JP4614103B2 - Pressure reducing valve for fine pressure - Google Patents

Pressure reducing valve for fine pressure Download PDF

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JP4614103B2
JP4614103B2 JP2006225972A JP2006225972A JP4614103B2 JP 4614103 B2 JP4614103 B2 JP 4614103B2 JP 2006225972 A JP2006225972 A JP 2006225972A JP 2006225972 A JP2006225972 A JP 2006225972A JP 4614103 B2 JP4614103 B2 JP 4614103B2
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秀一 小林
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Description

本発明は、一次側から供給される高圧ガスを微圧力に調圧し、二次側に出力する小型の微圧用減圧弁に関するものである。 The present invention, by regulating the high pressure gas supplied from the primary side to the fine pressure, to a fine pressure reducing valve compact to be output to the secondary side.

従来技術に係る減圧弁を図3に示す。一次側ポート51と二次側ポート52との間に形成された弁穴54の開口部に弁座55を設け、この弁座55を開閉する弁体56を弁軸57に設けるとともに、弁軸57の上端部にリリーフ機構を備えたダイヤフラム58が配置されている。 A pressure reducing valve according to the prior art is shown in FIG. A valve seat 55 is provided at the opening of a valve hole 54 formed between the primary port 51 and the secondary port 52, and a valve body 56 for opening and closing the valve seat 55 is provided on the valve shaft 57, and the valve shaft A diaphragm 58 having a relief mechanism is disposed at the upper end of 57.

このダイヤフラム58は中央をリリーフシート59とリテーナ61に挟まれ一体となっている。リテーナ61上部には弁体56を開く方向にバネ力を付勢するとともにそのバネ力を変化させて二次側圧力を調整するための調圧バネ66、調圧ネジ64が設けられている。またダイヤフラム58により区画形成されたダイヤフラム室62は連通路72により二次側ポート52に通じている。 The diaphragm 58 is integrated with a relief sheet 59 and a retainer 61 at the center. The retainer 61 is provided with a pressure adjusting spring 66 and a pressure adjusting screw 64 for biasing a spring force in the direction of opening the valve body 56 and adjusting the secondary side pressure by changing the spring force. The diaphragm chamber 62 defined by the diaphragm 58 communicates with the secondary port 52 through the communication path 72.

本体下部には弁座55の口径に相当する内径の室67が設けられその内壁を弁軸57下部は摺動する。シール70は一次側圧力が室67に漏れるのを防止し、二次側ポート52と室67は連通路71で通じて弁軸57への一次側圧力の影響を避ける構造となっている。また、弁軸57下部には弁体56を閉じる方向に圧縮バネ68が配置されている。 A chamber 67 having an inner diameter corresponding to the diameter of the valve seat 55 is provided at the lower part of the main body, and the lower part of the valve shaft 57 slides on the inner wall thereof. The seal 70 prevents the primary side pressure from leaking into the chamber 67, and the secondary side port 52 and the chamber 67 are connected to each other through the communication path 71 to avoid the influence of the primary side pressure on the valve shaft 57. A compression spring 68 is disposed below the valve shaft 57 in a direction to close the valve body 56.

この減圧弁の概略動作を説明すると、調圧ネジ64を加圧方向に回転させ調圧バネ66による付勢力をダイヤフラム58に与えると、ダイヤフラム58は弁軸57上端部を押圧しながら下降し、弁体56は弁座55を離れ一次側ポート51の高圧ガスは弁体56と弁座55の間を流れ弁穴54を通過し二次側ポート52に至る。室67及びダイヤフラム室62とも連通路71、72を通じて二次側ポート52と同圧となる。二次側圧力が上昇してくるとその圧力を受けダイヤフラム58が上昇し、それに応じて弁軸57も上昇、弁体56は弁座55を閉じはじめてついには完全に閉じる。このときの二次側圧力が設定圧である。 Explaining the general operation of this pressure reducing valve, when the pressure adjusting screw 64 is rotated in the pressurizing direction and the urging force by the pressure adjusting spring 66 is applied to the diaphragm 58, the diaphragm 58 descends while pressing the upper end of the valve shaft 57, The valve body 56 leaves the valve seat 55, and the high-pressure gas in the primary port 51 flows between the valve body 56 and the valve seat 55, passes through the valve hole 54, and reaches the secondary port 52. Both the chamber 67 and the diaphragm chamber 62 have the same pressure as the secondary port 52 through the communication passages 71 and 72. When the secondary pressure rises, the diaphragm 58 rises in response to the pressure, the valve shaft 57 rises accordingly, and the valve body 56 begins to close the valve seat 55 and finally closes completely. The secondary pressure at this time is the set pressure.

二次側圧力が設定圧を超えたときは、ダイヤフラム58に作用するガス圧の力が調圧バネ66による付勢力に勝り、弁体56が弁座55に圧接した状態のもとでダイヤフラム58は上昇し、これによりリリーフシート59は弁軸57上端部より離れリリーフ穴60が開通し、ダイヤフラム室62のガスは大気圧室63及び通気穴73を通り外部へ排出され、その結果二次側圧力は設定圧に戻される。 When the secondary pressure exceeds the set pressure, the force of the gas pressure acting on the diaphragm 58 surpasses the urging force of the pressure regulating spring 66, and the diaphragm 58 is pressed against the valve seat 55. As a result, the relief seat 59 is separated from the upper end of the valve shaft 57, the relief hole 60 is opened, and the gas in the diaphragm chamber 62 is discharged to the outside through the atmospheric pressure chamber 63 and the vent hole 73. The pressure is returned to the set pressure.

本形式による減圧弁の出力流量は弁座55口径面積より弁軸57断面積を減じた値に比例する。従って要求される減圧弁出力流量が僅かの場合に備え、弁座55附近のガス通過面積を小さくして減圧弁全体形状の小型化を図っても、弁座55穴の中を弁軸57が貫通する隙間構造なので、紙上の計算としては成立するが加工上の問題や使用上弁座55周辺の詰りで一定の限界がある。つまり小流量用には不向きな構造である。また室67が二次側ポート52と通じて一次圧変化の影響を受けない構造としても、シール70、74は弁軸57に対し摺動抵抗となり、本形式による減圧弁を微圧用減圧弁として使用する場合は誤差の要素となる。 The output flow rate of the pressure reducing valve in this form is proportional to the value obtained by subtracting the cross-sectional area of the valve shaft 57 from the area of the valve seat 55 bore. Thus reducing valve output flow that is required in case Kano small quantity, also to reduce the gas passage area of the valve seat 55 vicinity reduce the size of the entire pressure reducing valve configuration, the valve shaft through the valve seat 55 hole 57 since there gap structure penetrating, satisfied as a calculation on paper there is a certain limit in clogging around issues and using upper valve seat 55 on the work. That is, the structure is not suitable for a small flow rate. Even if the chamber 67 is connected to the secondary side port 52 and is not affected by the change in the primary pressure, the seals 70 and 74 have sliding resistance against the valve shaft 57, and the pressure reducing valve of this type is used as a pressure reducing valve for fine pressure. When used, it becomes an error factor.

減圧弁を使用する機器の減圧弁に対する要求が小流量な微圧出力である場合、従来の減圧弁では小型化に限界があり「大は小を兼ねる」の認識のもと仕様過剰で高価なものでも使用せざるを得なかった。
本発明はこのような点に鑑みなされたもので、小型化が容易で安価な微圧用減圧弁を提供するものである。 If the request for a pressure reducing valve of the device that uses the pressure reducing valve is a small flow rate fine pressure output, based on specifications excessive and expensive recognition of the conventional pressure reducing valve has a limit to the miniaturization "large doubles as a small" I was forced to use even a thing.
The present invention has been made in view of these points, and provides a pressure reducing valve for fine pressure that is easy to downsize and inexpensive.

請求項１記載の発明は、一次側ポートと二次側ポートに通じるダイヤフラム室とを連通させる円筒状弁穴が形成された非磁性の基体と、
前記弁穴の端部に形成された非磁性の弁座に接触する円筒軸方向に移動自在な円形磁石を内蔵の非磁性の主弁と、
リング磁石ホルダを介してリング磁石と一体化したダイヤフラムとを有し、
前記ダイヤフラムのリング磁石ホルダの円筒開部に前記円筒状弁穴が一部に入り込む構造とすることにより、
調圧バネの付勢力に対抗して二次側圧力により発生する前記ダイヤフラムの作動力でリン
グ磁石を従動させリング磁石と前記円形磁石内蔵の主弁との間に磁気吸引力が働き、
前記円筒状弁穴内にて前記主弁の開閉を行わせる調圧機構とを具備する微圧用減圧弁。 The invention according to claim 1 is a non-magnetic base body in which a cylindrical valve hole for communicating a primary side port and a diaphragm chamber communicating with a secondary side port is formed;
A non-magnetic main valve containing a circular magnet movable in the direction of the cylindrical axis that contacts a non-magnetic valve seat formed at the end of the valve hole;
Having a diaphragm integrated with the ring magnet via the ring magnet holder ,
By adopting a structure in which the cylindrical valve hole partially enters the cylindrical opening of the ring magnet holder of the diaphragm ,
The operating force of the diaphragm generated by the secondary side pressure against the biasing force of the pressure adjusting spring
Magnetic attraction force is generated between the ring magnet is driven with the circular magnet built of the main valve a grayed magnet,
Fine pressure reducing valve you and a pressure regulating mechanism for causing the opening and closing of the main valve in the cylindrical valve bore.

請求項1記載の発明によれば、調圧ネジによる付勢力と対抗する二次側圧力により発生するダイヤフラムの作動力を、磁力伝動である吸引力を利用することにより、隔壁を介した主弁を切換えることが可能となる。従って従来の減圧弁における伝動軸としての弁軸と軸シールは不要となり、かつ弁軸より生ずる摺動抵抗は生じません。その結果、一次側圧力を微圧力に調圧し、二次側に出力する微圧用減圧弁が可能となる。
また請求項1記載の発明による減圧弁によれば、弁座内の軸が貫通しない構造なので、従来の弁座穴の中を弁軸が貫通する構造に比べ加工上の問題や使用上の弁座の詰りで一定の限界があった弁座口径よりも小径な弁座を採用でき、流量出力を小さくした小型の微圧減圧弁も可能となる。 According to the invention described in claim 1, the operation force of the diaphragm generated by the secondary side pressure that opposes the urging force by the pressure adjusting screw is used as the main valve via the partition wall by using the suction force that is magnetic transmission. Can be switched. Thus the valve shaft and shaft seal as a transmission shaft in a conventional pressure reducing valves required and Do Ri, and do not cause sliding resistance resulting from the valve shaft. As a result, a pressure reducing valve for fine pressure that regulates the primary side pressure to a small pressure and outputs the pressure to the secondary side becomes possible.
Further, according to the pressure reducing valve according to the invention of claim 1, since the shaft in the valve seat does not penetrate, the processing problem and the valve in use are compared with the conventional structure in which the valve shaft penetrates the valve seat hole. A valve seat having a diameter smaller than the diameter of the valve seat having a certain limit due to clogging of the seat can be adopted, and a small-sized fine pressure reducing valve with a reduced flow output is also possible.

本発明の実施の形態を図1及び図2に基づいて詳細に説明する。 An embodiment of the present invention will be described in detail based on FIG. 1 and FIG.

図１は本発明の一実施の形態である減圧弁の断面図であり、非磁性体の基体1中央下部に、円筒状の弁穴5と上端部には気密用のパッキン9とネジ結合の非磁性体による弁座10を設け、その弁穴5内にパッキン6、円形磁石7を接着内蔵した非磁性六角棒部材より成る主弁8を設ける。円形磁石7は図中上下方向に磁極を有するものである。また主弁8は摺動自在で弁座10とキャップ2により上下移動を一定の範囲に規制されている。 FIG. 1 is a cross-sectional view of a pressure reducing valve according to an embodiment of the present invention. A non-magnetic base body 1 has a central lower portion, a cylindrical valve hole 5, an upper end portion and an airtight packing 9 and a screw connection. A valve seat 10 made of a non-magnetic material is provided, and a main valve 8 made of a non-magnetic hexagonal bar member in which a packing 6 and a circular magnet 7 are built in is provided in the valve hole 5. The circular magnet 7 has magnetic poles in the vertical direction in the figure. The main valve 8 is slidable, and its vertical movement is restricted to a certain range by the valve seat 10 and the cap 2.

基体1の上部にはダイヤフラム11がカバー24と止め輪25により取付けられ、下側はダイヤフラム室12、上側は大気圧室13を区画形成している。このダイヤフラム11には通気穴15の開いた非磁性部材によるリング磁石ホルダ14とリテーナ17がダイヤフラム11を挟んだ状態で固着され、なお中央にはリリーフ弁座19も固着されている。リング磁石ホルダ14の下部には厚み方向に磁極を有するリング磁石16が固着されダイヤフラム11の動きに従動する。このリング磁石16と主弁8に内蔵の円形磁石7との磁極の関係はダイヤフラム11の上下移動ストローク内では、常時「吸引」動作の関係とする。この磁気伝動によりダイヤフラム11が上下移動ストローク内の上方にあるときは主弁8を閉じ、下方にあるときは主弁8を開く。 A diaphragm 11 is attached to the upper portion of the base 1 by a cover 24 and a retaining ring 25, and a diaphragm chamber 12 is formed on the lower side and an atmospheric pressure chamber 13 is formed on the upper side. A ring magnet holder 14 and a retainer 17 made of a nonmagnetic member having a vent hole 15 are fixed to the diaphragm 11 with the diaphragm 11 sandwiched therebetween, and a relief valve seat 19 is also fixed at the center. A ring magnet 16 having a magnetic pole in the thickness direction is fixed to the lower part of the ring magnet holder 14 and is driven by the movement of the diaphragm 11. The relationship between the magnetic poles of the ring magnet 16 and the circular magnet 7 built in the main valve 8 is always a “suction” operation within the vertical movement stroke of the diaphragm 11. By this magnetic transmission, the main valve 8 is closed when the diaphragm 11 is above the vertical movement stroke, and the main valve 8 is opened when it is below.

リリーフ弁座19に形成された弁穴20の開口部側端面はリリーフ弁18の弁座を形成し、弁穴20の上部側壁には通気穴21を設け、かつ最上部はリリーフ弁18の弁軸が摺動自在に形成されている。リリーフ弁18は弁部がリリーフ弁座19に一定の力で付勢されるようリリーフ弁座19を貫通したリリーフ弁18の弁軸に圧縮バネ22を通しナット部材23で圧縮量を一定の値に規制する。 The opening side end face of the valve hole 20 formed in the relief valve seat 19 forms the valve seat of the relief valve 18, the vent hole 21 is provided in the upper side wall of the valve hole 20, and the uppermost part is the valve of the relief valve 18. The shaft is slidably formed. The relief valve 18 has a compression spring 22 inserted through the valve shaft of the relief valve 18 passing through the relief valve seat 19 so that the valve portion is urged to the relief valve seat 19 with a constant force. To regulate.

カバー24中心に上下移動をストッパー28で規制された調圧ネジ29が回転自在に取付けられ、この調圧ネジ29に回り止め30により回転を規制されたバネ受け31がネジ結合している。このバネ受け31とダイヤフラム11上部のリテーナ17との間に圧縮コイルバネが調圧バネ32として装着されている。従って調圧ネジ29を回転させるとバネ受け31が軸方向へ移動し調圧バネ29の圧縮量を変化させる。この調圧バネ29の圧縮による力がダイヤフラム11を下方向に付勢する。付勢力が「０」のとき、すなわち調圧ネジ29が減圧方向に回転し、バネ受け31が移動範囲上限に達したときは装着された調圧バネ32は自由長に復帰する。このときの上下移動ストローク内に於けるダイヤフラム11位置は中間附近とし、そして磁気伝動により主弁8を閉じている位置とする。 A pressure adjusting screw 29 whose vertical movement is restricted by a stopper 28 is rotatably attached to the center of the cover 24, and a spring receiver 31 whose rotation is restricted by a detent 30 is screwed to the pressure adjusting screw 29. A compression coil spring is mounted as a pressure adjusting spring 32 between the spring receiver 31 and the retainer 17 at the upper part of the diaphragm 11. Therefore, when the pressure adjusting screw 29 is rotated, the spring receiver 31 moves in the axial direction, and the compression amount of the pressure adjusting spring 29 is changed. The force generated by the compression of the pressure adjusting spring 29 urges the diaphragm 11 downward. When the urging force is “0”, that is, when the pressure adjusting screw 29 rotates in the pressure reducing direction and the spring receiver 31 reaches the upper limit of the moving range, the mounted pressure adjusting spring 32 returns to the free length. At this time, the position of the diaphragm 11 in the up-and-down movement stroke is close to the middle, and the main valve 8 is closed by magnetic transmission.

また調圧ネジ29中心にはリリーフ弁18を作動させる押ネジ33がネジ結合されている。
ダイヤフラム室12の二次側圧力が何らかの原因で設定圧を越え上昇したとき、ダイヤフラム11は設定圧に於ける位置より上昇する。押ネジ33が適当な位置にあると、リリーフ弁18弁軸端を押ネジ33最下端が押圧するかたちになり、リリーフ弁18が作動する。押ネジ33位置を調整することによりリリーフ圧力は一定の範囲で調整可能になる。 A push screw 33 for operating the relief valve 18 is screwed to the center of the pressure adjusting screw 29.
When the secondary side pressure of the diaphragm chamber 12 rises above the set pressure for some reason, the diaphragm 11 rises from a position at the set pressure. When the push screw 33 is in an appropriate position, the relief valve 18 is actuated so that the lower end of the push screw 33 presses the valve shaft end of the relief valve 18. By adjusting the position of the push screw 33, the relief pressure can be adjusted within a certain range.

設定圧に於けるダイヤフラム11の位置とリリーフ弁18が作動するダイヤフラム11の位置は異なるので、当然双方の圧力も異なる。双方の圧力を生じるダイヤフラム11の位置の差をLとし、リリーフ圧力と設定圧力との差をΔP、リリーフ弁18への圧縮バネによる付勢力をFr、リリーフ弁18に作用する二次側ガス圧力による付勢力をFp、調圧バネ32のバネ定数をk1、圧縮バネ22のバネ定数をk2、リリーフ弁18の有効弁ストロークをΔL、
ダイヤフラム11の有効受圧面積をＡ、とすれば次なる式が成立する。 Since the position of the diaphragm 11 at the set pressure is different from the position of the diaphragm 11 at which the relief valve 18 is operated, naturally both pressures are also different. The difference in the position of the diaphragm 11 that generates both pressures is L, the difference between the relief pressure and the set pressure is ΔP, the biasing force of the compression spring to the relief valve 18 is Fr, and the secondary gas pressure acting on the relief valve 18 , The spring constant of the pressure adjusting spring 32 is k1, the spring constant of the compression spring 22 is k2, the effective valve stroke of the relief valve 18 is ΔL,
If the effective pressure receiving area of the diaphragm 11 is A, the following equation is established.

[数１]
ΔP＝｛Fr＋Fp＋k1(L+ΔL)＋k2・ΔL｝／Ａ [Equation 1]
ΔP = {Fr + Fp + k1 (L + ΔL) + k2 · ΔL} / A

次に実施例の作動について説明する。 Next, the operation of the embodiment will be described.

二次側ポート27に圧力計を接続後、一次側ポート4に高圧ガスを供給する。調圧ネジ29を加圧方向に回転させると、調圧バネ32の下向き付勢力によりダイヤフラム11が下降する。ダイヤフラム11に従動するリング磁石16も下降し、磁気伝動により円形磁石7内蔵の主弁8も弁座10を離れ下降、弁開状態となりダイヤフラム室12に高圧ガスが流れる。
二次側ポート27の圧力増大に伴いダイヤフラム11は上昇する。その結果リング磁石16は主弁8を磁気伝動により吸引しながら上昇し、ついには弁座10を閉じる位置まで上昇する。これにより高圧ガスの流入がなくなりダイヤフラム11の上昇も停止し、二次側圧力は安定する。この圧力が設定圧である。 After connecting a pressure gauge to the secondary side port 27, high pressure gas is supplied to the primary side port 4. When the pressure adjusting screw 29 is rotated in the pressurizing direction, the diaphragm 11 is lowered by the downward biasing force of the pressure adjusting spring 32. The ring magnet 16 driven by the diaphragm 11 is also lowered, and the main valve 8 built in the circular magnet 7 is also moved away from the valve seat 10 by the magnetic transmission, so that the valve is opened and high-pressure gas flows into the diaphragm chamber 12.
As the pressure at the secondary port 27 increases, the diaphragm 11 rises. As a result, the ring magnet 16 rises while attracting the main valve 8 by magnetic transmission, and finally rises to a position where the valve seat 10 is closed. As a result, the inflow of high-pressure gas is eliminated, and the rise of the diaphragm 11 is stopped, and the secondary pressure is stabilized. This pressure is the set pressure.

二次側ポート27のガスが消費されることにより圧力が低下すると、ダイヤフラム11に対する付勢力と二次側圧力とのバランスがくずれ、ダイヤフラム11は下降し主弁8を開きダイヤフラム室12へ高圧ガスを流入させ設定圧へ復帰する。 When the pressure drops due to the consumption of the gas at the secondary port 27, the balance between the urging force against the diaphragm 11 and the secondary pressure is lost, the diaphragm 11 descends, the main valve 8 is opened, and the high pressure gas is supplied to the diaphragm chamber 12. To return to the set pressure.

任意の設定圧において、リリーフ弁18を作動させる押ネジ33を下方向へ回転移動させていくと、安定した設定圧を明示する圧力計指針が大きく変動する位置がある。このときの位置を原点とし押ネジ33を上方向に距離Ｌ上昇させナット34でロックする。この距離Ｌは（1）式に於いて記述された“位置の差Ｌ”である。一般に設定圧とリリーフ圧は接近しているのが望ましく、位置の差Ｌを極力小さくしたいが設定圧位置とリリーフ位置が重合すると減圧弁は不安定になる。これを考慮し位置の差Ｌは、リリーフ弁18の有効弁ストロークΔLの1.2〜1.5倍以内として、押ネジ33調整の容易な値とする。 When the push screw 33 that operates the relief valve 18 is rotated downward at an arbitrary set pressure, there is a position where the pressure gauge indicating the stable set pressure changes greatly. With the position at this time as the origin, the push screw 33 is moved upward by a distance L and locked with a nut 34. This distance L is the “positional difference L” described in the equation (1). Generally, it is desirable that the set pressure and the relief pressure are close to each other, and it is desired to make the position difference L as small as possible. However, if the set pressure position and the relief position overlap, the pressure reducing valve becomes unstable. Taking this into consideration, the position difference L is set within 1.2 to 1.5 times the effective valve stroke ΔL of the relief valve 18 so that the push screw 33 can be easily adjusted.

またリリーフ圧は（1）式で求めることが可能なΔＰを設定圧に加えた値である。任意の圧力に設定された減圧弁の二次側圧力が何らかの原因で設定圧を超えΔＰ上昇するとダイヤフラム11の位置も上昇し、押ネジ33の下端がリリーフ弁18の弁軸端を押圧しリリーフ弁18が作動、二次側圧力を大気圧室13及び通気穴26を通じて大気に開放しそれ以上の圧力上昇を防止する。 The relief pressure is a value obtained by adding ΔP, which can be obtained by the equation (1), to the set pressure. When the secondary pressure of the pressure reducing valve set to an arbitrary pressure exceeds the set pressure for some reason and ΔP rises, the position of the diaphragm 11 also rises, and the lower end of the push screw 33 presses the valve shaft end of the relief valve 18 to relieve it. The valve 18 is activated, and the secondary pressure is released to the atmosphere through the atmospheric pressure chamber 13 and the vent hole 26 to prevent further pressure increase.

従来の減圧弁のリリーフ機構は二次側圧力が設定圧を超えると作動し、二次側圧力が設定圧に復帰するまで作動する。これに対し本発明のリリーフ機構は、設定圧とは別の設定圧を一定の値超えたリリーフ圧が存在し、二次側圧力がそのリリーフ圧以上に上昇するのを防止するものである。 The relief mechanism of the conventional pressure reducing valve operates when the secondary pressure exceeds the set pressure, and operates until the secondary pressure returns to the set pressure. On the other hand, the relief mechanism of the present invention prevents a secondary pressure from rising beyond the relief pressure when there is a relief pressure that exceeds a preset pressure different from the preset pressure.

本発明の一実施の形態で設定圧が「0」の状態の断面図である。FIG. 3 is a cross-sectional view of a state where a set pressure is “0” in an embodiment of the present invention. リリーフ弁周辺部の詳細断面図である。It is detail sectional drawing of a relief valve periphery part. 従来の減圧弁の概略断面図である。It is a schematic sectional drawing of the conventional pressure reducing valve.

3シール
5弁穴
6パッキン
7円形磁石
8主弁
10弁座
16リング磁石
18リリーフ弁
19リリーフ弁座
20弁穴
21通気穴
22圧縮バネ
50基体
53カバー
65バネ受け
69キャップ
3 seals
5 Valve hole
6 packing
7 circular magnet
8 Main valve
10 valve seat
16 ring magnet
18 relief valve
19 Relief valve seat
20 valve holes
21 vent holes
22 compression spring
50 substrates
53 cover
65 spring holder
69 cap

Claims (1)

一次側ポートと二次側ポートに通じるダイヤフラム室とを連通させる円筒状弁穴が形成された非磁性の基体と、
前記弁穴の端部に形成された非磁性の弁座に接触する円筒軸方向に移動自在な円形磁石を内蔵の非磁性の主弁と、
リング磁石ホルダを介してリング磁石と一体化したダイヤフラムとを有し、
前記ダイヤフラムのリング磁石ホルダの円筒開部に前記円筒状弁穴が一部に入り込む構造とすることにより、
調圧バネの付勢力に対抗して二次側圧力により発生する前記ダイヤフラムの作動力でリン
グ磁石を従動させリング磁石と前記円形磁石内蔵の主弁との間に磁気吸引力が働き、
前記円筒状弁穴内にて前記主弁の開閉を行わせる調圧機構とを特徴とする微圧用減圧弁。
A non-magnetic base body formed with a cylindrical valve hole for communicating a primary side port and a diaphragm chamber communicating with the secondary side port;
A non-magnetic main valve containing a circular magnet movable in the direction of the cylindrical axis that contacts a non-magnetic valve seat formed at the end of the valve hole;
Having a diaphragm integrated with the ring magnet via the ring magnet holder ,
By adopting a structure in which the cylindrical valve hole partially enters the cylindrical opening of the ring magnet holder of the diaphragm ,
The operating force of the diaphragm generated by the secondary side pressure against the biasing force of the pressure adjusting spring
Magnetic attraction force is generated between the ring magnet is driven with the circular magnet built of the main valve a grayed magnet,
Fine pressure reducing valve you wherein the pressure regulating mechanism to perform the opening and closing of the main valve in the cylindrical valve bore.
JP2006225972A 2006-08-23 2006-08-23 Pressure reducing valve for fine pressure Expired - Fee Related JP4614103B2 (en)

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CN107940049A (en) * 2017-11-24 2018-04-20 海南广天恒科技发展有限公司 Multifunctional pipe gas stabilized-pressure valve
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WO2019163879A1 (en) * 2018-02-22 2019-08-29 三菱電機株式会社 Pressure reducing valve
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