JP4169611B2

JP4169611B2 - Pressure regulator

Info

Publication number: JP4169611B2
Application number: JP2003055453A
Authority: JP
Inventors: 保昭中村
Original assignee: Tokai Corp
Current assignee: Tokai Corp
Priority date: 2003-03-03
Filing date: 2003-03-03
Publication date: 2008-10-22
Anticipated expiration: 2023-03-03
Also published as: JP2004265183A

Description

【０００１】
【発明の属する技術分野】
本発明は、液化ガス利用機器、ガス供給設備などにおいて、高圧１次圧力より一定の２次圧力を得るために高圧ガス減圧用として圧力を調整する圧力調整器に関するものである。
【０００２】
【従来の技術】
通常、例えばガスボンベに収容された液化ガス、一般高圧ガスの１次圧力は、そのままでは利用するのに圧力が高すぎる。また、これら１次圧力は周囲温度、ガス残量等の要因により大きく変動する。そのため、液化ガス利用機器、ガス供給設備等では、高圧ガス減圧用として圧力調整器（調圧ガバナ）が広く利用されてきた。これら圧力調整器は２次圧力をダイヤフラムで検知し、ダイヤフラムの偏位に連動して動く調整弁を持ち、１次圧力が変動しても２次圧力が一定となるよう調整弁を作動させ、所定の２次圧力を得るようにした構造となっている（例えば、特許文献１参照）。
【０００３】
これら圧力調整器は、作動する１次圧力の範囲、応答性、安定性から種々の構造が実用化されており、要求される２次圧力の品質から１種類もしくは数種類の圧力調整器を組み合わせて所定の２次圧力を得ている。
【０００４】
以下に一般的な圧力調整器の基本構造を図６に基づき説明する。図６(ａ)は、単弁式圧力調整器を示す概略図である。この圧力調整器１００は、ケース１０１内を調圧室１０２と大気室１０３とに画成するダイヤフラム１０４と、１次圧力の高圧ガスが導入されるガス導入口１０５と、ダイヤフラム１０４に連係されてガス導入口１０５から調圧室１０２に連通する開口１０６ｃを１次圧力側より開閉して１次圧力を２次圧力へ減圧調整する調整弁１０６と、調圧室１０２を経た２次圧力のガスを排出するガス排出口１０８と、ダイヤフラム１０４を調整弁１０６の開方向へ付勢して２次圧力を設定する重錘１０９とにより構成されてなる。
【０００５】
この圧力調整器１００の原理は大気圧と２次圧力との差圧の検出によるもので、ダイヤフラム１０４の面積および大気圧と２次圧力との差圧から生まれる力が調整弁１０６の閉方向に作用し、重錘１０９の重量が調整弁１０６の開方向に作用し、両者が釣り合った状態で２次圧力を設定圧力に維持する。排出側すなわち調圧室１０２の２次圧力がこの設定圧力より高ければダイヤフラム１０４は大気室１０３側へ偏位し、調整弁１０６は開口１０６ｃを閉じる方向に作動し、逆に２次圧力が設定圧力より低ければダイヤフラム１０４は調圧室１０２側へ偏位し、調整弁１０６は開口１０６ｃを開く方向に作動する。つまり、前記差圧の検出による動きをガス導入側の調整弁１０６に伝え、その開閉作動による圧力調整で２次圧力を一定に保つものである。
【０００６】
しかし、上記単弁式圧力調整器１００の場合、調整弁１０６に流れるガス流により圧力損失が生じ、この圧力損失値と調整弁１０６の面積からダイヤフラム１０４を大気室１０３側へ偏位させる力、すなわち調整弁１０６を閉じる方向の力が余計に生じ、この力は調整弁１０６が１次圧力側から開口１０６ｃを開閉するために、１次圧力が上昇すると大きくなる特性となり、１次圧力の上昇に伴い２次圧力が徐々に低下しやがてガス流が止まってしまうことになる。
【０００７】
図６(ｂ)は、複弁式圧力調整器を示す概略図である。この圧力調整器２００は、ケース２０１内を調圧室２０２と大気室２０３とに画成するダイヤフラム２０４と、１次圧力の高圧ガスが導入されるガス導入口２０５と、ダイヤフラム２０４に連係されてガス導入口２０５から調圧室２０２に連通する２つの開口２０６ｃ，２０７ｃをそれぞれ開閉して１次圧力を２次圧力へ減圧調整する２つの調整弁２０６，２０７と、調圧室２０２を経た２次圧力のガスを排出するガス排出口２０８と、ダイヤフラム２０４を調整弁２０６の開方向へ付勢して２次圧力を設定する重錘２０９とにより構成されてなる。
【０００８】
そして、上記２つの調整弁２０６，２０７は、一方の調整弁２０６が調圧室２０２への開口２０６ｃを１次圧力側から開閉し、他方の調整弁２０７が開口２０７ｃを２次圧力側から開閉するように設置されている。これにより、複弁式圧力調整器２００では、調整弁２０６，２０７に発生する圧力損失による力は、２つの調整弁２０６，２０７で互いに逆方向となるように作用して打ち消しあい、１次圧力の上昇に伴う２次圧力の低下を補正し一定に保つことが可能となる。
【０００９】
しかし複弁式圧力調整器２００では、性能は良いものの、２つの調整弁２０６，２０７の配置が難しく、たとえ両方の調整弁２０６，２０７を同時に弁座に接するよう配置できたとしても、それぞれの調整弁２０６，２０７を通過するガス流の圧力損失が同じとは限らず、１次圧力による２つの調整弁２０６，２０７に作用する力を完全に打ち消しあうように構成するのは非常に困難である。
【００１０】
図６(ｃ)は、変形複弁式圧力調整器を示す概略図である。この圧力調整器３００は、ケース３０１内を調圧室３０２と大気室３０３とに画成するダイヤフラム３０４と、１次圧力の高圧ガスが導入されるガス導入口３０５と、ダイヤフラム３０４に連係されてガス導入口３０５から調圧室３０２に連通する開口３０６ｃを開閉して１次圧力を２次圧力へ減圧調整する調整弁３０６と、この調整弁３０６と一体に移動し摺動するＯ−リングで構成された調整部材３０７と、調圧室３０２を経た２次圧力のガスを排出するガス排出口３０８と、ダイヤフラム３０４を調整弁３０６を開方向へ付勢して２次圧力を設定する重錘３０９とにより構成されてなる。
【００１１】
そして、上記調整弁３０６は調圧室３０２への開口３０６ｃを１次圧力側から開閉し、Ｏ−リングによる調整部材３０７の片面には、ガス導入口３０５からの１次圧力が作用し、他面にはプランジャー内ガス通路３１０を通って調圧室３０２からの２次圧力が作用し、両者の差圧による力が調整部材３０７に加わり、これが調整弁３０６で生じる圧力損失値と調整弁面積からくる力を打ち消して、１次圧力が上昇しても２次圧力を一定に保つことが可能となる。この変形複弁式圧力調整器３００では、調整部材３０７（複弁式圧力調整器２００の他方の調整弁２０７に相当）をＯ−リングで摺動可能に構成することにより、２つの調整弁２０６，２０７の配置問題を解決している。
【００１２】
【特許文献１】
特開平８−３０３７７３号公報
【００１３】
【発明が解決しようとする課題】
上記のように、単弁式圧力調整器は構造が簡単ではあるが広い１次圧力範囲で精度良く２次圧力を得るのは困難であり、広い１次圧力範囲で作動させるためには圧力調整器を複数用意し、高圧から中圧、中圧から低圧、と言ったように徐々に圧力を低下させる必要があり、単弁式の簡易構造の利点が損なわれる。また、複弁式圧力調整器では２つの調整弁の配置が難しく、原理的には優れているが実現させるのは難しい。
【００１４】
さらに、変形複弁式圧力調整器は、実用性はあるが、調整弁から生じる圧力損失値はガス流量で変化するため、調整弁にかかる力をＯ−リングによる調整部材にかかる力で打ち消すのは事実上不可能で、やはり１次圧力の変化に伴い２次圧力に誤差が発生する。また、１次圧力変化に対し調整部材（Ｏ−リング）が摺動するため、この部分の摩擦抵抗が大きく、１次圧力変化に対する２次圧力制御の応答性が低下し、急激な１次圧力変化に対する調整が遅れて２次圧力の変動が大きくなる問題がある。また、これに対処するために、多くの場合、Ｏ−リング摺動部に潤滑剤を付与するが、溶解性の強いガスが導入されると、この潤滑剤が侵されて短時間の使用で応答性が低下するため、不活性ガスのみにしか対応できない。
【００１５】
また実際には、前述の調整弁は非常に狭い弁隙間で減圧を行うため、その弁体、若しくは弁座の少なくとも一方はゴム材等の弾性体で形成するのが一般的であるが、不活性ガスを除き多くのガスが多かれ少なかれこの弾性体を膨潤させ体積変化を生じさせる問題がある。この体積変化は主に調整弁の開閉作動方向に生じるため、使用時間の経過に伴って弁体と弁座との弁隙間が減少し、２次圧力が低下する原因となる。特にジメチルエーテルガスのような溶解性の高いガスに使用した場合、数１０分でガス流が停止する場合がある。
【００１６】
本発明はこのような点に鑑みなされたもので、高圧ガスの１次圧力の変動にかかわらず一定の２次圧力を得るよう圧力を調整するについて、特に低圧から高圧の広い１次圧力範囲を精度良く一定の２次圧力に調整する機構を小型で簡便な構造で構成した圧力調整器を提供することを目的とするものである。
【００１７】
また、溶解性の高いガスに対しても長時間使用可能な圧力調整器を提供することを目的とするものである。
【００１８】
【課題を解決するための手段】
本発明の圧力調整器は、１次圧力を有する高圧ガスを導入するガス導入口と、高圧ガスの１次圧力を２次圧力に圧力損失を有して減圧する調整弁と、前記調整弁を通過したガスの圧力振動を緩和する調圧室と、前記調圧室と大気室とを画成し、調圧室の２次圧力を受けて偏位するダイヤフラムと、前記ダイヤフラムと前記調整弁を連動させるプランジャーと、前記ダイヤフラムの偏位量を調整する圧力設定部と、２次圧力を有するガスを排出するガス排出口とを備えた圧力調整器において、
前記プランジャーにより前記調整弁と連動して作動し、圧力損失を有して高圧ガスの１次圧力を２次圧力に減圧し、その圧力損失に伴って受ける力が、前記調整弁における圧力損失に伴って前記プランジャーに作用する力を打ち消すように設置された副調整弁と、前記副調整弁の圧力損失値が調整可能な調整機構とをさらに備え、前記調整機構は、前記調整弁が受ける圧力損失値と前記副調整弁が受ける圧力損失値が同じとなるように調整されてなることを特徴とするものである。
【００１９】
また、前記調整弁の弁体および副調整弁の弁体を前記プランジャーに設置し、両弁体のうち一方の弁体を１次圧力側に配置し、他方の弁体を２次圧力側に配置するのが好適である。
【００２０】
前記調整機構は、前記プランジャーの移動に対する前記副調整弁の弁座位置を可変として、圧力損失値を調整可能に構成するのが好適である。この調整機構は、前記調整弁の弁体と前記副調整弁の弁体との間のプランジャーに摺動可能に嵌挿された開口と、前記副調整弁の弁座を有する複弁アジャスタで構成するのが好ましい。その際、前記複弁アジャスタに前記ガス排出口を形成するのが好ましい。また、前記調圧室の２次圧力のガスが、前記プランジャーの中心部の２次ガス通路を通って前記ガス排出口に連通するように構成するのが好ましい。
【００２１】
また、前記プランジャーを、前記調整弁の閉弁方向に付勢する閉弁スプリングをさらに備えるように構成してもよい。
【００２２】
前記調整弁および副調整弁は弁体または弁座の一方が弾性体を含み、前記調整弁および前記副調整弁の弾性体が、弁開閉移動方向に対し変形しないよう規制して配置するのが好適である。前記弾性体をＯ−リングで構成するのが好適である。
【００２３】
本発明の圧力調整器は、前記高圧ガスがジメチルエーテルガスである場合にも適用できる。
【００２４】
【発明の効果】
上記のような本発明によれば、１次圧力を２次圧力に圧力損失を有して減圧する調整弁とダイヤフラムとを連動させるプランジャーにより調整弁と連動して圧力損失を有して１次圧力を２次圧力に減圧作動する副調整弁を備え、この副調整弁はその圧力損失に伴って受ける力が、調整弁における圧力損失に伴ってプランジャーに作用する力を打ち消すように設置し、この副調整弁の圧力損失値を調整機構で調整し、調整弁が受ける圧力損失値と副調整弁が受ける圧力損失値が同じとなるようにしたことにより、１つの圧力調整器によって広い１次圧力範囲で精度良く２次圧力を得ることができ、２つの調整弁の配置が簡易で構成の簡素化が得られる。また、調整弁から生じる圧力損失値がガス流量で変化しても、調整弁にかかる力を副調整弁によって精度良く打ち消すことができ、１次圧力の変化に対し２次圧力を一定に調圧できる。さらに、圧力変化に対してプランジャーが移動しても、その摺動抵抗は少なく、１次圧力変化に対する２次圧力制御の応答性が高く、２次圧力の調整精度が高まる。
【００２５】
また、プランジャーを調整弁の閉弁方向に付勢する閉弁スプリングをさらに備えた圧力調整器では、２次圧力の設定圧が低いときにも、ダイヤフラムの偏位に応じた調整弁の正確な作動が得られ、安定した２次圧力調整が行えるとともに、調整弁および副調整弁が閉じた遮断状態を得ることができる。
【００２６】
一方、調整弁および副調整弁の弁体または弁座の一方が弾性体を含み、この弾性体を弁開閉移動方向に対し変形しないよう規制して配置すると、弾性体が膨潤して体積変化が生じても、使用時間の経過に伴って弁体と弁座との隙間変化が少なく、ジメチルエーテルガスのような溶解性の高いガスを調圧しても、流量変化を招かず性能を確保することができる。
【００２７】
【発明の実施の形態】
以下、本発明の実施の形態を詳細に説明する。図１は一つの実施の形態における圧力調整器の断面図である。
【００２８】
本実施形態の圧力調整器１０は、ケース１内を調圧室１１と大気室１２とに画成するダイヤフラム２と、１次圧力の高圧ガスが導入されるガス導入口１３と、ダイヤフラム２に連動してガス導入口１３から調圧室１１に連通する開口３３を１次圧力側より開閉して１次圧力を２次圧力へ減圧調整する調整弁３と、ダイヤフラム２に連動してガス導入口１３からガス排出口１４に連通する開口４３を２次圧力側より開閉する副調整弁４と、調圧室１１を経て圧力調整された２次圧力のガスを排出するガス排出口１４と、調圧室１１の２次圧力を受けて偏位するダイヤフラム２の偏位量を調整する圧力設定部５とを備える。さらに、ダイヤフラム２と調整弁３および副調整弁４はプランジャー６で繋がれて連動され、この副調整弁４の弁座位置の調整により圧力損失値を調整する調整機構としての複弁アジャスタ７を備える。
【００２９】
そして、上記調整弁３および副調整弁４は、圧力損失を有して高圧ガスの１次圧力を２次圧力に減圧するもので、その圧力損失により調整弁３に作用する力と、副調整弁４に作用する力とが、互いに打ち消す方向となるように配置してなり、前記複弁アジャスタ７（調整機構）により、副調整弁４での圧力損失値を調整弁３での圧力損失値と同じになるように調整可能としている。
【００３０】
さらに、前記調整弁３および副調整弁４は、弁体３１，４１をＯ−リングによる弾性体で構成し、この弾性体を弁開閉移動方向に対し変形しないよう、周溝部６３によって規制して配置してなり、高圧ガスが弾性体に対し膨潤等の影響を及ぼすジメチルエーテルガス等の使用を可能としている。
【００３１】
構造を具体的に説明する。前記ケース１はケース本体部１５とカバー部１６とからなり、このケース本体部１５とカバー部１６とを前記ダイヤフラム２を介して接合することにより、ケース内空間がダイヤフラム２によってケース本体部１５側の調圧室１１とカバー部１６側の大気室１２とに画成される。調圧室１１は、ある程度の容積を有し、調整弁３を通過したガスの圧力振動を緩和する。
【００３２】
ダイヤフラム２は、調圧室１１の２次圧力を受けて大気室１２との圧力差に応じて弾性偏位可能であり、その中心部には、ケース本体部１５側にプランジャー６が、カバー部１６側にサポータ８がそれぞれ固着され、ダイヤフラム２の偏位に応じて一体に軸方向に移動可能である。
【００３３】
プランジャー６は、ダイヤフラム２に固着され調圧室１１に位置する筒部６１と、この筒部６１の先端から軸方向に延長された軸部６２とを備え、この軸部６２に所定の間隔を持って２つの周溝部６３，６３を有し、この周溝部６３，６３に調整弁３および副調整弁４のＯ−リング（弾性体）による弁体３１，４１が装着される。プランジャー６の筒部６１および軸部６２の中心には、一端より他端に貫通する２次ガス通路６４を備え、筒部６１の側壁には、調圧室１１と２次ガス通路６４とを連通する連通口６５が開口されている。
【００３４】
サポータ８はダイヤフラム２に密着するフランジ部８１の中心にボルト部８２を備え、このボルト部８２がダイヤフラム２の中心を貫通して反対側のプランジャー６の２次ガス通路６４の一端ネジ部に螺合されて締結される。
【００３５】
また、サポータ８のフランジ部８１には、カバー部１６の筒状部１６ａの内部に設置された圧力設定部５の調圧スプリング５１の一端部が当接し、調圧スプリング５１の他端部は筒状部１６ａに位置調整可能に螺合された調圧ネジ５２（アジャスタ）に当接し、この調圧ネジ５２の軸方向位置の調整に応じて、調圧スプリング５１によるダイヤフラム２の付勢力が調整される。上記調圧ネジ５２は中心に軸方向に貫通開口した連通孔５３を有し、この連通孔５３により前記大気室１２を大気開放している。
【００３６】
ケース本体部１５の一側部には高圧ガスのガス導入口１３を備え、このガス導入口１３には、ガスボンベ等より供給される１次圧力を有するジメチルエーテルガスなどの高圧ガスを導入する第１コネクタ１８が接続される。ガス導入口１３はケース本体部１５の壁を中心方向へ貫通して内部の１次ガス通路２２に連通する導入ガス穴２１を有する。また、ケース本体部１５は１次ガス通路２２と調圧室１１とを区画する仕切壁１５ａを備え、この仕切壁１５ａの中心部に調整弁３によって開閉される開口３３が形成され、この開口３３には前記プランジャー６の軸部６２が摺動可能に挿通され、仕切壁１５ａの１次ガス通路２２側の開口周縁が調整弁３の弁座３２に構成される。
【００３７】
そして、調整弁３は、プランジャー６の移動に伴い弁体３１が上記弁座３２に密着して開口３３を閉じ、弁体３１が弁座３２より離れて開口３３を開いた際には、その開口量に応じたガス量が、開口３３とプランジャー６の隙間を通って１次ガス通路２２から調圧室１１へ流入する。
【００３８】
上記１次ガス通路２２には、ケース本体部１５の他端より筒状の複弁アジャスタ７が装着されてなる。この複弁アジャスタ７は、端部側内孔が調圧した２次圧力のガスを排出するガス排出口１４に形成され、このガス排出口１４には調圧されたガスを導出する第２コネクタ１９が接続される。複弁アジャスタ７は外周のネジがケース本体部１５の端部ネジに螺合されて位置調整され、止めナット１７により固定される。
【００３９】
また、上記複弁アジャスタ７は、先端筒部７１が１次ガス通路２２に摺動可能に挿入され、この先端筒部７１の外周に装着されたシール材７２が導入ガス穴２１より外側の１次ガス通路２２の周面に密着して外周側の摺動シールを行う。また、この先端筒部７１の中心開口４３には、プランジャー６の調整弁３の弁体３１と副調整弁４の弁体４１との間の軸部６２が摺動可能に挿通されている。そして、先端筒部７１のガス排出口１４側の開口周縁が副調整弁４の弁座４２に構成される。
【００４０】
この副調整弁４は、プランジャー６の移動に伴い弁体４１が上記弁座４２に密着して先端筒部７１の開口４３を閉じ、弁体４１が弁座４２より離れて開口４３を開いた際には、その開口量に応じたガス量が、開口４３とプランジャー６の隙間を通って１次ガス通路２２から２次圧力側のガス排出口１４へ流出する。
【００４１】
調整機構としての前記複弁アジャスタ７のケース本体部１５への挿入位置は、調整弁３の弁体３１がその弁座３２に着座して開口３３を閉塞したときに、副調整弁４の弁体４１がその弁座４２に着座して開口４３を閉塞するように、両者の圧力損失値が同じになるように調整される。
【００４２】
上記調整弁３および副調整弁４により、ダイヤフラム２の動きに応じて、１次圧力をその圧力に関係なく所定の２次圧力に減圧調整するものであり、その作用を説明する。
【００４３】
まず、ガス導入口１３から流入した１次ガス通路２２のガスは、調整弁３を通過して２次圧力に減圧され、プランジャー６内の２次ガス通路６４を経てガス排出口１４へ至る。この際生じる圧力損失と調整弁３の弁体投影面積との積の力が、調整弁３に対し閉方向でプランジャー６を後退させる方向（図で左方向）に生じる。
【００４４】
また、前記１次ガス通路２２のガスは、開口４３すなわち複弁アジャスタ７とプランジャー６の隙間から、副調整弁４を通過し２次圧力に減圧され、ガス排出口１４へ至り、これはプランジャー６内の２次ガス通路６４を通して調圧室１１に連通している。この際、副調整弁４に生じる圧力損失と副調整弁４の弁体投影面積との積の力が、副調整弁４に対し開方向でプランジャー６を前進させる方向（図で右方向）に生じ、調整弁３における力と逆方向に作用する。
【００４５】
通常上記調整弁３と副調整弁４の２つの流路で生じる圧力損失は異なるが、複弁アジャスタ７を軸方向に移動調整可能に配置したことにより、副調整弁４で生じる圧力損失を変化させることが可能となり、調整弁３の圧力損失値を、副調整弁４に働く圧力損失値で精度良く打ち消すことが可能となる。
【００４６】
また、ダイヤフラム２はプランジャー６とサポータ８で支持されており、２次圧力と大気圧との差圧による力と、調圧スプリング５１による付勢力とが平衡した位置に保たれる。そして、ガス排出口１４からのガス排出量の変動、１次圧力の変動等に応じて２次圧力が変化した場合、これに応動してダイヤフラム２の偏位量が変化し、プランジャー６の位置が変化するのに連動して調整弁３および副調整弁４が動き、２次圧力を一定に保つ。圧力設定部５の調圧ネジ５２を動かすことにより調圧スプリング５１の付勢力を変化させ、任意の２次圧力が設定可能である。
【００４７】
また、調整弁３および副調整弁４の弁体３１，４１をＯ−リングによる弾性体で構成し、ジメチルエーテルガスのような溶解性の強いガスを流通した際に、それに接してＯ−リングが膨潤、体積膨張したとしても、その体積変化は弁開閉移動方向に垂直な方向に抑制されているため、Ｏ−リングの体積膨張による圧力損失およびガス流量の変化は抑えられる。
【００４８】
さらに、１次圧力から２次圧力への減圧を調整弁３と副調整弁４の２つで行うことにより、１つの調整弁で減圧する場合と比較して各調整弁で生じる圧力損失値を半分にでき、調整弁の弁体と弁座との隙間を広く取れるため、１次圧力が非常に高い、つまり減圧分が大きく弁体と弁座との弁隙間が極端に狭く、少しの変動が２次圧力に影響する場合でも安定した性能が得られる。
【００４９】
なお、前記実施形態では、調整弁３および副調整弁４の弁体３１，４１をＯ−リングによる弾性体で構成しているが、弁座３２，４２をＯ−リングによる弾性体で構成してもよく、その場合においても、弾性体が弁開閉移動方向に対し変形しないよう周溝構造などにより規制して配置する。また、Ｏ−リング以外の弾性材で構成してもよい。
【００５０】
図２は本発明の他の実施形態の圧力調整器２０を示す断面図である。この実施形態の圧力調整器２０は、圧力室１１に閉弁スプリング９をさらに備えた他は、前述の実施形態と同様であり、図１と同一部品には同一符号を付してその説明を省略する。
【００５１】
上記閉弁スプリング９は、プランジャー６を後退させる方向（図で左方向）すなわち調整弁３の閉弁方向に付勢するものである。具体的には、閉弁スプリング９はコイルスプリングからなり、圧力室１１内のプランジャー６の筒部６１外周に、一端がケース本体部１５の仕切壁１５ａに当接し、他端がダイヤフラム６を大気室１２側へ押圧するように縮装配置されてなる。
【００５２】
そして、前記圧力設定部５の調圧ネジ５２による２次圧力の調整は、調圧スプリング５１の付勢力が前述の実施形態におけるものより、上記閉弁スプリング９の付勢力分だけ大きくなるように調整される。
【００５３】
本実施形態では上記閉弁スプリング９を備えたことにより、調圧スプリング５１の付勢力を弱めて２次圧力の設定圧が低いときにも、ダイヤフラム６は調圧室１１と大気室１２との圧力差に応じて偏位し、このダイヤフラム６の偏位に応じたプランジャー６の移動により調整弁３および副調整弁４の正確な作動が得られ、安定した２次圧力調整が行える。また、調圧スプリング５１の付勢力が閉弁スプリング９の付勢力より小さくなるように調整された場合には、この閉弁スプリング９の付勢力でプランジャー６が後退移動し、調整弁３および副調整弁４が閉じた遮断状態を得ることができ、ガス排出口１４からのガス排出が停止される。
【００５４】
なお、上記閉弁スプリング９を備えていない前記図１の場合は、２次圧力が通常ある程度高い圧力に設定されることを前提としているもので、２次圧力の設定が大気圧より十分に高い場合には、ダイヤフラム６には２次圧力と大気圧との差圧に応じた大きな力が作用し、このダイヤフラム６の偏位に応じてプランジャー６を介して調整弁３および副調整弁４による正確な２次圧力調整作動が得られる。しかし、２次圧力が大気圧に接近して低く設定された場合には、大気圧との差圧に応じたダイヤフラム６を偏位させる力が小さくなるとともに、この差圧以外にプランジャー６が後退する方向にダイヤフラム６を偏位させる力がなくて応動性が低下し、２次圧力を調整する作用が不安定となるのを、本実施形態では、閉弁スプリング９の設置によりプランジャー６が後退する方向にダイヤフラム６を偏位させる力を得て、２次圧力の設定が低いときにもダイヤフラム６の応動性を向上して、安定した２次圧力の調整作用を確保したものである。
【００５５】
次に、本発明の圧力調整器（図１に示す実施形態のもの）による調圧作用を評価した実験結果を、比較例の圧力調整器（図５に示す単弁式の圧力調整器）によるものと比較して、図３および図４に示す。
【００５６】
図５に示す単弁式の圧力調整器１００は、原理的には図６(ａ)に示すものであり、同じ符号で示せば、ガス導入口１０５から導入された１次圧力の高圧ガスは、ダイヤフラム１０４の偏位に応じて開閉する調整弁１０６（弁体１０６ａが剛体、弁座１０６ｂが弾性体で構成されている）を経て、ダイヤフラム１０４で大気室１０３と画成されてなる調圧室１０２に流入し、調圧室１０２を経た２次圧力のガスがガス排出口１０８より排出される。なお、ダイヤフラム１０４に対する付勢力が、調圧スプリング１０９ａと調圧ネジ１０９ｂを備えた圧力設定部１０９により調整され、２次圧力が設定される。
【００５７】
＜測定例１＞
この測定例は、圧力調整器に供給する高圧ガス（不活性ガス）の１次圧力を変化させた場合の２次圧力の変化を測定したもので、図３に実線で本発明による測定結果を、破線で比較例による測定結果を示す。
【００５８】
２次圧力の設定は、本発明および比較例ともに、１次圧力が４００ｋＰａのときに、２次圧力が５０ｋＰａとなるように、圧力設定部の調圧ネジの調整により設定した。その際、ガス流量は、４０ｍＬ／ｍｉｎである。
【００５９】
図３のグラフより、実線で示す本発明の圧力調整器では、１次圧力を５０〜２０００ｋＰａの範囲で変化させても、２次圧力は設定値（５０ｋＰａ）を維持して変化せず、一定の圧力を維持した。調整弁と副調整弁の機能によって、圧力損失に伴って作用する力の影響を解消し、広い圧力範囲で調圧作用が得られることが確認できた。
【００６０】
これに対し、破線の比較例による単弁式の圧力調整器では、１次圧力が４００ｋＰａより低い領域では、２次圧力は設定値（５０ｋＰａ）より高く、１次圧力が４００ｋＰａより高い領域では、２次圧力は設定値（５０ｋＰａ）より低くなるように、全体として１次圧力の上昇に対し２次圧力が低下するように変化し、一定の２次圧力を維持することができなかった。
【００６１】
＜測定例２＞
この測定例は、圧力調整器に導入する高圧ガスに、弾性材（ゴム材）を膨潤させるガスの代表としてジメチルエーテルガスを使用し、時間の経過に対するガス流量の変化を測定したもので、図４に実線で本発明による測定結果を、破線で比較例による測定結果を示す。ジメチルエーテルガスの初期流量は８０ｍＬ／ｍｉｎであり、蒸気圧が４００ｋＰａとなる温度で試験した。
【００６２】
図４のグラフより、実線で示す本発明の圧力調整器では、時間が１２０分経過しても、排出ガス流量は初期流量を維持して変化せず、ガスとの接触によりＯ−リングに膨潤があってもガス流量への影響がないことが確認できた。
【００６３】
これに対し、破線の比較例による単弁式の圧力調整器では、弾性体による弁座の膨潤により弁隙間が変化し、測定を開始して１５分程度経過した時期からガス流量が低下し始め、その後時間の経過と共に急激に流量が低下し、約６０分経過した時点で流量が０となって、ガスが排出されなくなった。
【図面の簡単な説明】
【図１】本発明の一つの実施の形態における圧力調整器の断面図
【図２】本発明の他の実施の形態における圧力調整器の断面図
【図３】圧力調整器に供給する高圧ガスの１次圧力を変化させた場合の２次圧力の変化を測定した結果を比較例と共に示すグラフ
【図４】圧力調整器に供給する高圧ガスにジメチルエーテルガスを使用し時間の経過に対するガス流量の変化を測定した結果を比較例と共に示すグラフ
【図５】図３および図４の測定例に使用した比較例の圧力調整器の断面図
【図６】一般的な圧力調整器の基本構造をそれぞれ示す概略図
【符号の説明】
10，20 圧力調整器
１ケース
２ダイヤフラム
３調整弁
４副調整弁
５圧力設定部
６プランジャー
７複弁アジャスタ（調整機構）
９閉弁スプリング
11 調圧室
12 大気室
13 ガス導入口
14 ガス排出口
22 １次ガス通路
31，41 弁体
32，42 弁座
33，43 開口
51 調圧スプリング
52 調圧ネジ
61 筒部
62 軸部
63 周溝部
64 ２次ガス通路[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pressure regulator that adjusts the pressure for depressurizing high-pressure gas in order to obtain a constant secondary pressure from the high-pressure primary pressure in liquefied gas utilizing equipment, gas supply facilities, and the like.
[0002]
[Prior art]
Usually, for example, the primary pressure of liquefied gas and general high-pressure gas stored in a gas cylinder is too high to be used as it is. Further, these primary pressures vary greatly depending on factors such as the ambient temperature and the remaining amount of gas. Therefore, pressure regulators (pressure regulators) have been widely used for liquefied gas utilization equipment, gas supply facilities, and the like for decompressing high-pressure gas. These pressure regulators detect the secondary pressure with a diaphragm, have a regulating valve that moves in conjunction with the displacement of the diaphragm, and operates the regulating valve so that the secondary pressure remains constant even if the primary pressure fluctuates, The structure is such that a predetermined secondary pressure is obtained (see, for example, Patent Document 1).
[0003]
These pressure regulators have various structures in practical use due to the range of primary pressure to operate, responsiveness, and stability. Depending on the required secondary pressure quality, one or several types of pressure regulators can be combined. A predetermined secondary pressure is obtained.
[0004]
The basic structure of a general pressure regulator will be described below with reference to FIG. FIG. 6A is a schematic diagram showing a single valve pressure regulator. The pressure regulator 100 is linked to a diaphragm 104 that defines a case 101 into a pressure regulating chamber 102 and an atmospheric chamber 103, a gas inlet 105 through which a high-pressure gas of primary pressure is introduced, and a diaphragm 104. An opening valve 106c communicating from the gas inlet 105 to the pressure regulating chamber 102 is opened and closed from the primary pressure side to adjust the primary pressure to a secondary pressure, and a secondary pressure gas passing through the pressure regulating chamber 102 And a weight 109 for urging the diaphragm 104 in the opening direction of the regulating valve 106 to set the secondary pressure.
[0005]
The principle of the pressure regulator 100 is based on the detection of the differential pressure between the atmospheric pressure and the secondary pressure, and the force generated from the area of the diaphragm 104 and the differential pressure between the atmospheric pressure and the secondary pressure in the closing direction of the regulating valve 106. The weight of the weight 109 acts in the opening direction of the regulating valve 106, and the secondary pressure is maintained at the set pressure in a state where both are balanced. If the secondary pressure in the discharge side, that is, the pressure regulating chamber 102 is higher than the set pressure, the diaphragm 104 is displaced to the atmosphere chamber 103 side, and the regulating valve 106 operates in a direction to close the opening 106c, and conversely, the secondary pressure is set. If it is lower than the pressure, the diaphragm 104 is displaced to the pressure regulating chamber 102 side, and the regulating valve 106 operates in a direction to open the opening 106c. That is, the movement due to the detection of the differential pressure is transmitted to the regulating valve 106 on the gas introduction side, and the secondary pressure is kept constant by adjusting the pressure by the opening / closing operation.
[0006]
However, in the case of the single valve pressure regulator 100, pressure loss occurs due to the gas flow flowing through the regulating valve 106, and the force that causes the diaphragm 104 to deviate from the pressure loss value and the area of the regulating valve 106 toward the atmosphere chamber 103, that is, An extra force in the direction of closing the regulating valve 106 is generated, and this force becomes a characteristic that increases as the primary pressure rises because the regulating valve 106 opens and closes the opening 106c from the primary pressure side, which increases the primary pressure. As a result, the secondary pressure gradually decreases and the gas flow stops.
[0007]
FIG. 6B is a schematic view showing a double valve pressure regulator. This pressure regulator 200 is linked to a diaphragm 204 that defines a case 201 into a pressure regulating chamber 202 and an atmospheric chamber 203, a gas inlet 205 through which high-pressure gas of primary pressure is introduced, and a diaphragm 204. Two adjustment valves 206 and 207 for adjusting the primary pressure to the secondary pressure by opening and closing the two openings 206c and 207c communicating from the gas inlet 205 to the pressure regulating chamber 202, respectively, and 2 through the pressure regulating chamber 202 The gas discharge port 208 discharges the gas at the secondary pressure, and the weight 209 that biases the diaphragm 204 in the opening direction of the regulating valve 206 to set the secondary pressure.
[0008]
Of the two regulating valves 206 and 207, one regulating valve 206 opens and closes the opening 206c to the pressure regulating chamber 202 from the primary pressure side, and the other regulating valve 207 opens and closes the opening 207c from the secondary pressure side. It is installed to do. Thereby, in the double valve pressure regulator 200, the force due to the pressure loss generated in the regulating valves 206 and 207 cancels each other by acting in the opposite directions in the two regulating valves 206 and 207. It is possible to correct and keep constant the decrease in the secondary pressure accompanying the increase in.
[0009]
However, in the double-valve pressure regulator 200, although the performance is good, it is difficult to arrange the two regulating valves 206 and 207. Even if both regulating valves 206 and 207 can be arranged to contact the valve seat at the same time, The pressure loss of the gas flow passing through the regulating valves 206 and 207 is not necessarily the same, and it is very difficult to completely cancel the force acting on the two regulating valves 206 and 207 due to the primary pressure. is there.
[0010]
FIG. 6C is a schematic view showing a modified double-valve pressure regulator. This pressure regulator 300 is linked to a diaphragm 304 that defines a case 301 into a pressure regulating chamber 302 and an atmospheric chamber 303, a gas inlet 305 through which a high-pressure gas having a primary pressure is introduced, and a diaphragm 304. An adjustment valve 306 that opens and closes an opening 306 c communicating from the gas inlet 305 to the pressure regulation chamber 302 to adjust the primary pressure to a secondary pressure, and an O-ring that moves and slides integrally with the regulation valve 306. The adjustment member 307 configured, the gas discharge port 308 that discharges the gas of the secondary pressure that has passed through the pressure adjusting chamber 302, and the weight that urges the diaphragm 304 in the opening direction to set the secondary pressure. 309.
[0011]
The adjusting valve 306 opens and closes the opening 306c to the pressure adjusting chamber 302 from the primary pressure side, and the primary pressure from the gas inlet 305 acts on one side of the adjusting member 307 by the O-ring. A secondary pressure from the pressure adjusting chamber 302 acts on the surface through the plunger gas passage 310, and a force due to the pressure difference between the two is applied to the adjusting member 307, which is a pressure loss value generated by the adjusting valve 306 and the adjusting valve. Even if the primary pressure rises by canceling the force coming from the area, the secondary pressure can be kept constant. In this modified double-valve pressure regulator 300, the regulating member 307 (corresponding to the other regulating valve 207 of the double-valve pressure regulator 200) is configured to be slidable by an O-ring, thereby providing two regulating valves 206. , 207 are solved.
[0012]
[Patent Document 1]
JP-A-8-303773
[0013]
[Problems to be solved by the invention]
As described above, the single-valve pressure regulator is simple in structure, but it is difficult to obtain the secondary pressure accurately in a wide primary pressure range, and in order to operate in a wide primary pressure range, the pressure regulator It is necessary to gradually reduce the pressure, such as from high pressure to medium pressure and from medium pressure to low pressure, and the advantage of the simple structure of the single valve type is impaired. Further, in the double valve pressure regulator, it is difficult to arrange the two regulating valves, which is excellent in principle but difficult to realize.
[0014]
Furthermore, the modified double-valve pressure regulator has practicality, but the pressure loss value generated from the regulating valve varies with the gas flow rate, so that the force applied to the regulating valve is canceled by the force applied to the regulating member by the O-ring. Is practically impossible, and an error occurs in the secondary pressure as the primary pressure changes. Further, since the adjusting member (O-ring) slides with respect to the primary pressure change, the frictional resistance of this portion is large, and the responsiveness of the secondary pressure control to the primary pressure change is reduced, and the sudden primary pressure is abrupt. There is a problem that secondary pressure fluctuations increase due to delays in adjustments to changes. In order to cope with this, in many cases, a lubricant is applied to the O-ring sliding portion. However, when a highly soluble gas is introduced, the lubricant is attacked and can be used for a short time. Since responsiveness is reduced, only inert gas can be handled.
[0015]
In practice, since the aforementioned regulating valve performs pressure reduction in a very narrow valve gap, at least one of the valve body or the valve seat is generally formed of an elastic body such as a rubber material. There is a problem that many gases except the active gas swell the elastic body more or less and cause a volume change. Since this volume change mainly occurs in the opening / closing operation direction of the regulating valve, the valve gap between the valve body and the valve seat decreases with the passage of the use time, which causes the secondary pressure to decrease. In particular, when used for a highly soluble gas such as dimethyl ether gas, the gas flow may stop in several tens of minutes.
[0016]
The present invention has been made in view of the above points, and in adjusting the pressure so as to obtain a constant secondary pressure regardless of fluctuations in the primary pressure of the high pressure gas, in particular, a wide primary pressure range from low pressure to high pressure. An object of the present invention is to provide a pressure regulator in which a mechanism for adjusting to a constant secondary pressure with high accuracy has a small and simple structure.
[0017]
It is another object of the present invention to provide a pressure regulator that can be used for a long time even with a highly soluble gas.
[0018]
[Means for Solving the Problems]
The pressure regulator of the present invention includes a gas inlet for introducing a high-pressure gas having a primary pressure, an adjustment valve for reducing the primary pressure of the high-pressure gas to a secondary pressure with a pressure loss, and the adjustment valve. A pressure regulating chamber for relaxing the pressure vibration of the gas that has passed through, a pressure regulating chamber and an air chamber; a diaphragm that is displaced by receiving a secondary pressure in the pressure regulating chamber; and the diaphragm and the regulating valve In a pressure regulator comprising a plunger to be interlocked, a pressure setting unit that adjusts the displacement amount of the diaphragm, and a gas discharge port that discharges a gas having a secondary pressure,
The plunger operates in conjunction with the regulating valve, reduces the primary pressure of the high pressure gas to the secondary pressure with pressure loss, and the force received with the pressure loss is the pressure loss in the regulating valve. Is further provided with a sub-regulator valve installed so as to cancel the force acting on the plunger, and an adjustment mechanism capable of adjusting the pressure loss value of the sub-regulator valve. The pressure loss value received and the pressure loss value received by the sub regulating valve are adjusted to be the same.
[0019]
Further, the valve body of the regulating valve and the valve body of the sub regulating valve are installed on the plunger, one of the valve bodies is disposed on the primary pressure side, and the other valve body is disposed on the secondary pressure side. It is preferable to arrange in the above.
[0020]
It is preferable that the adjusting mechanism is configured such that a pressure loss value can be adjusted by changing a valve seat position of the sub adjusting valve with respect to the movement of the plunger. The adjustment mechanism is a double valve adjuster having an opening slidably fitted in a plunger between the valve body of the adjustment valve and the valve body of the sub adjustment valve, and a valve seat of the sub adjustment valve. It is preferable to configure. In that case, it is preferable to form the gas outlet in the double valve adjuster. Moreover, it is preferable that the secondary pressure gas in the pressure regulating chamber communicate with the gas discharge port through a secondary gas passage at the center of the plunger.
[0021]
Further, the plunger may be configured to further include a valve closing spring that urges the adjusting valve in a valve closing direction.
[0022]
One of the valve body and the valve seat includes an elastic body, and the adjustment valve and the sub-regulation valve are arranged so that the elastic body of the adjustment valve and the sub-regulation valve is not deformed in the valve opening / closing movement direction. Is preferred. It is preferable that the elastic body is composed of an O-ring.
[0023]
The pressure regulator of the present invention can also be applied when the high-pressure gas is dimethyl ether gas.
[0024]
【The invention's effect】
According to the present invention as described above, the primary pressure has a pressure loss in conjunction with the regulating valve by the plunger that interlocks the diaphragm with the regulating valve that reduces the primary pressure to the secondary pressure with a pressure loss. It is equipped with a secondary regulator that depressurizes the secondary pressure to the secondary pressure, and this secondary regulator is installed so that the force received with the pressure loss cancels the force acting on the plunger with the pressure loss at the regulator. Then, the pressure loss value of the sub-regulating valve is adjusted by the adjusting mechanism so that the pressure loss value received by the regulating valve is the same as the pressure loss value received by the sub-regulating valve. The secondary pressure can be obtained with high accuracy in the primary pressure range, the arrangement of the two regulating valves is simple, and the configuration can be simplified. In addition, even if the pressure loss value generated from the regulator valve changes with the gas flow rate, the force applied to the regulator valve can be accurately canceled by the secondary regulator valve, and the secondary pressure is regulated to a constant primary pressure. it can. Further, even if the plunger moves with respect to the pressure change, the sliding resistance is small, the responsiveness of the secondary pressure control to the primary pressure change is high, and the adjustment accuracy of the secondary pressure is increased.
[0025]
In addition, in a pressure regulator further provided with a valve closing spring that urges the plunger in the valve closing direction, even when the set pressure of the secondary pressure is low, the accuracy of the adjusting valve corresponding to the displacement of the diaphragm is reduced. Thus, a stable secondary pressure adjustment can be performed, and a shut-off state in which the regulating valve and the sub regulating valve are closed can be obtained.
[0026]
On the other hand, if one of the valve body or the valve seat of the regulating valve and the sub regulating valve includes an elastic body, and this elastic body is placed so as not to be deformed in the valve opening / closing movement direction, the elastic body swells and the volume changes. Even if it occurs, there is little change in the gap between the valve body and the valve seat as the usage time elapses, and even if a highly soluble gas such as dimethyl ether gas is regulated, the flow rate does not change and the performance is ensured. it can.
[0027]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described in detail. FIG. 1 is a cross-sectional view of a pressure regulator according to one embodiment.
[0028]
The pressure regulator 10 according to the present embodiment includes a diaphragm 2 that defines the inside of the case 1 into a pressure regulating chamber 11 and an atmospheric chamber 12, a gas inlet 13 through which high-pressure gas having a primary pressure is introduced, and a diaphragm 2. In conjunction with the diaphragm 2, the gas introduction is performed in conjunction with the adjustment valve 3 that opens and closes the opening 33 communicating from the gas inlet 13 to the pressure regulating chamber 11 from the primary pressure side to adjust the primary pressure to the secondary pressure. From mouth 13 Gas outlet 14 The secondary adjustment valve 4 that opens and closes the opening 43 communicating with the secondary pressure side, the gas discharge port 14 that discharges the gas of the secondary pressure that has been pressure-adjusted through the pressure regulating chamber 11, and the secondary of the pressure regulating chamber 11 A pressure setting unit 5 that adjusts the amount of displacement of the diaphragm 2 that is displaced by receiving pressure. Further, the diaphragm 2, the adjusting valve 3 and the sub-regulating valve 4 are connected by a plunger 6 and interlocked, and a double valve adjuster 7 as an adjusting mechanism for adjusting the pressure loss value by adjusting the valve seat position of the sub-regulating valve 4. Is provided.
[0029]
The regulating valve 3 and the secondary regulating valve 4 have a pressure loss and reduce the primary pressure of the high-pressure gas to the secondary pressure. The force acting on the regulating valve 3 due to the pressure loss and the secondary regulation valve The force acting on the valve 4 is arranged so as to cancel each other, and the pressure loss value at the sub-regulating valve 4 is changed to the pressure loss value at the regulating valve 3 by the double valve adjuster 7 (adjusting mechanism). Can be adjusted to be the same.
[0030]
Further, the adjusting valve 3 and the sub-regulating valve 4 are configured such that the valve bodies 31 and 41 are composed of elastic bodies using O-rings, and the elastic bodies are regulated by the circumferential groove portion 63 so as not to be deformed in the valve opening / closing movement direction. It is possible to use dimethyl ether gas or the like in which the high-pressure gas has an influence such as swelling on the elastic body.
[0031]
The structure will be specifically described. The case 1 includes a case main body 15 and a cover 16, and the case main body 15 and the cover 16 are joined to each other via the diaphragm 2, so that the inner space of the case is separated from the case main body 15 by the diaphragm 2. The pressure regulating chamber 11 and the atmosphere chamber 12 on the cover 16 side are defined. The pressure regulating chamber 11 has a certain volume and relieves pressure oscillation of the gas that has passed through the regulating valve 3.
[0032]
Diaphragm 2 receives the secondary pressure of pressure regulating chamber 11 and can be elastically displaced in accordance with the pressure difference from atmospheric chamber 12. The supporters 8 are respectively fixed to the side of the portion 16 and can be integrally moved in the axial direction according to the displacement of the diaphragm 2.
[0033]
The plunger 6 includes a cylindrical portion 61 fixed to the diaphragm 2 and positioned in the pressure regulating chamber 11, and a shaft portion 62 extending in the axial direction from the tip of the cylindrical portion 61, and the shaft portion 62 has a predetermined interval. And have two circumferential groove portions 63, 63, and the circumferential groove portions 63, 63 are connected to the regulating valve 3 and Sub-regulator valve 4 The valve bodies 31 and 41 by the O-ring (elastic body) are mounted. A secondary gas passage 64 penetrating from one end to the other end is provided at the center of the cylindrical portion 61 and the shaft portion 62 of the plunger 6, and the pressure regulating chamber 11 and the secondary gas passage 64 are provided on the side wall of the cylindrical portion 61. A communication port 65 for communicating is opened.
[0034]
The supporter 8 includes a bolt portion 82 at the center of the flange portion 81 that is in close contact with the diaphragm 2, and the bolt portion 82 passes through the center of the diaphragm 2 and is connected to one end thread portion of the secondary gas passage 64 of the plunger 6 on the opposite side. It is screwed and fastened.
[0035]
In addition, one end portion of the pressure adjusting spring 51 of the pressure setting portion 5 installed inside the cylindrical portion 16 a of the cover portion 16 abuts on the flange portion 81 of the supporter 8, and the other end portion of the pressure adjusting spring 51 is Abutting on a pressure adjusting screw 52 (adjuster) screwed to the cylindrical portion 16a so that the position of the pressure adjusting screw 52 can be adjusted, and the biasing force of the diaphragm 2 by the pressure adjusting spring 51 is adjusted according to the adjustment of the axial position of the pressure adjusting screw 52. Adjusted. The pressure adjusting screw 52 has a communication hole 53 that opens in the axial direction in the center, and the atmosphere chamber 12 is opened to the atmosphere through the communication hole 53.
[0036]
A gas inlet 13 for high-pressure gas is provided at one side of the case main body 15, and a first high-pressure gas such as dimethyl ether gas having a primary pressure supplied from a gas cylinder or the like is introduced into the gas inlet 13. A connector 18 is connected. The gas introduction port 13 has an introduction gas hole 21 that penetrates the wall of the case body 15 in the center direction and communicates with the internal primary gas passage 22. Further, the case main body 15 includes a partition wall 15a that partitions the primary gas passage 22 and the pressure regulating chamber 11, and an opening 33 that is opened and closed by the regulating valve 3 is formed at the center of the partition wall 15a. The shaft portion 62 of the plunger 6 is slidably inserted into the plunger 33, and the opening peripheral edge of the partition wall 15 a on the primary gas passage 22 side is formed in the valve seat 32 of the adjustment valve 3.
[0037]
Then, the adjusting valve 3 closes the opening 33 by closely contacting the valve seat 32 with the movement of the plunger 6, and when the valve body 31 moves away from the valve seat 32 and opens the opening 33, A gas amount corresponding to the opening amount flows into the pressure regulating chamber 11 from the primary gas passage 22 through the gap between the opening 33 and the plunger 6.
[0038]
A cylindrical double valve adjuster 7 is attached to the primary gas passage 22 from the other end of the case body 15. The double-valve adjuster 7 is formed in a gas discharge port 14 for discharging the secondary pressure gas whose end side inner hole has been regulated, and the second connector for leading the regulated gas to the gas discharge port 14. 19 is connected. The position of the double valve adjuster 7 is adjusted by screwing the outer peripheral screw with the end screw of the case main body 15, and is fixed by a lock nut 17.
[0039]
Further, in the double valve adjuster 7, the distal end cylinder portion 71 is slidably inserted into the primary gas passage 22, and the sealing material 72 attached to the outer periphery of the distal end cylinder portion 71 is 1 outside the introduction gas hole 21. A sliding seal on the outer peripheral side is performed in close contact with the peripheral surface of the secondary gas passage 22. A shaft portion 62 between the valve body 31 of the adjustment valve 3 of the plunger 6 and the valve body 41 of the auxiliary adjustment valve 4 is slidably inserted into the central opening 43 of the distal end cylindrical portion 71. . The opening peripheral edge of the distal end cylinder portion 71 on the gas discharge port 14 side is formed in the valve seat 42 of the sub regulating valve 4.
[0040]
In the sub-regulating valve 4, the valve body 41 comes into close contact with the valve seat 42 with the movement of the plunger 6 and closes the opening 43 of the distal end cylindrical portion 71, and the valve body 41 moves away from the valve seat 42 and opens the opening 43. In this case, a gas amount corresponding to the opening amount flows out from the primary gas passage 22 to the gas discharge port 14 on the secondary pressure side through the gap between the opening 43 and the plunger 6.
[0041]
The position where the double valve adjuster 7 as the adjusting mechanism is inserted into the case main body 15 is such that when the valve body 31 of the adjusting valve 3 is seated on the valve seat 32 and the opening 33 is closed, the valve 33 of the auxiliary adjusting valve 4 is closed. Both the pressure loss values are adjusted to be the same so that the body 41 sits on the valve seat 42 and closes the opening 43.
[0042]
The adjustment valve 3 and the sub-regulation valve 4 are used to adjust the primary pressure to a predetermined secondary pressure regardless of the pressure according to the movement of the diaphragm 2, and the operation thereof will be described.
[0043]
First, the gas in the primary gas passage 22 flowing from the gas inlet 13 passes through the regulating valve 3 and is reduced to the secondary pressure, and reaches the gas outlet 14 through the secondary gas passage 64 in the plunger 6. . A product force of the pressure loss generated at this time and the valve element projection area of the adjusting valve 3 is generated in the direction in which the plunger 6 is retracted in the closing direction with respect to the adjusting valve 3 (left direction in the figure).
[0044]
The gas in the primary gas passage 22 passes through the sub-regulating valve 4 from the opening 43, that is, the gap between the double valve adjuster 7 and the plunger 6, and is reduced to the secondary pressure, and reaches the gas outlet 14. The pressure control chamber 11 communicates with the secondary gas passage 64 in the plunger 6. At this time, the product force of the pressure loss generated in the sub-regulating valve 4 and the valve element projection area of the sub-regulating valve 4 moves the plunger 6 forward in the opening direction with respect to the sub-regulating valve 4 (right direction in the figure). And acts in the opposite direction to the force in the regulating valve 3.
[0045]
Usually, the pressure loss generated in the two flow paths of the adjusting valve 3 and the sub-regulating valve 4 is different, but the pressure loss generated in the sub-regulating valve 4 is changed by arranging the double valve adjuster 7 so as to be movable and adjustable in the axial direction. Therefore, the pressure loss value of the regulating valve 3 can be canceled with high accuracy by the pressure loss value acting on the sub regulating valve 4.
[0046]
The diaphragm 2 is supported by a plunger 6 and a supporter 8, and is maintained at a position where the force due to the differential pressure between the secondary pressure and the atmospheric pressure and the biasing force due to the pressure adjusting spring 51 are balanced. When the secondary pressure changes according to the fluctuation of the gas discharge amount from the gas discharge port 14 or the fluctuation of the primary pressure, the displacement amount of the diaphragm 2 changes in response to this, and the plunger 6 The adjusting valve 3 and the sub-regulating valve 4 move in conjunction with the change in position to keep the secondary pressure constant. An arbitrary secondary pressure can be set by changing the urging force of the pressure adjusting spring 51 by moving the pressure adjusting screw 52 of the pressure setting unit 5.
[0047]
Further, the valve bodies 31 and 41 of the regulating valve 3 and the auxiliary regulating valve 4 are constituted by an elastic body made of an O-ring, and when a highly soluble gas such as dimethyl ether gas is circulated, the O-ring comes into contact therewith. Even if swelling and volume expansion occur, the volume change is suppressed in the direction perpendicular to the valve opening / closing movement direction, and therefore pressure loss and gas flow rate change due to O-ring volume expansion can be suppressed.
[0048]
Further, by performing pressure reduction from the primary pressure to the secondary pressure with the regulating valve 3 and the secondary regulating valve 4, the pressure loss value generated in each regulating valve is reduced as compared with the case where the pressure is reduced with one regulating valve. Since the clearance between the valve body and the valve seat of the regulating valve can be widened, the primary pressure is very high, that is, the pressure reduction is large and the valve clearance between the valve body and the valve seat is extremely narrow, with slight fluctuations. Stable performance can be obtained even when the pressure affects the secondary pressure.
[0049]
In the above-described embodiment, the valve bodies 31 and 41 of the regulating valve 3 and the sub regulating valve 4 are configured by an elastic body using an O-ring, but the valve seats 32 and 42 are configured by an elastic body using an O-ring. Even in such a case, the elastic body may be restricted by a circumferential groove structure so as not to be deformed in the valve opening / closing movement direction. Moreover, you may comprise with elastic materials other than an O-ring.
[0050]
FIG. 2 is a sectional view showing a pressure regulator 20 according to another embodiment of the present invention. The pressure regulator 20 of this embodiment is the same as that of the above-described embodiment except that the pressure chamber 11 further includes a valve closing spring 9, and the same components as those in FIG. Omitted.
[0051]
The valve closing spring 9 urges the plunger 6 in the retreating direction (leftward in the drawing), that is, in the valve closing direction of the adjusting valve 3. Specifically, the valve closing spring 9 is a coil spring, and one end abuts on the outer periphery of the cylindrical portion 61 of the plunger 6 in the pressure chamber 11 and the partition wall 15 a of the case main body portion 15. It is shrunk and arranged so as to press toward the atmosphere chamber 12 side.
[0052]
The secondary pressure is adjusted by the pressure adjusting screw 52 of the pressure setting unit 5 so that the biasing force of the pressure adjusting spring 51 is larger than that in the above-described embodiment by the biasing force of the valve closing spring 9. Adjusted.
[0053]
In the present embodiment, since the valve closing spring 9 is provided, the diaphragm 6 is formed between the pressure regulating chamber 11 and the atmospheric chamber 12 even when the biasing force of the pressure regulating spring 51 is weakened and the set pressure of the secondary pressure is low. The displacement is caused in accordance with the pressure difference, and the movement of the plunger 6 in accordance with the displacement of the diaphragm 6 makes it possible to accurately operate the regulating valve 3 and the auxiliary regulating valve 4, thereby enabling stable secondary pressure adjustment. When the urging force of the pressure adjusting spring 51 is adjusted to be smaller than the urging force of the valve closing spring 9, the plunger 6 moves backward by the urging force of the valve closing spring 9, and the adjusting valve 3 and A shut-off state in which the sub-regulating valve 4 is closed can be obtained, and gas discharge from the gas discharge port 14 is stopped.
[0054]
In the case of FIG. 1 that does not include the valve closing spring 9, it is assumed that the secondary pressure is normally set to a somewhat higher pressure, and the setting of the secondary pressure is sufficiently higher than the atmospheric pressure. In this case, a large force corresponding to the differential pressure between the secondary pressure and the atmospheric pressure acts on the diaphragm 6, and the adjusting valve 3 and the sub-regulating valve 4 are connected via the plunger 6 according to the displacement of the diaphragm 6. Thus, an accurate secondary pressure adjustment operation can be obtained. However, when the secondary pressure is set close to the atmospheric pressure and is set low, the force for deflecting the diaphragm 6 corresponding to the differential pressure with respect to the atmospheric pressure becomes small, and the plunger 6 other than this differential pressure In this embodiment, the plunger 6 is provided by the valve closing spring 9 because there is no force to deflect the diaphragm 6 in the backward direction, the responsiveness is lowered, and the action of adjusting the secondary pressure becomes unstable. The force which deviates the diaphragm 6 in the reverse direction is obtained, and the responsiveness of the diaphragm 6 is improved even when the setting of the secondary pressure is low, thereby ensuring a stable secondary pressure adjusting action. .
[0055]
Next, the experimental results of evaluating the pressure regulating action by the pressure regulator of the present invention (the embodiment shown in FIG. 1) are based on the pressure regulator of the comparative example (single valve pressure regulator shown in FIG. 5). 3 and FIG. 4 as compared with FIG.
[0056]
The single-valve pressure regulator 100 shown in FIG. 5 is in principle shown in FIG. 6 (a). If the same reference numerals are used, the primary pressure high-pressure gas introduced from the gas inlet 105 is A pressure regulating chamber defined by the diaphragm 104 and the atmospheric chamber 103 after passing through a regulating valve 106 (the valve body 106a is formed of a rigid body and the valve seat 106b is formed of an elastic body) that opens and closes according to the displacement of the diaphragm 104. The secondary pressure gas that flows into the pressure chamber 102 and passes through the pressure regulating chamber 102 is discharged from the gas discharge port 108. The urging force for the diaphragm 104 is adjusted by a pressure setting unit 109 including a pressure adjusting spring 109a and a pressure adjusting screw 109b, and a secondary pressure is set.
[0057]
<Measurement Example 1>
In this measurement example, the change in the secondary pressure when the primary pressure of the high-pressure gas (inert gas) supplied to the pressure regulator is changed, and the measurement result according to the present invention is shown by the solid line in FIG. The measurement result by a comparative example is shown with a broken line.
[0058]
The secondary pressure was set by adjusting the pressure adjusting screw of the pressure setting section so that the secondary pressure was 50 kPa when the primary pressure was 400 kPa in both the present invention and the comparative example. At that time, the gas flow rate is 40 mL / min.
[0059]
From the graph of FIG. 3, in the pressure regulator of the present invention indicated by the solid line, even if the primary pressure is changed in the range of 50 to 2000 kPa, the secondary pressure remains constant at the set value (50 kPa) and is constant. The pressure of was maintained. It was confirmed that the function of the regulating valve and the sub regulating valve eliminates the influence of the force acting with pressure loss, and the pressure regulating action can be obtained in a wide pressure range.
[0060]
On the other hand, in the single-valve pressure regulator according to the broken line comparative example, the secondary pressure is higher than the set value (50 kPa) in the region where the primary pressure is lower than 400 kPa, and 2 in the region where the primary pressure is higher than 400 kPa. The secondary pressure as a whole changed so that the secondary pressure decreased as the primary pressure increased so that the secondary pressure was lower than the set value (50 kPa), and a constant secondary pressure could not be maintained.
[0061]
<Measurement Example 2>
In this measurement example, dimethyl ether gas is used as a representative gas that swells an elastic material (rubber material) as a high-pressure gas introduced into a pressure regulator, and changes in gas flow over time are measured. The solid line shows the measurement result of the present invention, and the broken line shows the measurement result of the comparative example. The initial flow rate of dimethyl ether gas was 80 mL / min, and the test was performed at a temperature at which the vapor pressure was 400 kPa.
[0062]
From the graph of FIG. 4, in the pressure regulator of the present invention indicated by the solid line, the exhaust gas flow rate does not change while maintaining the initial flow rate even after 120 minutes have elapsed, and the O-ring swells due to contact with the gas. It was confirmed that there was no effect on the gas flow rate even if there was.
[0063]
On the other hand, in the single valve type pressure regulator according to the broken line comparative example, the valve gap changes due to the swelling of the valve seat by the elastic body, and the gas flow rate starts to decrease from about 15 minutes after the start of measurement, Thereafter, the flow rate suddenly decreased with the passage of time, and when about 60 minutes passed, the flow rate became 0, and gas was not discharged.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a pressure regulator according to an embodiment of the present invention.
FIG. 2 is a sectional view of a pressure regulator according to another embodiment of the present invention.
FIG. 3 is a graph showing the result of measuring the change in secondary pressure when the primary pressure of the high-pressure gas supplied to the pressure regulator is changed, together with a comparative example.
FIG. 4 is a graph showing the result of measuring the change in gas flow rate over time using dimethyl ether gas as the high pressure gas supplied to the pressure regulator together with a comparative example.
5 is a cross-sectional view of a comparative pressure regulator used in the measurement examples of FIGS. 3 and 4. FIG.
FIG. 6 is a schematic diagram showing the basic structure of a general pressure regulator.
[Explanation of symbols]
10, 20 Pressure regulator
1 case
2 Diaphragm
3 Regulating valve
4 Sub-regulator valve
5 Pressure setting part
6 Plunger
7 Double valve adjuster (adjustment mechanism)
9 Valve closing spring
11 Pressure control chamber
12 Atmospheric chamber
13 Gas inlet
14 Gas outlet
22 Primary gas passage
31, 41 Disc
32, 42 Valve seat
33, 43 opening
51 Pressure spring
52 Pressure adjusting screw
61 Tube
62 Shaft
63 Circumferential groove
64 Secondary gas passage

Claims

A gas introduction port for introducing a high-pressure gas having a primary pressure and communicating with the primary gas passage ;
An adjustment valve for reducing the primary pressure of the high-pressure gas in the primary gas passage to a secondary pressure with a pressure loss;
A pressure regulating chamber for relaxing pressure vibration of the gas that has passed through the regulating valve;
A diaphragm that defines the pressure regulating chamber and the atmospheric chamber, and is displaced by receiving a secondary pressure of the pressure regulating chamber;
A pressure setting unit for adjusting the displacement amount of the diaphragm;
A cylindrical portion fixed to the diaphragm and positioned in the pressure adjusting chamber and a shaft portion extending in the axial direction from the tip thereof, and the cylindrical portion and the shaft portion penetrate from the one end to the other end in the central portion. A plunger provided with a passage, and having a communication port communicating with the pressure regulating chamber and the secondary gas passage on a side wall of the cylindrical portion;
In the pressure regulator and a gas discharge port for discharging a gas having a secondary pressure through the secondary gas passage,
Connected by the plunger and operating in conjunction with the regulating valve, the primary pressure of the high pressure gas having a pressure loss is reduced to a secondary pressure, and the force received with the pressure loss is the regulating valve. A sub-regulating valve installed to act in the opposite direction to the force acting on the plunger in accordance with the pressure loss in the counter, and to cancel the force acting on the plunger;
An adjustment mechanism capable of adjusting a pressure loss value of the auxiliary adjusting valve by changing a valve seat position of the auxiliary adjusting valve;
The valve body of the regulating valve and the valve body of the sub regulating valve are installed on the plunger, the valve body of the regulating valve is disposed on the primary pressure side, and the valve body of the sub regulating valve is on the secondary pressure side. Arranged,
The adjustment mechanism has an opening through which a shaft portion of the plunger is slidably inserted between a circumferential groove portion to which the valve body of the adjustment valve is attached and a circumferential groove portion to which the valve body of the sub adjustment valve is attached. And a double valve adjuster having a valve seat for the auxiliary regulating valve, wherein the pressure loss value received by the regulating valve and the pressure loss value received by the auxiliary regulating valve are adjusted to be the same. Pressure regulator.

The adjusting mechanism is a pressure regulator of claim 1, wherein said that the insertion position of the auxiliary control valve to close is adjusted when closing the regulating valve.

Said valve seat of said sub-control valve of the double valve adjuster, a pressure regulator according to claim 1, characterized by being formed on the periphery of the opening of the gas outlet side.

Wherein the plunger, the pressure regulator of any one of claims 1 to 3, further comprising a closing spring for urging the closing direction of the control valve.

Gas secondary pressure of the pressure regulating chamber is of any one of claims 1 to 4 through the secondary gas passage of the central portion of the plunger, characterized in that communicating with the gas outlet Pressure regulator.

One of the valve body or the valve seat includes an elastic body in the adjustment valve and the sub adjustment valve, and the elastic body of the adjustment valve and the sub adjustment valve changes the volume thereof in a direction perpendicular to the valve opening / closing movement direction. The pressure regulator according to any one of claims 1 to 5 , wherein the pressure regulator is arranged in a regulated manner.

The pressure regulator according to claim 6, wherein the elastic body is an O-ring.

The pressure regulator according to claim 1 , wherein the high-pressure gas is dimethyl ether gas.