken line) in FIG.
The increase in the fluid inlet pressure with the increase in the fluid flow rate is moderate. Then, when the fluid flow rate reaches Q 2 , the moving valve 4 abuts on the stopper 5 to form a constant flow path, and the surging phenomenon does not occur in the flow rate region thereafter. On the other hand, the relationship between the orifice fluid inlet pressure and the fluid flow rate in the case of having a fluid control orifice is represented as a curve B (one-dot chain line) in FIG. That is, the fluid control orifice 7 is provided with the fluid inflow hole 8 whose total opening area is smaller than the opening area between the moving valve 4 and the valve seat 3 when the moving valve 4 is fully opened. In addition, the rate of increase in pressure with respect to the increase in the flow rate becomes steeper than that in the curve A, and when the fluid flow rate reaches Q 1 , the moving valve 4 hits the stopper 5 and a constant flow path is formed. When the flow rate at the intersection S between the curves A and B in the present invention and Q 0, the moving valve 4 and the valve seat 3 resistance fluid control orifice 7 of the gap between the between the fluid flow rate 0～Q 0
Since the resistance of the fluid control orifice 7 is larger than the resistance of the fluid control orifice 7, the relationship between the fluid inlet pressure and the fluid flow rate as a whole follows the curve A. The relationship between the fluid flow rate and the fluid flow rate follows the curve B. That is, the occurrence flow rate range of surging due to the fluid flow path not determined prior 0～Q 2
From 0 to Q 1 .
【００１１】また、前記移動弁４の作動開始からストッ
パー５に突き当たるまでの圧力調整はスプリング２の弾
発力の調整により、またフルストロークに達する流量
（Ｑ0）の調整は流体制御用オリフィス７に設ける流体
流入孔８の開孔面積合計値の調整によりそれぞれ容易に
行うことができるので、バルブ作動圧やフルオープン流
量などの多様なニーズに対しても当該部品以外を共通に
して容易に対処することができ高品質のチェックバルブ
を廉価、かつ短期間に製造することも可能となる。な
お、以上の関係は流体の供給を停止する場合にも同様
で、本発明はサージング現象の発生を極力防止して的確
に流体の流出・遮断を自動制御することができるもので
あり、前記のスプリング、移動弁、ストッパー、流体制
御用オリフィス等の形状や位置関係などについては実施
例に限定されるものではなく、本発明の作用効果を奏す
る範囲内において任意に設計変更することができること
は勿論である。The pressure from the start of the operation of the moving valve 4 to the contact with the stopper 5 is adjusted by adjusting the elastic force of the spring 2, and the flow rate (Q 0 ) reaching the full stroke is adjusted by the fluid control orifice 7. Since it can be easily performed by adjusting the total opening area value of the fluid inflow holes 8 provided in the, it is possible to easily deal with various needs such as the valve operating pressure and the full open flow rate in common with other parts. Therefore, it becomes possible to manufacture a high-quality check valve at low cost and in a short period of time. The above relationship is the same when the supply of the fluid is stopped, and the present invention can prevent the occurrence of the surging phenomenon as much as possible and can automatically control the outflow and interruption of the fluid accurately. The shapes, positional relationships, etc. of the springs, moving valves, stoppers, fluid control orifices, etc. are not limited to those in the embodiments, and it is needless to say that the design can be arbitrarily changed within the range in which the effects of the present invention are exhibited. Is.
【００１２】[0012]
【発明の効果】以上の説明からも明らかなように、本発
明はバルブの開閉動作を行う移動弁にこれと一体に移動
する流体制御用オリフィスを取付けてこの流体制御用オ
リフィスに開孔面積の合計が前記移動弁の全開時におけ
る移動弁と弁座間の開口面積よりも小さい流体流入孔を
設けたものとしたので、サージング現象が発生する流量
域を極力短縮化し安定した流体の供給を行うことがで
き、また、下流に装着したスプレーノズル等の寿命を長
くできるので優れた経済性も発揮するなどの利点があ
る。よって本発明は従来の問題点を一掃したチェックバ
ルブとして、産業の発展に寄与するところは極めて大で
ある。As is apparent from the above description, according to the present invention, a moving valve for opening and closing a valve is provided with a fluid control orifice that moves integrally with the moving valve, and the opening area of the fluid control orifice is reduced. Since the total fluid inlet holes are smaller than the opening area between the moving valve and the valve seat when the moving valve is fully opened, the flow rate range where the surging phenomenon occurs is shortened as much as possible to provide a stable fluid supply. Moreover, since the life of the spray nozzle or the like mounted downstream can be extended, there is an advantage that excellent economic efficiency can be exhibited. Therefore, the present invention, as a check valve that eliminates the conventional problems, has an extremely large contribution to industrial development.
【図１】本発明の実施例を示す正面断面図である。FIG. 1 is a front sectional view showing an embodiment of the present invention.
【図２】本発明の実施例を開状態において示す正面断面
図である。FIG. 2 is a front sectional view showing an embodiment of the present invention in an open state.
【図３】本発明の実施例における流体制御用オリフィス
の縦断側面図である。FIG. 3 is a vertical sectional side view of a fluid control orifice according to an embodiment of the present invention.
【図４】本発明における流体の入口圧力と流量との関係
を示すグラフである。FIG. 4 is a graph showing a relationship between a fluid inlet pressure and a flow rate in the present invention.
【図５】本発明を用いた鋼板の冷却装置を示す概略図で
ある。FIG. 5 is a schematic view showing a steel plate cooling device using the present invention.
【図６】チェックバルブの従来例を示す正面断面図であ
る。FIG. 6 is a front sectional view showing a conventional example of a check valve.
【図７】チェックバルブの他の従来例を示す正面断面図
である。FIG. 7 is a front sectional view showing another conventional example of a check valve.
１ 流路 ２ スプリング ３ 弁座 ４ 移動弁 ７ 流体制御用オリフィス ８ 流体流入孔 1 flow path 2 spring 3 valve seat 4 moving valve 7 fluid control orifice 8 fluid inflow hole
Claims (1)
り弁座(3) に押し付けられて閉状態をなすが所定値以上
の流体の押圧力により移動して開状態となる移動弁(4)
を配置したチェックバルブにおいて、前記移動弁(4) に
これと一体に移動する流体制御用オリフィス(7) を取付
け、該流体制御用オリフィス(7) には前記移動弁(4) が
全開された時における移動弁(4) と弁座(3) 間の開口面
積よりも開孔面積の合計が小さい流体流入孔(8) を設け
たことを特徴とするチェックバルブ。1. A movement in which a spring (2) normally presses against a valve seat (3) in a flow path (1) to close it, but it moves by a fluid pressure of a predetermined value or more to open. Valve (4)
In the check valve in which the moving valve (4) is arranged, a fluid control orifice (7) that moves integrally with the moving valve (4) is attached, and the moving valve (4) is fully opened in the fluid control orifice (7). A check valve provided with a fluid inflow hole (8) having a smaller total opening area than the opening area between the moving valve (4) and the valve seat (3) at the time.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4313182A JPH0776589B2 (en) | 1992-11-24 | 1992-11-24 | Check valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4313182A JPH0776589B2 (en) | 1992-11-24 | 1992-11-24 | Check valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06159538A JPH06159538A (en) | 1994-06-07 |
| JPH0776589B2 true JPH0776589B2 (en) | 1995-08-16 |
Family
ID=18038092
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4313182A Expired - Fee Related JPH0776589B2 (en) | 1992-11-24 | 1992-11-24 | Check valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0776589B2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6479413B1 (en) | 2000-08-30 | 2002-11-12 | Benjamin V. Booher | Composite friction elements and pultrusion method of making |
| TW568762B (en) * | 2002-08-23 | 2004-01-01 | Ren-Shiou Tsai | Assembled aircushion with automatic inflation |
| JP2008267399A (en) * | 2007-04-16 | 2008-11-06 | Mitsubishi Heavy Ind Ltd | Delivery valve |
| JP5243172B2 (en) * | 2008-09-30 | 2013-07-24 | 株式会社共立合金製作所 | Liquid leakage prevention valve |
| KR100896751B1 (en) * | 2008-09-30 | 2009-05-11 | 퓨쳐이엔지 주식회사 | Check valve for valve replacing and repairing |
| DE102020110181A1 (en) * | 2020-04-14 | 2021-10-14 | Hanon Systems | Device for damping pressure pulsations for a compressor of a gaseous fluid |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0749018Y2 (en) * | 1989-03-15 | 1995-11-13 | トキコ株式会社 | air compressor |
| JPH0456276U (en) * | 1990-09-20 | 1992-05-14 | ||
| JP3012671U (en) * | 1994-12-19 | 1995-06-20 | ひろみ 榊間 | Perforated inner paper |
-
1992
- 1992-11-24 JP JP4313182A patent/JPH0776589B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06159538A (en) | 1994-06-07 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 19960202 |
|
| LAPS | Cancellation because of no payment of annual fees |