JP3070079B2 - Flow control valve - Google Patents
Flow control valveInfo
- Publication number
- JP3070079B2 JP3070079B2 JP2216851A JP21685190A JP3070079B2 JP 3070079 B2 JP3070079 B2 JP 3070079B2 JP 2216851 A JP2216851 A JP 2216851A JP 21685190 A JP21685190 A JP 21685190A JP 3070079 B2 JP3070079 B2 JP 3070079B2
- Authority
- JP
- Japan
- Prior art keywords
- control valve
- valve body
- fluid
- pressure
- receiving
- 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
Landscapes
- Magnetically Actuated Valves (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は流体の流量を制御する流量制御弁に関する。Description: TECHNICAL FIELD The present invention relates to a flow control valve for controlling a flow rate of a fluid.
従来の技術 流量制御弁において、絞りにより発生する流体の圧力
を受圧体に導き、流量を制御することは既に知られてい
る。すなわち、第３図に示すように本体１内の差圧発生
体２で発生する差圧を受圧体３に導き、受圧体３の力と
スプリング４の力をバランスさせ、受圧体３と一体で動
く弁体５で流量を制御するものである。ここで弁体５
は、流体の一次圧に対してもバランスをとるため弁体の
受圧面積と等しくしたピストン６を設けている。2. Description of the Related Art It is already known to control the flow rate of a flow control valve by guiding the pressure of a fluid generated by a throttle to a pressure receiving body. That is, as shown in FIG. 3, the differential pressure generated by the differential pressure generating body 2 in the main body 1 is guided to the pressure receiving body 3, and the force of the pressure receiving body 3 and the force of the spring 4 are balanced. The flow rate is controlled by the moving valve element 5. Here the valve 5
Is provided with a piston 6 which is equal to the pressure receiving area of the valve body in order to balance the primary pressure of the fluid.
発明が解決しようとする課題 しかしながら上記のような構成では、完全止水が不十
分、それを達成させるには、差圧発生体２において完全
止水しなければならず構成が複雑になってしまう。ま
た、差圧発生体２やピストン６が、流体中のゴミや水垢
で詰まりやすく、耐久的な問題があった。Problems to be Solved by the Invention However, in the above configuration, complete water stoppage is insufficient, and in order to achieve this, complete water stoppage is required in the differential pressure generator 2, which complicates the configuration. . Further, the differential pressure generator 2 and the piston 6 are liable to be clogged with dirt and scale in the fluid, and there is a problem of durability.
本発明はかかる従来の課題を解消するもので、構成が
簡単で、止水も可能で、比例的に流量を調節できる、主
に温水に用いる耐久的に優れた流量制御弁を提供するこ
とを目的とする。SUMMARY OF THE INVENTION The present invention solves the conventional problems, and provides a durable flow control valve having a simple configuration, capable of stopping water, being capable of proportionally adjusting a flow rate, and mainly used for hot water. Aim.
課題を解決するための手段 上記課題を解決するために本発明の流量制御弁は、流
入路と流出路を有する弁筐体と、前記弁筐体内に設け、
流量を調節する円錐状の制御弁体と、それに対応する弁
座と、この制御弁体の後流側に設けた流体力を受ける受
流手段と、前記制御弁体のリフト量にかかわらず前記弁
座の口径と受圧面積が等しい、可撓性の受圧体と、前記
受圧体で１次側と仕切られた背圧室と、前記背圧室と前
記制御弁体の２次側と連通する連通孔と、前記制御弁体
を前記弁座に当接する方向に付勢する付勢手段と、この
付勢手段の付勢力に対抗して、任意の位置に前記制御弁
体をリフトさせる可変操作力発生手段とからなる。Means for Solving the Problems To solve the above problems, a flow control valve of the present invention is provided with a valve housing having an inflow passage and an outflow passage, and provided in the valve housing,
A conical control valve body for adjusting the flow rate, a corresponding valve seat, a flow receiving means provided on the downstream side of the control valve body for receiving a fluid force, and regardless of the lift amount of the control valve body, A flexible pressure receiving member having a valve seat having a diameter equal to a pressure receiving area, a back pressure chamber partitioned from the primary side by the pressure receiving member, and communicating with the back pressure chamber and a secondary side of the control valve body. A communication hole, an urging means for urging the control valve body in a direction of contacting the valve seat, and a variable operation for lifting the control valve body to an arbitrary position against the urging force of the urging means And force generating means.
作用 以上の構成により、可変操作力発生手段の操作力がな
い場合は、付勢手段により制御弁体は弁座に当接し、流
体は流れない。可変操作力発生手段の操作力を加える
と、付勢手段の付勢力に対抗して制御弁体がリフトし、
その操作力の強弱により任意の位置に前記制御弁体をリ
フトさせ流量調節するものである。According to the above configuration, when there is no operating force of the variable operating force generating means, the control valve body contacts the valve seat by the urging means, and no fluid flows. When the operating force of the variable operating force generating means is applied, the control valve body lifts against the urging force of the urging means,
The control valve body is lifted to an arbitrary position depending on the strength of the operation force to adjust the flow rate.
実施例 以下、本発明の実施例を添付図面を用いて説明する。
第１図は、本発明に一実施例における流量制御弁の断面
図である。第１図において、流入路７と流出路８を有す
る弁筐体９と、前記弁筐体９内に、流量を調節する円錐
状の制御弁体10とそれに対応する弁座11を設けている。
前記制御弁体10の後流側に設けた流体力を受ける受流手
段12としてピストン13とから構成している。前記制御弁
体10と流体の１次圧とバランスをとるため、可撓性受圧
体14として溝付きダイヤフラム15を連結しており、更に
溝を深くして、前記制御弁体10のリフト量にかかわら
ず、有効受圧面積が前記弁座11の口径と常に等しくなる
ように構成している。前記ダイヤフラム15で１次側と完
全に仕切られた背圧室16と前記制御弁体10の２次側と
は、連通孔17により連通し、前記制御弁体10は、付勢手
段18としてスプリング19により、前記弁座11に当接する
方向に付勢している。また、可変操作力発生手段20とし
て、ソレノイド21は、このソレノイド21により駆動する
プランジャ22があり、前記プランジャ22は、シャフト23
を介して、前記制御弁体10と連動する構成になってい
る。また、前記ピストン13に対して、弁筐体９にシリン
ダ24を構成し、制御弁体10が所定リフト量を越えると当
接し摺動するものである。Embodiments Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is a sectional view of a flow control valve according to an embodiment of the present invention. In FIG. 1, a valve housing 9 having an inflow passage 7 and an outflow passage 8, and a conical control valve element 10 for adjusting a flow rate and a corresponding valve seat 11 are provided in the valve housing 9. .
A piston 13 is provided as a receiving means 12 provided on the downstream side of the control valve body 10 for receiving a fluid force. In order to balance the primary pressure of the fluid with the control valve body 10, a grooved diaphragm 15 is connected as a flexible pressure receiving body 14, and the groove is further deepened so that the lift amount of the control valve body 10 is reduced. Regardless, the configuration is such that the effective pressure receiving area is always equal to the diameter of the valve seat 11. The back pressure chamber 16 completely separated from the primary side by the diaphragm 15 and the secondary side of the control valve element 10 communicate with each other through a communication hole 17. 19 urges the valve seat 11 in a direction in which it comes into contact with the valve seat 11. Further, as the variable operating force generating means 20, the solenoid 21 includes a plunger 22 driven by the solenoid 21, and the plunger 22 includes a shaft 23.
Through the control valve body 10. Further, a cylinder 24 is formed in the valve housing 9 with respect to the piston 13, and the control valve body 10 comes into contact with and slides when the control valve body 10 exceeds a predetermined lift amount.
以上の構成で、前記ソレノイド21に通電していない状
態では、前記スプリング19により制御弁体10は弁座11に
当接し、流体は流れない。前記ソレノイド21に通電する
と、前記プランジャ22を吸引或いは押出し、前記スプリ
ング19の付勢力に対抗して、前記制御弁体10をリフトさ
せ、流体が流れ始める。つまり、ソレノイド21への通電
量を変えることにより、前記制御弁体10を任意のリフト
量に調整し流量を制御するものである。With the above configuration, when the solenoid 21 is not energized, the spring 19 causes the control valve body 10 to abut on the valve seat 11 and no fluid flows. When the solenoid 21 is energized, the plunger 22 is sucked or pushed out, the control valve body 10 is lifted against the urging force of the spring 19, and the fluid starts flowing. That is, by changing the amount of current supplied to the solenoid 21, the control valve body 10 is adjusted to an arbitrary lift amount to control the flow rate.
本実施例では可変操作力発生手段20として、ソレノイ
ド21と、このソレノイド21により駆動するプランジャ22
でシャフト23を介して、前記制御弁体10リフトさせる構
成であり、プランジャ22の推進力は比較的小さく、可撓
性受圧体14として溝付きダイヤフラム15を設けて、制御
弁体10のリフト量にかかわらず、有効受圧面積が前記弁
座11の口径と常に等しくなるように構成して、流体の圧
力に対してバランスをとっている。しかし、前記制御弁
体10のように、円錐形状の弁の場合、制御弁体10と弁座
11間の開口部を通過する流体の流速が大きくなると、前
記制御弁体10にかかる静圧分が小さくなり、ダイヤフラ
ム15と制御弁体10の有効受圧面積にズレを生じ、前記ダ
イヤフラム15が相対的に大きくなり、流体の圧力により
前記ダイヤフラム15側に制御弁体10が引かれ、流量を絞
ることになる。第４図は、この場合の動作特性を、ソレ
ノイド21へ流す電流値を一定にして、流体の１次圧力と
流量の関係を示している。本実施例では、制御弁体10の
後流側に設けた流体力を受ける受流手段12として、ピス
トン13を設けている。これは制御弁体10と弁座11間の開
口部を通過した後で、その流体の流体力を制御弁体10に
作用させるためのもので、ダイヤフラム15と制御弁体10
の有効受圧面積にズレを生じ、前記ダイヤフラム15が相
対的に大きくなり、流体の圧力により、前記ダイヤフラ
ム15側に制御弁体10が引かれ、流量を絞る方向に作用す
る、その力に対抗させるものである。第２図に、本実施
例における、流体の１次圧力と流量の関係を示してい
る。つまり本実施例の場合、流体の１次圧に関係なく、
ソレノイド21へ流す流量値と流体の流量値が一対一で決
まるものである。In this embodiment, a solenoid 21 and a plunger 22 driven by the solenoid 21 are used as the variable operating force generating means 20.
The control valve body 10 is lifted via a shaft 23. The propulsive force of the plunger 22 is relatively small, and a grooved diaphragm 15 is provided as a flexible pressure receiving body 14, and the lift amount of the control valve body 10 is increased. Irrespective of the above, the pressure receiving area is configured so that the effective pressure receiving area is always equal to the diameter of the valve seat 11 so as to balance the pressure of the fluid. However, in the case of a conical valve like the control valve body 10, the control valve body 10 and the valve seat
When the flow rate of the fluid passing through the opening between the openings 11 increases, the static pressure applied to the control valve body 10 decreases, and the effective pressure receiving area between the diaphragm 15 and the control valve body 10 shifts, and the relative movement of the diaphragm 15 increases. The control valve element 10 is pulled toward the diaphragm 15 by the pressure of the fluid, and the flow rate is reduced. FIG. 4 shows the relationship between the primary pressure and the flow rate of the fluid when the current flowing through the solenoid 21 is kept constant. In the present embodiment, a piston 13 is provided as the flow receiving means 12 provided on the downstream side of the control valve body 10 for receiving the fluid force. This is to cause the fluid force of the fluid to act on the control valve body 10 after passing through the opening between the control valve body 10 and the valve seat 11, and the diaphragm 15 and the control valve body 10
Causes a shift in the effective pressure receiving area of the diaphragm 15, the diaphragm 15 becomes relatively large, and the pressure of the fluid causes the control valve body 10 to be pulled toward the diaphragm 15 to act in the direction of reducing the flow rate, thereby opposing the force. Things. FIG. 2 shows the relationship between the primary pressure and the flow rate of the fluid in this embodiment. That is, in the case of the present embodiment, regardless of the primary pressure of the fluid,
The flow value flowing to the solenoid 21 and the flow value of the fluid are determined on a one-to-one basis.
以上のように本実施例の流量制御弁によれば、制御弁
体10と可撓性受圧体14としての溝付きダイヤフラム15の
間で流体の１次圧、２次圧共にバランスをとる構成にな
っているため、前記制御弁体10は流体の圧力による荷重
が相殺され、小さな駆動力で駆動することが可能で、ソ
レノイド21もコンパクトなもので消費電力も少ない。ま
た、前記溝付きダイヤフラム15の溝を深くして、前記制
御弁体10のリフト量にかかわらず、有効受圧面積が前記
弁座11の口径と常に等しくなるように構成しているた
め、前記制御弁体10がリフトして、流体が流れ、その流
速が大きくなると制御弁体10にかかる静圧分が小さくな
り、相対的にダイヤフラム13側の受圧面積が大きくなる
のと同じで、制御弁体10のリフトを抑える方向に荷重が
加わり、流体の１次圧が高ければ高いほど、その荷重が
大きくなる。その荷重に対して、制御弁体10の後流側に
設けた流体力を受ける受流手段12として、ピストン13を
設けたことにより、制御弁体10と弁座11間の開口部を通
過した後で、その流体の流体力を制御弁体10に作用さ
せ、前述した荷重とバランスをとり、ソレノイド21への
通電量と流量が流体の１次圧力に関係なく一対一で対応
するものである。As described above, according to the flow control valve of the present embodiment, the primary pressure and the secondary pressure of the fluid are balanced between the control valve body 10 and the grooved diaphragm 15 as the flexible pressure receiving body 14. As a result, the load caused by the pressure of the fluid is offset in the control valve element 10, and the control valve element 10 can be driven with a small driving force. The solenoid 21 is also compact and consumes little power. Further, since the groove of the grooved diaphragm 15 is deepened so that the effective pressure receiving area is always equal to the diameter of the valve seat 11 regardless of the lift amount of the control valve body 10, the control is performed. When the valve body 10 is lifted, the fluid flows, and the flow velocity increases, the static pressure applied to the control valve body 10 decreases, and the pressure receiving area on the diaphragm 13 side relatively increases. A load is applied in the direction of suppressing the lift of 10, and the higher the primary pressure of the fluid, the greater the load. With respect to the load, the piston 13 is provided as the receiving means 12 for receiving the fluid force provided on the downstream side of the control valve body 10, so that the piston passes through the opening between the control valve body 10 and the valve seat 11. Later, the fluid force of the fluid is applied to the control valve body 10 to balance with the above-mentioned load, so that the amount of electricity supplied to the solenoid 21 and the flow rate correspond one-to-one regardless of the primary pressure of the fluid. .
また本実施例では、前記ピストン13に対して、弁筐体
９にシリンダ24を構成し、制御弁体10が所定リフト量を
越えると当接し摺動する構成しているため、制御弁体10
のリフト量が小さく少ない流量で制御している時は、シ
リンダ24はピストン13と離れ、摺動抵抗がまったく生じ
ず、微妙な調整に可能であり、リフト量が所定値を越え
るような大流量の時は、制御弁体10と弁座11間の開口部
を通過する流速も大きく、制御弁体10が流れによりすり
こぎ状に動かされ振動することがある。その場合、ピス
トン13はシリンダ24に当接し、振動を防止する効果があ
る。In this embodiment, a cylinder 24 is formed in the valve housing 9 with respect to the piston 13, and the control valve body 10 is configured to abut and slide when the lift exceeds a predetermined lift amount.
When the lift amount is small and the flow rate is controlled at a small flow rate, the cylinder 24 separates from the piston 13, no sliding resistance is generated, and fine adjustment is possible. In this case, the flow velocity passing through the opening between the control valve element 10 and the valve seat 11 is also large, and the control valve element 10 may be moved in a pestle shape by the flow and vibrate. In this case, the piston 13 comes into contact with the cylinder 24, and has an effect of preventing vibration.
発明の効果 以上のように本発明の流量制御弁によれば、次の効果
が得られる。Effects of the Invention As described above, according to the flow control valve of the present invention, the following effects can be obtained.
（１） 制御弁体と可撓性受圧体の間で、流体の１次
圧、２次圧共にバランスをとる構成になっていると共
に、前記制御弁体の後流側に設けた流体力を受ける受流
手段により、流体の流量に対してもバランスをとる構成
のため、前記制御弁体は元圧の変化や、制御弁下流に取
り付けられる機器の抵抗の大きさに影響されず、可変操
作力発生手段の操作量と流量が流体の１次圧力に関係な
く一対一で対応するものである。(1) The primary pressure and the secondary pressure of the fluid are balanced between the control valve body and the flexible pressure receiving body, and the fluid force provided on the downstream side of the control valve body is The control valve body is configured not to be affected by the change of the original pressure or the magnitude of the resistance of the equipment attached downstream of the control valve, so that the variable operation can be performed. The operation amount and the flow rate of the force generating means correspond one to one regardless of the primary pressure of the fluid.
（２） 弁筐体にシリンダを構成し、制御弁体が所定リ
フト量を越えると当接し摺動する構成しているため、大
流量の時は、制御弁体が流れによりすりこぎ状に動かさ
れて振動することを防止する効果がある。(2) A cylinder is formed in the valve housing, and when the control valve body exceeds a predetermined lift amount, it comes into contact with and slides. Therefore, when the flow rate is large, the control valve body moves in a swirl shape by the flow. This has the effect of preventing vibrations.
第１図は本発明の一実施例の流量制御弁の断面図、第２
図は本発明の一実施例の流量制御弁の電流値一定で流体
の１次圧力と流量を示す特性図、第３図は従来の流量制
御弁の断面図、第４図は従来の流量制御弁の電流値一定
で流体の１次圧力と流量を示す特性図である。 ７……流入路、８……流出路、９……弁筐体、10……制
御弁体、11……弁座、12……受流手段、14……受圧体、
16……背圧室、17……連通孔、18……付勢手段、20……
可変操作力発生手段。FIG. 1 is a sectional view of a flow control valve according to an embodiment of the present invention, and FIG.
FIG. 3 is a characteristic diagram showing the primary pressure and flow rate of a fluid at a constant current value of a flow control valve according to one embodiment of the present invention. FIG. 3 is a sectional view of a conventional flow control valve. FIG. 5 is a characteristic diagram showing a primary pressure and a flow rate of a fluid at a constant valve current value. 7 inflow passage, 8 outflow passage, 9 valve housing, 10 control valve body, 11 valve seat, 12 flow receiving means, 14 pressure receiving body,
16 ... back pressure chamber, 17 ... communication hole, 18 ... biasing means, 20 ...
Variable operating force generating means.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 長岡 行夫 大阪府門真市大字門真1006番地 松下電 器産業株式会社内 (72)発明者 芝 文一 大阪府門真市大字門真1006番地 松下電 器産業株式会社内 (56)参考文献 特開 昭62−137480（ＪＰ，Ａ) 特開 昭57−54787（ＪＰ，Ａ) 特開 昭60−215170（ＪＰ，Ａ) 特開 昭59−170640（ＪＰ，Ａ) 実開 昭62−54374（ＪＰ，Ｕ) 実開 昭63−184282（ＪＰ，Ｕ) 特公 昭62−31231（ＪＰ，Ｂ２) 特公 昭63−14367（ＪＰ，Ｂ２) (58)調査した分野(Int.Cl.7，ＤＢ名) F16K 31/06 - 31/11 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Yukio Nagaoka 1006 Kazuma Kadoma, Osaka Prefecture Inside Matsushita Electric Industrial Co., Ltd. In-company (56) References JP-A-62-137480 (JP, A) JP-A-57-54787 (JP, A) JP-A-60-215170 (JP, A) JP-A-59-170640 (JP, A) Japanese Utility Model Showa 62-54374 (JP, U) Japanese Utility Model Showa 63-184282 (JP, U) Japanese Patent Publication 62-31231 (JP, B2) Japanese Patent Publication 63-14367 (JP, B2) (58) Field (Int.Cl. 7 , DB name) F16K 31/06-31/11
Claims (2)
筐体内に設け、流量を調節する円錐状の制御弁体と、そ
れに対応する弁座と、前記制御弁体の後流側に設けた流
体力を受ける受流手段と、前記制御弁体のリフト量にか
かわらず前記弁座の口径と受圧面積が等しい可撓性の受
圧体と、前記受圧体で１次側と仕切られた背圧室と、前
記背圧室と前記制御弁体の２次側と連通する連通孔と、
前記制御弁体を前記弁座に当接する方向に付勢する付勢
手段と、この付勢手段の付勢力に対抗して、任意の位置
に前記制御弁体をリフトさせる可変操作力発生手段とか
らなる流量制御弁。1. A valve housing having an inflow passage and an outflow passage, a conical control valve body provided in the valve housing for adjusting a flow rate, a corresponding valve seat, and a wake of the control valve body. Receiving means provided on the side for receiving a fluid force, a flexible pressure receiving body having a pressure receiving area equal to the diameter of the valve seat regardless of the lift amount of the control valve body, and a primary side partitioned by the pressure receiving body. And a communication hole communicating with the back pressure chamber and the secondary side of the control valve body.
Urging means for urging the control valve body in a direction in which it comes into contact with the valve seat, and variable operating force generating means for lifting the control valve body to an arbitrary position in opposition to the urging force of the urging means; Flow control valve consisting of.
受流手段は、円盤状のピストンで構成し、弁筐体にはシ
リンダを設け、前記ピストン制御弁体が所定リフト量を
越えると、前記シリンダに当接する構成とした特許請求
の範囲第１項記載の流量制御弁。2. The receiving means provided on the downstream side of the control valve body for receiving a fluid force is constituted by a disk-shaped piston, a cylinder is provided in a valve housing, and the piston control valve body has a predetermined lift amount. 2. The flow control valve according to claim 1, wherein the flow control valve is configured to come into contact with the cylinder when the pressure exceeds the limit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2216851A JP3070079B2 (en) | 1990-08-16 | 1990-08-16 | Flow control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2216851A JP3070079B2 (en) | 1990-08-16 | 1990-08-16 | Flow control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04102778A JPH04102778A (en) | 1992-04-03 |
| JP3070079B2 true JP3070079B2 (en) | 2000-07-24 |
Family
ID=16694903
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2216851A Expired - Fee Related JP3070079B2 (en) | 1990-08-16 | 1990-08-16 | Flow control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3070079B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5292231B2 (en) * | 2009-09-01 | 2013-09-18 | 川崎重工業株式会社 | Control valve |
| JP5911706B2 (en) * | 2011-11-28 | 2016-04-27 | 株式会社不二工機 | Motorized valve |
-
1990
- 1990-08-16 JP JP2216851A patent/JP3070079B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH04102778A (en) | 1992-04-03 |
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