JP3718488B2

JP3718488B2 - Valve device

Info

Publication number: JP3718488B2
Application number: JP2002211540A
Authority: JP
Inventors: 薫野道; 清治石井; 誠二宮
Original assignee: Kawasaki Precision Machinery Ltd
Current assignee: Kawasaki Precision Machinery Ltd
Priority date: 2002-07-19
Filing date: 2002-07-19
Publication date: 2005-11-24
Anticipated expiration: 2022-07-19
Also published as: JP2004054624A

Description

【０００１】
【発明の属する技術分野】
本発明は、たとえば流体圧装置に設けられる弁装置に関する。
【０００２】
【従来の技術】
図１８は、従来の技術の弁装置１を示す断面図である。図１９は、弁装置１を示す構成回路図である。弁装置１は、天然ガス自動車のタンク２に設けられるレギュレータ装置であって、米国特許第６０４１７６２に示されている。この弁装置１は、タンク２のガスを減圧してタンク２外に吐出する減圧弁部３と、タンク２のガスの吐出および吐出停止をする開閉弁部４と、緊急時開放用の安全弁部５とを有し、減圧弁部３がタンク２内に設けられ、開閉弁部４および安全弁部５がタンク２外に設けられている。また安全弁部５を作動させる圧力および温度を検出する検出センサ６が、タンク２外に設けられている。開閉弁部４は、減圧弁部３の下流側に設けられている。
【０００３】
図２０は、従来の技術の減圧弁部３の構成を簡略化して模式的に示す断面図である。減圧弁部３は、ハウジング７内に、軸線方向に変位自在にピストン８が保持され、ピストン８に軸線方向一方ｘ１に向かうばね力を与えるばね部材９が設けられて構成される。ハウジング７には、一次ポート１０および二次ポート１１が形成され、一次ポート１０を外囲して突起片１２が形成され、この突起片１２とこれに対向するピストン８のシート部１３とによって、減圧のためのオリフィス１４が形成される。このようにして、ハウジング７内が、一次ポート１０に連なる一次圧力室１５と、二次ポート１１に連なる二次圧力室１６とに仕切られる。この減圧弁部３は、一次ポート１０に供給された一次圧力（以下「一次圧」という）ｐ１の流体を、オリフィス１４の通過によって二次圧力（以下「二次圧」という）ｐ２に減圧し、二次ポート１１から吐出することができる。
【０００４】
【発明が解決しようとする課題】
弁装置１では、減圧弁部３と開閉弁部４とが、ガスの流下方向に縦列に設けられるので、弁装置１が大形化してしまう。また開閉弁部４を減圧弁部３よりも下流側に設ける構成では、開閉弁部４を閉じた状態で長時間放置されたとき、減圧弁部３の二次圧が一次圧と同一の高圧になってしまう場合があり、この場合、開閉弁部４を開いた直後に、高圧のガスが吐出されてしまう。
【０００５】
図２１は、従来技術の減圧弁部３の二次圧力ｐ２を示すグラフである。減圧弁部３では、二次圧ｐ２は、一次圧ｐ１を用いて、次式（１）のように表される。
【０００６】
【数１】

【０００７】
ここで、ａ１は、軸線方向一方ｘ１に一次圧ｐ１を受ける受圧面積であり、ａ２は、軸線方向一方ｘ１に二次圧ｐ２を受ける受圧面積であり、ａ３は、軸線方向他方ｘ２に二次圧ｐ２を受ける受圧面積である。またｋは、ばね部材９のばね定数であり、Δｈは、ばね部材９の初期状態での撓み量である。またｚは、ピストン３の初期状態からの変位量であって、式（２）で表されるように、一次圧ｐ１と、減圧弁部３を流下する流体の流量ｑとの関数で表される。
【０００８】
減圧弁部３では、ピストン８が一次圧ｐ１を面積ａ１の受圧面で軸線方向一方ｘ１にだけ受ける構成であって、二次圧ｐ２を表す式（１）は、右辺の第一項および第二項がともに、一次圧ｐ１の変化に伴って変化する式となる。特に、式（１）の右辺第二項は、一次圧ｐ１の変化に伴って大きく変化する項である。したがって図２１に示されるように、一次圧ｐ１が変化すると、二次圧ｐ２が大きく変化する。
【０００９】
また減圧弁部３の流量キャパシティ、すなわち最大許容流量を大きくするためには、突起片１２の直径を大きくする必要がある。突起片１２の直径を大きくすると、受圧面積ａ１が大きくなり、一次圧ｐ１の変化量Δｐ１に対する二次圧ｐ２の変化量Δｐ２が大きくなる。この二次圧ｐ２の変化量Δｐ２を小さく抑えるためには、式（１）の右辺第二項の分母を大きくするために、受圧面積ａ３を大きくする必要があり、ピストン８の最大外径が大きくなる。またこれに伴ってばね部材９も、外径を大きくする必要がある。したがって減圧弁部３の半径方向寸法が大きくなる。
【００１０】
また減圧弁部３について具体的に説明したけれども、開閉弁部４においても、減圧弁部３と同様に、最大許容流量を大きくしようとすると、開閉弁部４の半径方向寸法が大きくなる。
【００１１】
本発明の目的は、半径方向の寸法を小さく抑えることができる弁装置を提供することである。
【００１２】
また本発明の目的は、減圧弁部において、一次圧力の変化に伴う二次圧力の変化を小さく抑えることができる弁装置を提供することである。
【００１３】
また本発明の目的は、耐久性を高くできるとともに、開閉弁部を閉じて長期間放置した後、開閉弁部を開いても、高圧の流体が吐出されることを防ぐことができる弁装置を提供することである。
【００１４】
【課題を解決するための手段】
請求項１記載の本発明は、一次ポートおよび二次ポートが形成されるハウジングと、
ハウジング内に設けられ、二次ポートにおける流体の二次圧力を、一次ポートにおける一次圧力よりも減圧させる減圧弁部と、
減圧弁部を同軸に挿通して設けられ、一次ポートと二次ポートとの接続状態を開状態と閉状態とに切換える開閉弁部とを含むことを特徴とする弁装置である。
【００１５】
本発明に従えば、一次ポートと二次ポートとの接続状態を切換える開閉弁部が、二次圧力を一次圧力よりも減圧させる減圧弁部を挿通して設けられる。これによって開閉弁部と減圧弁部とを単に縦列して設ける場合に比べて、軸線方向の寸法を小さくすることができる。しかも開閉弁部と減圧弁部とは、同軸に設けられており、開閉弁部が減圧弁部を挿通する部分では、ハウジングを共用することができ、開閉弁部と減圧弁部とを単に並列して設ける場合に比べて、半径方向の寸法を小さくすることができる。このように軸線方向寸法および半径方向寸法を小さくして、小形の弁装置を実現することができる。
【００１６】
請求項２記載の本発明は、減圧弁部は、
ハウジング内に軸線方向に変位自在に保持され、一次ポートに連なる一次圧力室と二次ポートに連なる二次圧力室とにハウジング内を仕切り、一次圧力室の流体から軸線方向一方に向かう一次圧力を受ける一次受圧面積の一次受圧面と、一次圧力に保持される減圧背圧力室の流体から軸線方向他方に向かう一次圧力を一次受圧面積と同一の背受圧面積で受ける背受圧面と、二次圧力室の流体から軸線方向他方に向かう二次圧力を受ける二次受圧面とが形成される減圧ピストンと、減圧ピストンに軸線方向一方に向かう減圧ばね力を与える減圧ばね力発生手段とを含むことを特徴とする。
【００１７】
本発明に従えば、減圧ピストンに一次受圧面積と同一の背受圧面積を有する背受圧面が形成され、この背受圧面は減圧背圧力室から一次圧力を受けるように構成される。一次受圧面と背受圧面とは、軸線方向に相互に反対方向から一次圧力を受ける。これによって一次圧力に基づいて、減圧ピストンに軸線方向一方に働く力と、減圧ピストンに軸線方向他方に働く力とを釣り合わせて、減圧ピストンに働く一次圧力による軸線方向の力を相殺することができるので、二次圧力が、一次圧力の影響を受けにくくすることができる。したがって一次圧力の変化量に対する二次圧力の変化量を、大幅に低減することができる。
【００１８】
さらに最大許容流量を大きくするために、一次圧力を受ける減圧ピストンの一次受圧面積を大きくしても、一次受圧面積の変化が二次圧力の変化に大きく影響しないので、一次圧力の変化量に対する二次圧力の変化量を抑えるために、減圧ピストンの最大外径を大きくする必要がない。したがって半径方向寸法を小さく抑えて最大許容流量を大きくし、かつ二次圧力の変化量を小さく抑えることができる弁装置を実現することができる。
【００１９】
請求項３記載の本発明は、開閉弁部は、
ハウジング内に軸線方向に変位自在に保持され、ハウジングに形成される弁座に着座および離間することによって、一次ポートと二次ポートとの接続状態を切換える開閉ピストンであって、開閉ピストンを弁座に着座させる方向の一次圧力を閉受圧面積で受ける閉受圧面と、開閉ピストンを弁座から離間方向の一次圧力を閉受圧面積と同一の開受圧面積で受ける開受圧面とが形成される開閉ピストンと、
開閉ピストンに軸線方向の駆動力を与えて、一次ポートと二次ポートとの接続状態を、開状態と閉状態とに切換え駆動する開閉駆動手段とを含むことを特徴とする。
【００２０】
本発明に従えば、開閉ピストンに、閉受圧面積を有する閉受圧面と、閉受圧面積と同一の開受圧面積を有する開受圧面が形成され、閉受圧面は開閉ピストンを弁座に着座させる方向に一次圧力を受け、開受圧面は開閉ピストンを弁座から離間させる方向に一次圧力を受けるように構成される。閉受圧面と開受圧面とは、軸線方向に相互に反対方向から一次圧力を受ける。これによって一次圧力に基づいて、開閉ピストンに軸線方向一方に働く力と、開閉ピストンに軸線方向他方に働く力とを釣り合わせて、開閉ピストンに働く供給圧力による軸線方向の力を相殺することができるので、一次圧力の大小に拘わらず、開閉駆動手段が一次ポートと二次ポートとの接続状態を切換えるために、開閉ピストンに与える軸線方向の駆動力を小さくすることができる。
【００２１】
さらに最大許容流量を大きくするために、一次圧力を受ける開閉ピストンの閉受圧面積および開受圧面積を大きくしても、閉受圧面積と開受圧面積とを同一に形成することで、一次圧力に基づいて、開閉ピストンに軸線方向一方に働く力と、開閉ピストンに軸線方向他方に働く力とを釣り合わせて、ピストンに働く一次圧力による軸線方向の力を相殺できる。これによって開閉ピストンを駆動するために大きな駆動力を必要とせず、開閉駆動手段を大きくすることなく、最大許容流量を大きくすることができる弁装置を容易に実現することができる。
【００２２】
請求項４記載の本発明は、開閉弁部における流路の開閉位置は、減圧弁部における減圧位置に比べて、流体の流下方向上流側に配置されていることを特徴とする。
【００２３】
本発明に従えば、開閉弁部における流路の開閉位置が、減圧弁部における減圧位置に比べて、流体の流下方向上流側に配置されている。これによって開閉弁部が閉じた状態では、減圧弁部に高圧の一次圧力が働くことがなく、耐久性を高くすることができる。また開閉弁部を通過した流体は、必ず減圧弁部で減圧されることになり、開閉弁部を閉じた状態で長時間放置した後に、開閉弁部を開放しても、二次圧力は、減圧されている。このように高圧のガスが吐出されてしまうことが防がれる。
【００２４】
【発明の実施の形態】
図１は、本発明の実施の一形態の弁装置２０を示す断面図である。弁装置２０は、一次側から二次側に流体が流下する流路に介在され、供給される一次圧力（以下「一次圧」という）Ｐ１の流体を、一次圧Ｐ１よりも低い二次圧力（以下「二次圧」という）Ｐ２に減圧して吐出する弁装置である。本実施の形態では、弁装置２０は、高圧容器である高圧タンク（以下、単に「タンク」という場合がある）２００の開口部８１に装着され、タンク２００に貯留される流体のタンク２００外への排出および排出停止を制御するために用いられる。したがって一次側がタンク２００内となり、二次側がタンク２００外となり、タンク２００内からタンク２００外への流体の流下を制御する。
【００２５】
この弁装置２０は、ハウジング２１と、減圧ピストン２２と、減圧ばね部材２３と、筒状部材２４と、開閉ピストン８５と、開閉駆動手段８６とを含んで構成される。開閉ピストン８５は、開閉弁体８７と、軸体８８とを含み、開閉駆動手段８６は、駆動ばね部材８９と、電磁ソレノイド９０とを含む。少なくとも減圧ばね部材２３と、筒状部材２４とを含んで、減圧弁部が構成され、少なくとも開閉ピストン８５と、開閉駆動手段８６とを含んで、開閉弁部が構成される。
【００２６】
弁装置２０では、少なくも、ハウジング２１、減圧ピストン２２、減圧ばね部材２３、筒状部材２４、開閉ピストン８５および駆動ばね部材８９は、相互に同軸に設けられる。本実施の形態では電磁ソレノイド９０を含めて、同軸に設けられ、それぞれの軸線は、弁装置２０の装置軸線Ｌ１と一致している。
【００２７】
ハウジング２１は、有底円筒状のハウジング本体２５と、ハウジング本体２５の開放端部２６に内挿されて装着されるキャップ部材２７とを有する。キャップ部材２７は、ハウジング本体２５に対して、装置軸線Ｌ１まわりに回転して、装置軸線Ｌ１に沿って螺進および螺退自在に螺着され、軸線方向の位置を調節自在に設けられる。キャップ部材２７は、有底筒状であって、開放端部９１をハウジング本体２５の底部２９側に配置して、したがってハウジング２１の軸線方向一端部３１側に底部９２を配置し、ハウジング２１の軸線方向他端部３２側に配置して設けられる。ハウジング本体２５の内周部とキャップ部材２７の外周部との間は、周方向全周にわたってシールが達成されている。
【００２８】
キャップ部材２７には、底部９２に装置軸線Ｌ１に沿って挿通する一次ポート２８が形成され、ハウジング本体２５の底部２９には、装置軸線Ｌ１からずれて二次ポート３０が形成される。このようにハウジング２１には、軸線方向一端部３１に一次ポート２８が形成され、軸線方向他端部３２に二次ポート３０が形成され、このハウジング２１内に、一次ポート２８と二次ポート３０を連通する弁空間９４が形成される。
【００２９】
またキャップ部材２７には、開放端部９１寄りの部分に、半径方向内方に突出して周方向全周に延びるフランジ状の内向き凸部９３が形成されている。この内向き凸部９３には、軸線方向一方Ｘ１の端面部、したがってハウジング本体２５の底部２９に臨む側の端面部に、ハウジング本体２５の底部２９に向けて、軸線方向一方Ｘ１へ先細状に突出し、周方向全周に延びる円環状の突起片３８が形成される。またキャップ部材２７の内向き凸部９３には、軸線方向他方Ｘ２の端面部、したがってキャップ部材２７の底部９２に臨む側の端面部に、弁座１１２が形成される。
【００３０】
このようなハウジング２１は、一次ポート２８がタンク２００内で開口し、二次ポート３０がタンク２００外で開口するように、外周部をタンク２００の開口部８１における内周部に螺合して螺着される。ハウジング２１の外周部とタンク２００の開口部８１における内周部との間は、周方向全周にわたってシールが達成されている。軸線方向一方Ｘ１は、ハウジング２１の軸線方向一端部３１から他端部３２に向かう方向である。
【００３１】
減圧ピストン２２は、有底円筒状に形成され、軸線方向一端部である底部３５側をハウジング２１の軸線方向一端部３１側に配置し、軸線方向他端部である開放端部３６側をハウジング２１の軸線方向他端部３２側に配置して、ハウジング２１内に保持される。この状態で減圧ピストン２２は、装置軸線Ｌ１に沿って、軸線方向一方Ｘ１およびその反対の軸線方向他方Ｘ２へ変位自在である。
【００３２】
ハウジング２１の軸線方向両端部３１，３２間の軸線方向中間部３９には、半径方向内方に突出して周方向全周に延びるフランジ状の内向き凸部４０が形成され、この内向き凸部４０の内周部に、減圧ピストン２２の底部３５および開放端部３６間の軸線方向中間部３７における外周部が、シールを達成した状態で当接している。また減圧ピストン２２の開放端部３６には、半径方向外方に突出して周方向全周に延びるフランジ状の外向き凸部４１が形成され、この外向き凸部４１の外周部が、ハウジング２１の軸線方向中間部３９における内向き凸部４０よりも軸線方向他端部３２寄りの部分の内周部に、シールを達成した状態で当接している。
【００３３】
減圧ばね力発生手段である減圧ばね部材２３は、圧縮コイルばねであり、ハウジング２１と減圧ピストン２２とが半径方向に間隔をあけて形成される円環状のばね収容空間４３に配置されて、減圧ピストン２２に外嵌される状態でハウジング２１内に設けられる。ばね収容空間４３は、内向き凸部４０と外向き凸部４１との間に形成され、ハウジング２１に形成される大気開放孔４４によって大気に開放されている。
【００３４】
減圧ばね部材２３は、軸線方向一端部４５がハウジング本体２５の内向き凸部４０に支持され、軸線方向他端部４６が開閉ピストン２２の外向き凸部４１に支持される。この減圧ばね部材２３によって、ハウジング２１に対して軸線方向一方Ｘ１に向かうばね力を、減圧ピストン２２に与えることができる。
【００３５】
筒状部材２４は、大略的に円筒状であって、ハウジング２１に保持され、軸線方向一端部４８側の部分を減圧ピストン２２内に、減圧ピストン２２に対して、装置軸線Ｌ１に沿って、軸線方向一方Ｘ１および軸線方向他方Ｘ２へ変位自在に挿入されている。この筒状部材２４は、少なくとも軸線方向他端部５１が減圧ピストン２２から突出した状態で設けられ、この軸線方向他端部５１は、残余の部分に比べて外径が大きく形成されており、減圧ピストン２２の開放端部３６を軸線方向に支持することができるように構成されている。
【００３６】
ハウジング２１の軸線方向一端部３１、したがってハウジング本体２５の底部２９には、開放端部２６に向かって（軸線方向他方Ｘ２に）凹となる嵌合凹所５０が形成される。筒状部材２４は、この嵌合凹所５０に軸線方向他端部５１が嵌まり込んで保持されている。
【００３７】
筒状部材２４の軸線方向一端部４８は、その外周部が減圧ピストン２２の内周部にシールを達成した状態で当接し、開閉ピストン８５と協働して、減圧ピストン２２と筒状部材２４との間に減圧背圧力室５５が形成される。また筒状部材２４は、軸線方向一端部４８を除く部分であって、減圧ピストン２２内に挿入される部分の外周部は、減圧ピストン２２の内周部との間に半径方向に間隔をあけており、円環状のピストン内空間５６が形成される。
【００３８】
開閉ピストン８５の開閉弁体８７は、有底筒状の弁体部９５と、弁体部９５の底部から同軸に突出する動力伝達部９６とを有する。この開閉弁体８７は、弁体部９５をハウジング２１の軸線方向一端部３１側に配置し、動力伝達部９６をハウジング２１の軸線方向他端部３２側に配置し、弁体部９５が、キャップ部材２７の底部９２と内向き凸部９３とに挟まれる弁体室９７に嵌まり込み、かつ動力伝達部９６がキャップ部材２７の内向き凸部９３の内方を緩やかに挿通する状態で、ハウジング２１内に保持される。また減圧ピストン２２の底部３５には、この底部３５を装置軸線Ｌ１に沿って挿通する透孔７１が形成されており、動力伝達部９６は、この透孔７１を緩やかに挿通して、減圧ピストン２２内まで延びている。
【００３９】
開閉弁体８７は、このように設けられた状態で、弁体部９５の底部に形成される開閉シート部９９が弁座１１２に着座する閉位置と、開閉シート部９９が弁座１１２から離間する開位置とにわたって、装置軸線Ｌ１に沿って軸線方向一方Ｘ１および軸線方向他方Ｘ２へ変位自在である。開閉弁体８７が開位置にある場合、一次ポート２８と、減圧ピストン一次圧受圧空間部１００とが開放され、開閉弁体８７が閉位置にある場合、一次ポート２８と、減圧ピストン一次圧受圧空間部１００とが閉塞される。減圧ピストン一次圧受圧空間部１００は、キャップ部材２７の内向き凸部９３と、減圧ピストン２２の底部３５とに挟まれ、かつキャップ部材２７の内向き凸部９３に形成される突起片３８の半径方向内方側の空間である。
【００４０】
開閉ピストン８５の軸体８８は、大略的に円筒状であって、ハウジング２１に装置軸線Ｌ１に沿って、軸線方向一方Ｘ１および軸線方向他方Ｘ２へ変位自在に保持される。この軸体８８は、軸線方向一端部１０１側の部分を筒状部材２４内に、筒状部材２４に対して、装置軸線Ｌ１に沿って、軸線方向一方Ｘ１および軸線方向他方Ｘ２へ変位自在に挿入されている。
【００４１】
この軸体８８は、少なくとも軸線方向他端部１０２が筒状部材２４から突出した状態で設けられる。ハウジング２１の軸線方向他端部３２、具体的にはハウジング本体２５の底部２９には、装置軸線Ｌ１に沿って挿通する挿通孔１０４が形成されており、軸体８８は、この挿通孔１０４を挿通して、軸線方向他端部１０２がハウジング２１の外部に突出するように延びている。
【００４２】
軸体８８の軸線方向一端部１０１は、その外周部が筒状部材２４の内周部にシールを達成した状態で当接し、これによって前述の減圧背圧力室５５の形成にされる。また軸体８８は、挿通孔１０４を挿通する部分に、軸線方向一端部１０１側の部分が軸線方向他端部１０２側の部分に比べて、外径の大きい段差部１０５が形成され、段差部１０５の軸線方向両側で、外周部がハウジング本体２５の挿通孔１０４に臨む内周部にシールを達成した状態で当接している。
【００４３】
このようにして、ハウジング本体２５と軸体８８とによって、軸体８８の段差部１０５が臨む開閉背圧力室１０６が形成され、この開閉背圧力室１０６は、ハウジング本体２５に形成される連通路１０７によってタンク２００内に連通され、一次圧Ｐ１が導かれる。またハウジング２１と、筒状部材２４と、軸体８８とによって空間１２３が形成されが、この空間１２３は、前記大気開放孔４４によって、大気に開放されている。
【００４４】
開閉弁体８７と軸体８８とは、相互に当接した状態で、開閉弁体８７から軸体８８に、軸線方向一方Ｘ１への力を伝達することができ、軸体８８から開閉弁体８７に、軸線方向他方Ｘ２への力を伝達することができる。したがって開閉ピストン８５は、開閉弁体８７と軸体８８とが相互に当接した状態で、開閉弁体８７に軸線方向一方Ｘ１への駆動力を与えて、一体に軸線方向一方Ｘ１へ変位させることができ、軸体８８に軸線方向他方Ｘ２への駆動力を与えて、一体に軸線方向他方Ｘ２へ変位させることができる。
【００４５】
開閉駆動手段８６の駆動ばね部材８９は、圧縮コイルばねであり、弁体室９７に配置されて、開閉弁体８７の弁体部９５に少なくとも部分的に内挿されて設けられる。駆動ばね力発生手段であるこの駆動ばね部材８９は、軸線方向一端部１１０がキャップ部材２７の底部９２に支持され、軸線方向他端部１１１が弁体部９５の底部付近（底部を含む）に支持される。この駆動ばね部材８９によって、ハウジング２１に対して、装置軸線Ｌ１沿って軸線方向へ変位駆動するためのばね力を、具体的には軸線方向一方Ｘ１に向かうばね力であって弁体部９５を弁座１１２に着座させる閉方向のばね力を、開閉ピストン８５に与えることができる。
【００４６】
開閉駆動手段８６の電磁ソレノイド９０は、ハウジング２１の外方に配置され、ハウジング本体２５の底部２９に、挿通孔１０４を外方から覆う状態で設けられる。電磁駆動源であるこの電磁ソレノイド９０は、装置軸線Ｌ１に沿って、軸線方向一方Ｘ１および軸線方向他方Ｘ２へ変位自在に保持される駆動部材１２０と駆動コイルとを有している。電磁ソレノイド９０とハウジング２１とによって形成され、軸部材８８が臨む空間１２２は、前記大気開放孔４４によって、大気に開放されている。
【００４７】
駆動コイルへの通電および非通電を切換えることによって、駆動部材１２０を装置軸線Ｌ１に沿って軸線方向へ変位させ、この駆動部材１２０によって軸体８８を押圧して、ハウジング２１に対して、装置軸線Ｌ１に沿って軸線方向へ変位駆動するための電磁駆動力を、具体的には軸線方向他方Ｘ２に向かう電磁駆動力であって弁体部９５を弁座１１２から離間させる開方向の電磁駆動力を、開閉ピストン８５に与えることができる。電磁ソレノイド９０による電磁駆動力は、駆動ばね部材８９のばね力よりも大きい。
【００４８】
このような弁装置２０では、上述のように減圧ピストン２２の外周部が、２箇所において、ハウジング２１の内周部に、周方向全周にわたってシールを達成した状態で当接している。ハウジング２１内には、ハウジング２１と減圧ピストン２２との間に、ハウジング本体２５の内向き凸部４０よりも軸線方向他方Ｘ２側に、有底筒状の第１空間６０が形成されるとともに、減圧ピストン２２の外向き凸部４１よりも軸線方向一方Ｘ１側に、二次ポート３０に連なる環状の第２空間６１が形成される。
【００４９】
減圧ピストン２２は、軸線方向一端部の端面部分に、周方向全周に延びる特殊樹脂から成る減圧シート部６２が形成され、この減圧シート部６２がキャップ部材２７の突起片３８に軸線方向に対向して、周方向全周に延びる円環状のオリフィス６３が形成される。第１空間６０は、オリフィス６３を介して連なる２つの空間部１００，６５を有する。オリフィス６３よりも半径方向内方側となる領域は、一次ポート２８に連なる前述の減圧ピストン一次圧受圧空間部１００である。
【００５０】
また減圧ピストン２２には、軸線方向中間部３７における筒状部材２４の軸線方向一端部４８に当接する部分よりも開放端部３６寄りの部分に、内外に挿通する挿通孔６７が形成される。この挿通孔６７によって、第１空間６０のオリフィス６３よりも半径方向外方側の外側空間部６５と、ピストン内空間５６とが連通される。
【００５１】
また筒状部材２４の軸線方向他端部５１およびその付近には、一端部が減圧ピストン２２内に挿入される部分で開口し、他端部が減圧ピストン２２から突出する部分で開口する連通孔６８が形成される。この連通孔６８によって、第２空間６１と、ピストン内空間５６とが連通されるとともに、これら第２空間６１およびピストン内空間５６が、二次ポート３０に連通される。オリフィス６３よりも半径方向外方側の外側空間部６５、第２空間６１、ピストン内空間５６、挿通孔６７および連通孔６８を含んで、二次ポート３０に連なる二次圧力室７０が構成される。
【００５２】
開閉弁体８７の弁体部９５には、内外に挿通する挿通孔１１５が形成される。この挿通孔１１５によって、弁体室９７内に密閉される領域が形成されることを防ぐことができる。この弁体室９７と減圧ピストン一次圧受圧空間部１００とは、キャップ部材２７の内向き凸部９３と開閉弁体８７の動力伝達部９６との間の環状の連通空間１２１を介して連なり、弁体室９７および減圧ピストン一次圧受圧空間部１００が一次ポート２８に連通される。弁体室９７、減圧ピストン一次圧受圧空間部１００および連通空間１２１を含んで、一次ポート２８に連なる一次圧力室６４が構成される。
【００５３】
開閉弁体８７によって、弁体室９７と減圧ピストン一次圧受圧空間部１００との間を、開放する開状態と、閉塞する閉状態とに切換えることができる。閉状態では、減圧ピストン一次圧受圧空間部１００および連通空間１２１には、一次圧Ｐ１が導かれないが、開状態では、一次圧力室６４全体に一次圧Ｐ１が導かれる。また弁体室９７と減圧ピストン一次圧受圧空間部１００との間を、開放する開状態と、閉塞する閉状態とに切換えることによって、一次ポート２８と二次ポート３０との間を、開放する開状態と、閉塞する閉状態とに、一次ポート２８と二次ポート３０との接続状態を切換える。
【００５４】
また減圧ピストン２２の底部３５には、この底部３５を装置軸線Ｌ１に沿って挿通する透孔７１が形成されている。この透孔７１によって、一次圧力室６４の減圧ピストン一次圧受圧空間部１００と、減圧背圧力室５５とが連通され、減圧背圧力室５５が一次圧Ｐ１に保持される。
【００５５】
このような弁装置２０では、電磁ソレノイド９０の駆動コイルに駆動電流を与えない非通電状態では、開閉ピストン８５は、駆動ばね部材８９の軸線方向一方Ｘ１に向かう閉方向のばね力によって、図１に示すような、開閉弁体８７が開閉シート部９９を弁座１１２に着座させる閉位置にある第１位置に配置される。この状態で、弁装置２０は、一次ポート２８から二次ポート３０への流体の流下を阻止し、タンク２００内からタンク２００外への流体の吐出を停止する。
【００５６】
また弁装置２０では、電磁ソレノイド９０の駆動コイルに駆動電流を与える通電状態では、電磁ソレノイド９０によって発生される電磁力であって、軸線方向他方Ｘ２に向かう開方向の電磁力によって、駆動ばね部材８９のばね力に抗して、開閉ピストン８５が、図１の第１位置から軸線方向他方Ｘ２に変位した第２位置、したがって開閉弁体８７が開閉シート部９９を弁座１１２から離間させる開位置にある第２位置に配置される。この状態で、弁装置２０は、一次ポート２８から二次ポート３０への流体の流下を許容し、タンク２００内からタンク２００外への流体の吐出を解除する。
【００５７】
このように開閉弁部は、電磁ソレノイド９０への駆動電流の供給および供給停止によって、電磁ソレノイド９０と駆動ばね部材８９とが協働して、開閉ピストン８５に電磁力およびばね力の少なくともいずれか一方を働かせて、開閉ピストン８５を変位駆動させ、一次ポート２８と二次ポート３０との連通および遮断を制御することができる。本実施の形態において、開閉ピストン８５の駆動力は、駆動ばね部材８９によるばね力および電磁ソレノイド９０による電磁力を含む。
【００５８】
また弁装置２０では、減圧ピストン２２は、ハウジング２１内を、オリフィス６３によって連なる一次圧力室６４と二次圧力室７０とに仕切る。開閉弁部が開いている状態で、一次ポート２８に供給される流体は、一次圧力室６４からオリフィス６３を通過して二次圧力室７０に、具体的には、第１空間６０の外側空間部６５に流下し、挿通孔６７、ピストン内空間５６および連通孔６８を経て、二次ポート３０に流下し、二次ポート３０から吐出される。このように弁装置２０を流体が流下するとき、減圧ピストン２２は、筒状部材２４の軸線方向他端部５１との間に軸線方向に間隔をあける。
【００５９】
流体がオリフィス６３を通過するとき、流体の圧力が低下される。言い換えるならば、流体は、一次圧力室から、オリフィス６３を通過することによって減圧されて、二次圧力室７０に流下する。したがって一次ポート２８、一次圧力室６４および減圧背圧力室５５内の流体は、一次圧Ｐ１を有し、二次ポート３０および二次圧力室７０内の流体は、一次圧Ｐ１よりも低い減圧された二次圧Ｐ２を有する。
【００６０】
図２は、弁装置２０の各部の寸法を説明するために示す断面図である。開閉ピストン８５の開閉弁体８７は、その外表面が、一次圧Ｐ１に保持される一次圧力室６４および減圧背圧力室５５に臨み、軸体８８は、一次圧Ｐ１に保持される減圧背圧力室５５および開閉背圧力室１０６に臨んでいる。このような開閉ピストン８５は、開閉ピストン８５を弁座１１２に着座させる方向の一次圧Ｐ１を、有効的に受ける閉受圧面積Ａ１の閉受圧面１３０を有する。閉受圧面積Ａ１は、開閉ピストン８５が一次圧力室６４および減圧背圧力室５５内の流体によって軸線方向一方Ｘ１に一次圧Ｐ１を受ける受圧面積から、開閉ピストン８５が一次圧力室６４および減圧背圧力室５５内の流体によって軸線方向他方Ｘ２に一次圧Ｐ１を受ける受圧面積を減算した面積であって、一次圧力室６４および減圧背圧力室５５内の流体から受ける一次圧Ｐ１が、開閉ピストン８５に軸線方向一方Ｘ１への力として有効的に働く面積である。本実施の形態では、軸部８８の減圧背圧力室５５に臨む軸線方向一端部１０１の装置軸線Ｌ１に垂直な断面の直径Ｄ４は、弁座１１２の先端部の外径Ｄ１と同一に形成されている。したがって、開閉ピストン８５は、開閉弁部が開いているか閉じているかに拘わらず、また開閉弁体８７と軸体８８とが当接しているか離間しているかに拘わらず、閉受圧面積Ａ１は、弁座１１２の先端部の外径Ｄ１と同一の外径の円の面積となり、次式（３）で表される。
【００６１】
【数２】

【００６２】
ここで軸体８８の軸線方向一端部１０１における装置軸線Ｌ１に垂直な断面の面積Ａ４は、次式（４）で表され、閉受圧面積Ａ１と同一である。
【００６３】
【数３】

【００６４】
また開閉ピストン８５は、前述のように軸体８８に段差部１０５が形成され、この段差部１０５が開閉背圧力室１０６に設けられるように構成される。これによって開閉ピストン８５は、開閉ピストン８５を弁座１１２から離間方向の一次圧Ｐ１を、有効的に受ける開受圧面積Ａ７−Ａ８の開受圧面１３１を有する。開受圧面積Ａ７−Ａ８は、開閉ピストン８５が開閉背圧力室１０５内の流体によって軸線方向他方Ｘ２に一次圧Ｐ１を受ける受圧面積から、開閉ピストン８５が開閉背圧力室１０６内の流体によって軸線方向一方Ｘ１に一次圧Ｐ１を受ける受圧面積を減算した面積であって、開閉背圧力室１０６内の流体から受ける一次圧Ｐ１が、開閉ピストン８５に軸線方向他方Ｘ２への力として有効的に働く面積である。
【００６５】
本実施の形態では、軸体８８の段差部１０５に、開受圧面１３１が形成されており、段差部１０５における軸線方向一端部１０１側の外径が大きい部分の装置軸線Ｌ１に垂直な断面の面積Ａ７から、段差部１０５における軸線方向他端部１０２側の外径が小さい部分の装置軸線Ｌ１に垂直な断面の面積Ａ８を減算した面積である。したがって、開受圧面積Ａ７−Ａ８は、段差部１０５における軸線方向一端部１０１側の外径が大きい部分の外径Ｄ７と、段差部１０５における軸線方向他端部１０２側の外径が小さい部分の外径Ｄ８とを用いて、次式（５）で表される。
【００６６】
【数４】

【００６７】
本実施の形態では、開受圧面積Ａ７−Ａ８は、閉受圧面積Ａ１（＝Ａ４）と同一である。開閉ピストン８５は、二次圧Ｐ２に保持される二次圧力室７０には臨んでおらず、二次圧Ｐ２は受けない。
【００６８】
開閉ピストン８５には、大気圧も働くが、開閉ピストン８５の動作に与える影響が小さいので、便宜上、大気圧による力を無視すると、開閉ピストン８５に働く軸線方向の力Ｆ１は、軸線方向一方Ｘ１の力を正として、次式（６）のように表される。
Ｆ１＝Ｆｋ＋｛Ａ１−（Ａ７−Ａ８）｝Ｐ１−Ｆｓ …（６）
Ｆｋ＝Ｋ１(ΔＨ１＋Ｚ１) …（７）
【００６９】
ここで、Ｆｋは、駆動ばね部材８９によるばね力であって、Ｋ１は、駆動ばね部材８９のばね定数であり、ΔＨ１は、開閉弁体８７が閉位置にある場合の駆動ばね部材８９の自然状態からの撓み量であり、Ｚ１は、開閉弁体８７の閉位置からの軸線方向一方Ｘ１への変位量である。Ｆｓは、電磁ソレノイド９０による電磁力である。
【００７０】
本実施の形態の開閉弁部では、上式（６）において、開閉背圧力室１０６を形成して、開閉ピストン８５が一次圧Ｐ１を開受圧面積Ａ７−Ａ８で、軸線方向他方Ｘ２に受けるように構成し、これによって開閉ピストン８５が軸線方向一方Ｘ１に受ける一次圧Ｐ１による力（Ａ１×Ｐ１）と、開閉ピストン８５が軸線方向他方Ｘ２に受ける一次圧Ｐ１による力｛（Ａ７−Ａ８）×Ｐ１｝とを釣り合わせて、開閉ピストン８５に働く一次圧Ｐ１による軸線方向の力を相殺すること、つまり｛Ａ１−（Ａ７−Ａ８）｝Ｐ１＝０にすることができる。
【００７１】
従来の構成では、一次圧を高くすると、安定して開閉ピストンを弁座に着座させるために、その一次圧によって開閉ピストンに働く力に抗するような大きさのばね力を開閉ピストンに与えるばね力の大きな駆動ばね部材を用いる必要があり、開閉ピストンを弁座から離間するときには、このような大きなばね力に抗する大きな電磁力を与えることができるように電磁ソレノイドを大形化しなければならない。これに対して、本実施の形態の弁装置２０における開閉弁部では、開閉ピストン８５に働く一次圧Ｐ１による軸線方向の力が相殺されるので、一次圧Ｐ１を高くしても、安定して開閉ピストン８５の開閉シート部９９を弁座１１２に着座させて閉じるために、駆動ばね部材８９のばね力を大きくする必要がない。これに伴って、開閉ピストン８５の開閉シート部９９を弁座１１２から離間させて開くために、電磁ソレノイド９０が開閉ピストン８５に与える電磁力を大きくする必要がなく、電磁ソレノイド９０を小形化することができ、開閉弁部の寸法を小さく抑えることができる。
【００７２】
また流量キャパシティ、すなわち最大許容流量を大きくするために、一次圧Ｐ１を受ける閉受圧面積Ａ１を大きくしても、開閉ピストン８５に働く一次圧Ｐ１による軸線方向の力を相殺して、駆動ばね部材８９が一次ポート２８と二次ポート３０とを閉塞するために開閉ピストン８５に与えるばね力を小さくすることができる。これによって電磁ソレノイド９０が一次ポート２８と二次ポート３０とを開放するために開閉ピストン８５に与える電磁力を大きくすることがない。
【００７３】
また減圧ピストン２２は、一次圧力室６４の流体から軸線方向一方Ｘ１に向かう一次圧Ｐ１を、有効的に受ける一次受圧面積Ａ２の一次受圧面７５を有する。一次受圧面積Ａ２は、減圧ピストン２２が一次圧力室６４内の流体によって軸線方向一方Ｘ１に一次圧Ｐ１を受ける受圧面積から、減圧ピストン２２が一次圧力室６４内の流体によって軸線方向他方Ｘ２に一次圧Ｐ１を受ける受圧面積を減算した面積であって、一次圧力室６４内の流体から受ける一次圧Ｐ１が、減圧ピストン２２を軸線方向一方Ｘ１への力として有効的に働く面積である。
【００７４】
減圧ピストン２２は、一次圧力室６４に軸線方向一方Ｘ１側からだけ臨んでおり、一次圧力室６４の流体から軸線方向一方Ｘ１にだけ一次圧Ｐ１を受ける。一次受圧面積Ａ２は、減圧シート部６２と協働してオリフィス６３を形成する突起片３８の先端部の直径Ｄ２と、減圧ピストン２２に形成される透孔７１の直径Ｄ１０とを用いて、次式（８）で表される。
【００７５】
【数５】

【００７６】
また減圧背圧力室５５は、上述のように減圧ピストン２２内に筒状部材２４の軸線方向一端部４８が挿入されることによって形成されており、減圧ピストン２２は、減圧背圧力室５５内の流体から軸線方向他方Ｘ２に向かう一次圧Ｐ１を、有効的に受ける背受圧面積Ａ３の背受圧面７６を有する。背受圧面積Ａ３は、減圧ピストン２２が減圧背圧力室５５内の流体から軸線方向他方Ｘ２に一次圧Ｐ１を受ける受圧面積から、減圧ピストン２２が減圧背圧力室５５内の流体から軸線方向一方Ｘ１に一次圧Ｐ１を受ける受圧面積を減算した面積であって、減圧背圧力室５５内の流体から受ける一次圧Ｐ１が、減圧ピストン２２を軸線方向他方Ｘ２への力として有効的に働く面積である。この背受圧面積Ａ３は、筒状部材２４の軸線方向一端部４８の外径Ｄ３と、減圧ピストン２２に形成される透孔７１の直径Ｄ１０とを用いて、次式（９）で表される。
【００７７】
【数６】

【００７８】
突起片３８の先端部の直径Ｄ２と、筒状部材２４の軸線方向一端部４８の外径Ｄ３は、同一であって、したがって一次受圧面積Ａ２と有効背受圧面積Ａ３とは同一である。このように減圧ピストン２２は、一次圧力室６４内の流体から一次圧Ｐ１を軸線方向一方Ｘ１に受ける一次受圧面７５の一次受圧面積Ａ２と同一の有効背受圧面積Ａ３とを有し、減圧背圧力室５５内の流体から軸線方向他方Ｘ２に向かう一次圧Ｐ１を受ける背受圧面７６を有する。
【００７９】
また減圧ピストン２２は二次圧力室７０内の流体から軸線方向他方Ｘ２に向かう二次圧Ｐ２を有効的に受ける受圧面積Ａ６−Ａ５の二次受圧面８０を有する。減圧ピストン２２が二次圧力室７０内の流体から軸線方向他方Ｘ２に二次圧Ｐ２を受ける受圧面積Ａ６は、減圧ピストン２２の第２空間６１に臨む部分の最大外径である外向き凸部４１の外径Ｄ６を直径とする円の面積から筒状部材２４の軸線方向一端部４８の装置軸線Ｌ１に垂直な断面の面積（＝（π／４）Ｄ３^２）を減算した面積であって、次式（１０）で表される。
【００８０】
【数７】

【００８１】
また減圧ピストン２２が二次圧力室７０内の流体から軸線方向一方Ｘ１に二次圧Ｐ２を受ける受圧面積Ａ５は、減圧ピストン２２の外側空間部６５に臨む部分の最大外径Ｄ５を直径とする円の面積から突起片３８の先端部の直径Ｄ２と同一直径の円の面積を減算した面積であって、次式（１１）で表される。
【００８２】
【数８】

【００８３】
図３は、弁装置２０の二次圧Ｐ２を示すグラフであって、図３（１）は、一次圧Ｐ１と二次圧Ｐ２との関係を示し、図３（２）は、流量Ｑと二次圧Ｐ２との関係を示す。弁装置２０では、減圧ピストン２２に働く力の釣り合いは、次式（１２）によって表される。
【００８４】
【数９】

【００８５】
ここで、Ｋ２は、減圧ばね部材２３のばね定数であり、ΔＨは、図１に示される減圧ばね部材２３の初期状態での自然状態からの撓み量である。この初期状態は、たとえば減圧ピストン２２が最も軸線方向一方Ｘ１に配置され、筒状部材２４によって軸線方向に支持されている状態である。またＺ２は、減圧ピストン２２の図１に示される初期状態からの軸線方向他方Ｘ２への変位量であって、式（１３）で表されるように、一次圧Ｐ１と、弁装置２０を流下する流体の流量Ｑとの関数で表される。
【００８６】
前記式（１２）の釣り合いの式から、二次圧Ｐ２は、次式（１４）のように表される。
【００８７】
【数１０】

【００８８】
本実施の形態の弁装置２０では、上述のように減圧背圧力室５５を形成して、減圧ピストン２２が一次圧Ｐ１を背受圧面積Ａ３で、軸線方向他方Ｘ２に受けるように構成し、これによって減圧ピストン２２が軸線方向一方Ｘ１に受ける一次圧Ｐ１による力と、減圧ピストン２２が軸線方向他方Ｘ２に受ける一次圧Ｐ１による力とを釣り合わせて、相殺することができる。つまり一次受圧面積Ａ２と背受圧面積Ａ３を同一とし、上式（１４）における右辺第二項の分子を零にする（Ａ２−Ａ３＝０）ことができ、一次圧Ｐ１が変化しても、式（１４）における右辺第二項の値を一定値（＝０）として、右辺第一項だけが変化する式（Ｐ２＝ε）となるようにすることができる。したがって図３（１）に示すように、減圧ピストン２２に背受圧面７６を形成しない、従来の構成に比べて、一次圧Ｐ１の変化量ΔＰ１に対する二次圧Ｐ２の変化量ΔＰ２を大幅に低減することができる。
【００８９】
また弁装置２０では、流量キャパシティ、すなわち最大許容流量を大きくするために、突起片３８の先端部の直径Ｄ１を大きくして、一次受圧面積Ａ２が大きくなっても、背受圧面積Ａ３を大きくすれば、一次圧Ｐ１の変化量ΔＰ１に対する二次圧Ｐ２の変化量ΔＰ２を小さく抑えることができる。したがって最大許容流量を大きくするために、減圧ピストン２２に背受圧面７６を形成しない場合のように、減圧ピストン２２の二次圧Ｐ２を軸線方向他方Ｘ２に受ける受圧面積Ａ６を大きくする必要がなく、減圧ピストン２２の最大外径である外向き凸部４１の外径Ｄ６を大きくする必要がない。したがって弁装置２０の半径方向寸法を小さく抑えることができる。このように流量Ｑに拘わらず、弁装置２０の半径方向寸法を小さく抑えた上、一次圧Ｐ１の変化量ΔＰ１に対する二次圧Ｐ２の変化量ΔＰ２を小さく抑えることができる。
【００９０】
また筒状部材２４を設けて、減圧ピストン２２内に部分的に挿入する構成とすることによって、簡単な構成によって、減圧背圧力室５５を形成し、上述の効果が得られる弁装置２０を容易に実現することができる。さらに減圧ピストン２２と筒状部材２４との間のピストン内空間５６を流体が流下する通路として利用することによって、減圧ピストン２２に第１空間６０の外側空間部６５と第２空間６１とを連通するための軸線方向に延びる通路を穿設する必要がなく、構成が簡単であり、複雑な加工を必要としないので、容易に製造することができる。また通路の穿設に伴う減圧ピストン２２の強度低下がないので、減圧ピストン２２の肉厚（半径方向寸法）を小さく抑えることができ、これによっても、弁装置２０の半径方向寸法を小さくすることができる。もちろん減圧ピストン２２に外側空間部６５と第２空間６１とを連通するための軸線方向に延びる通路を穿設する構成も、本発明に含まれることは言うまでもない。
【００９１】
また一次ポート２８と二次ポート３０との接続状態を切換える開閉弁部と、二次圧Ｐ２を一次圧Ｐ１よりも減少させる減圧弁部とが、相互に、少なくとも一部の構成が流体の流下方向に重複する位置に配置されて設けられる。本実施の形態では、開閉弁部が減圧弁部を挿通するように構成される。これによって開閉弁部と減圧弁部とを単に縦列して設ける場合に比べて、流下方向、具体的には軸線方向の寸法を小さくすることができる。しかも開閉弁部と減圧弁部とは、同軸に設けられており、開閉弁部と減圧弁部とが部分的に重複する領域では、ハウジング２１を共用することができ、開閉弁部と減圧弁部とを単に並列して設ける場合に比べて、流下方向に交差する方向、具体的には半径方向の寸法を小さくすることができる。このように軸線方向寸法および半径方向寸法を小さくして、小形の弁装置２０を実現することができる。
【００９２】
したがって圧力装置、圧力容器および圧力配管などへの装着が容易になるうえ、取扱も容易になる。また小形にすることによって、外部から振動が与えられても大きく振動することがなく、耐振性を高くすることができ、たとえば可搬形の圧力装置および圧力容器に好適に用いることができる。また小形にすることによって、高圧容器に設ける場合に、高圧容器に容易に内蔵することが可能になり、高圧容器の外部に高圧流体が流下する配管を設ける必要がなく、高い安全性および取扱性を達成することができる。たとえば高圧タンクなどの高圧容器に減圧弁を内蔵して用いる場合、高圧容器の強度の観点から高圧容器の外径を小さく抑える必要があり、このような用途には、特に効果を発揮して、好適に用いることができる。また全体の質量を小さくすることができ、これによっても取扱性を容易にすることができる。また前述のような一体化構造によって、弁装置２０の部品点数を少なくすることができ、製造コストを低くすることができる。
【００９３】
さらに開閉弁部における流路の開閉位置が、減圧弁部における減圧位置に比べて、流体の流下方向上流側に配置されている。これによって開閉弁部が閉じた状態では、減圧弁部に高圧の一次圧力が働くことがなく、耐久性を高くすることができる。また開閉弁部を通過した流体は、必ず減圧弁部で減圧されることになり、開閉弁部を閉じた状態で長時間放置した後に、開閉弁部を開放しても、二次圧力Ｐ２は、一次圧力に比べて減圧されている。このように高圧のガスが吐出されてしまうことが防がれる。
【００９４】
また本実施の形態では、突起片３８が形成されるキャップ部材２７を、ハウジング本体２５に対する軸線方向に位置を調節できるので、突起片３８と減圧ピストン２２の減圧シート部６２との軸線方向間隔を調節することができ、一次圧Ｐ１に対する二次圧Ｐ２の減圧比を調節することができる。
【００９５】
このような弁装置２０は、たとえば消防士が火災現場などで背負う酸素を収容したタンクなどの高圧タンクに設け、高圧タンク内の酸素を、減圧しながら外部に吐出するための減圧弁として用いることができる。このような高圧タンクに内蔵化して用いる場合、高圧タンクは、強度の観点から半径方向寸法を小さくする必要があり、上述のように半径方向寸法を小さく抑えることができる弁装置２０は、好適である。
【００９６】
また開閉弁部における開閉ピストン８５を、開閉弁体８７と軸体８８とを分離して構成し、開閉弁体８７を軸体８８を介して電磁ソレノイド９０によって遠隔駆動する。これによって電磁ソレノイド９０の構成部品には、高圧の流体が働くことがなく、電磁ソレノイド９０のチューブ（ケーシング）を堅牢に形成する必要がない。また電磁ソレノイド９０の加工精度を高くしなくても、流体の漏れを防ぐシール性を高くすることができる。
【００９７】
図４は、本発明の実施の他の形態の弁装置２０Ａを示す断面図である。本実施の形態の弁装置２０Ａは、図１〜図３に示す実施の形態の弁装置２０と類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ａは、開閉弁部を手動で開閉操作するための操作ハンドル１４０をさらに有する。この操作ハンドル１４０は、電磁ソレノイド９０のケーシングに螺着され、回動させて螺進および螺退させることによって、駆動部材１２０を変位操作することができる。これによって操作ハンドル１４０を手動操作することによって、駆動ばね部材８９と協働して、開閉ピストン８５を変位駆動することができる。
【００９８】
このような弁装置２０Ａは、図１〜３の弁装置２０の効果に加えて、手動で開閉弁部を操作できる効果を達成することができる。このように手動で開閉弁部を操作できるようにすれば、電磁ソレノイド９０が何らかの要因で電気的に作動させることができない事態が生じても、開閉弁部を作動させることができる。
【００９９】
図５は、本発明の実施のさらに他の形態の弁装置２０Ｂを示す断面図である。本実施の形態の弁装置２０Ｂは、図１〜図３に示す実施の形態の弁装置２０と類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ｂは、開閉弁部に関して、開閉背圧力室１０６を形成しない構成である。このような構成では、開閉ピストン８５に、一次圧Ｐ１による軸線方向一方Ｘ１に働く力を、前述のようにして相殺（キャンセル）することはできないが、開閉背圧力室１０６および連通路１０７を設ける必要がなく、また開閉ピストン８５に段差部１０５を形成する必要がないので、構成を簡単にすることができる。この弁装置２０Ｂは、開閉ピストン８５に、一次圧Ｐ１による軸線方向一方Ｘ１に働く力を、前述のようにして相殺すること以外の効果については、図１〜図３の弁装置２０と同様に達成することができる。
【０１００】
図６は、本発明の実施のさらに他の形態の弁装置２０Ｃを示す断面図である。本実施の形態の弁装置２０Ｃは、図５に示す実施の形態の弁装置２０Ｂと類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ｃは、図５の弁装置２０Ｂの構成に加えて、図４に示す弁装置２０Ａと同様の操作ハンドル１４０が設けられる。これによって、図５の弁装置２０Ｂの効果に加えて、図４の弁装置２０Ａで説明した操作ハンドル１４の効果を同様に達成することができる。
【０１０１】
図７は、本発明の実施のさらに他の形態の弁装置２０Ｄを示す断面図である。本実施の形態の弁装置２０Ｄは、図４に示す実施の形態の弁装置２０Ａと類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ｄは、図４の弁装置２０Ａの構成において、電磁ソレノイド９０を取り除いた構成であり、換言すれば、図１〜図３の弁装置２０の構成において電磁ソレノイド９０に代えて、操作ハンドル１４０を設けた構成であり，操作ハンドル１４０は、ハウジング２１に螺着される。この弁装置２０Ｄでは、操作ハンドル１４０の操作によって、駆動永久磁石片を介することなく、開閉ピストン８５を直接操作することができる。その他の構成については、図４の弁装置２０Ａと同様であり、電磁ソレノイド９０に関連する効果以外の効果については、図４の弁装置２０Ａと同様に達成することができる。
【０１０２】
図８は、本発明の実施のさらに他の形態の弁装置２０Ｅを示す断面図である。本実施の形態の弁装置２０Ｅは、図５に示す実施の形態の弁装置２０Ｂと類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ｅは、図５の弁装置２０Ｂの構成において、図７の弁装置２０Ｄと同様に、電磁ソレノイド９０を取り除いた構成である。その他の構成については、図５の弁装置２０Ｂと同様であり、電磁ソレノイド９０に関連する効果以外の効果については、図５の弁装置２０Ｂと同様に達成することができる。
【０１０３】
図９は、タンク２００に設けられるタンク内蔵型の弁装置の分類の一例を示す図である。タンク内蔵型の弁装置２０，２０Ａ〜２０Ｅは、電磁式と手動式とに大別される。電磁式および手動式ともに、圧力キャンセル機構付と圧力キャンセル機構無とにさらに別けることができる。また電磁式では、圧力キャンセル機構付および圧力キャンセル機構無ともに、応急手動ハンドル付と応急手動ハンドル無とに別けられる。
【０１０４】
図１〜図３の弁装置２０が、電磁式であって圧力キャンセル機構付の応急手動ハンドル無の弁装置に相当する。図４の弁装置２０Ａが、電磁式であって圧力キャンセル機構付の応急手動ハンドル付の弁装置に相当する。図５の弁装置２０Ｂが、電磁式であって圧力キャンセル機構無の応急手動ハンドル無の弁装置に相当する。図６の弁装置２０Ｃが、電磁式であって圧力キャンセル機構無の応急手動ハンドル付の弁装置に相当する。図７の弁装置２０Ｄが、手動式であって圧力キャンセル機構付の弁装置に相当する。図８の弁装置２０Ｅが、手動式であって圧力キャンセル機構無の弁装置に相当する。
【０１０５】
図１０は、配管１５０の途中に設けられるインライン型の弁装置の分類の一例を示す図である。図１〜図９を参照して説明した各弁装置２０，２０Ａ〜２０Ｅは、タンク８０に設けられたけれども、弁装置は、配管途中に設けるようにしてもよい。インライン型の弁装置２０Ｆ〜２０Ｋもまた、電磁式と手動式とに大別される。電磁式および手動式ともに、圧力キャンセル機構付と圧力キャンセル機構無とにさらに別けることができる。また電磁式では、圧力キャンセル機構付および圧力キャンセル機構無ともに、応急手動ハンドル付と応急手動ハンドル無とに別けられる。
【０１０６】
図１１の弁装置２０Ｆが、電磁式であって圧力キャンセル機構付の応急手動ハンドル無の弁装置に相当する。図１２の弁装置２０Ｇが、電磁式であって圧力キャンセル機構付の応急手動ハンドル付の弁装置に相当する。図１３の弁装置２０Ｈが、電磁式であって圧力キャンセル機構無の応急手動ハンドル無の弁装置に相当する。図１４の弁装置２０Ｉが、電磁式であって圧力キャンセル機構無の応急手動ハンドル付の弁装置に相当する。図１５の弁装置２０Ｊが、手動式であって圧力キャンセル機構付の弁装置に相当する。図１６の弁装置２０Ｋが、手動式であって圧力キャンセル機構無の弁装置に相当する。このようなインライン型の弁装置であて、圧力キャンセル機構付の弁装置において、開閉弁部における一次圧Ｐ１を相殺するために、開閉背圧力室１０６に一次圧Ｐ１を導くためのハウジング本体２５の連通路１０７は、弁体室９７と開閉背圧力室１０６とを接続するように構成される。
【０１０７】
これらインライン型の各弁装置２０Ｆ〜２０Ｋは、タンク２００に設けられず、配管途中に設けられ、一次ポート２８に配管１５０の一次側部分が連結され、二次ポート３０に配管１５０の二次側部分が連結される。インライン型の各弁装置２０Ｆ〜２０Ｋは、その他の構成については、対応する分類のタンク内蔵型の各弁装置２０，２０Ａ〜２０Ｅと同様の構成であり、同様の効果を達成することができる。
【０１０８】
図１７は、本発明の実施の他の形態の弁装置２０Ｌを示す断面図である。本実施の形態の弁装置２０Ｌは、図１〜図３に示す実施の形態の弁装置２０と類似しており、同一の構成は、同一の符号を付して説明を省略し、異なる構成についてだけ説明する。本実施の形態の弁装置２０Ｌは、図１〜図３の弁装置２０の電磁ソレノイド９０に代えて、装置軸線Ｌ１上ではなく、装置軸線Ｌ１に対して交差する方向から駆動する電磁ソレノイド９０Ｌが設けられる。
【０１０９】
この弁装置２０Ｌでは、ハウジング２１の軸線方向他端部に、軸体８８の軸線方向他端部１０１が配置される作動片収容部１６０が形成され、Ｌ字状の作動片１６１が収容されている。作動片１６１は、一端部で装置軸線Ｌ１に垂直な角変位軸線Ｌ２まわりに角変位自在に保持されている。
【０１１０】
電磁ソレノイド９０Ｌは、ハウジング２１の外方に配置されて、外周部に設けられ、装置軸線Ｌ１と交差する方向、具体的には装置軸線Ｌ１に垂直であり、かつ角変位軸線Ｌ２に垂直なソレノイド軸線に沿って変位自在な駆動部材１６４と、駆動コイルとを有する。この電磁ソレノイド９０Ｌは、駆動コイルへの通電および非通電を切換えることによって、駆動部材１６４をソレノイド軸線に沿って変位させ、この駆動部材１６４によって、作動片１６１を角変位させ、この作動片１６１によって押圧して、ハウジング２１に対して、装置軸線Ｌ１に沿って軸線方向へ、具体的には軸線方向他方Ｘ２に向かう方向へ変位駆動するための電磁駆動力であって弁体部９５を弁座１１２から離間させる開方向の電磁駆動力力を、開閉ピストン８５に与えることができる。
【０１１１】
このような構成では、電磁ソレノイド９０Ｌを半径方向にずらすことによって、装置軸線Ｌ１の方向の寸法をさらに小さくすることができる。また駆動部材１６４による作動片１６１への入力位置（力点）と作動片１６１の角変位軸線（支点）との距離が、作動片１６１によって軸体８８を押圧する押圧位置（作用点）と作動片１６１の角変位軸線との距離よりも大きい。これによっててこの原理によって、電磁ソレノイド９０Ｌの電磁力を増幅させて軸体８８に与えることができる。これによって電磁ソレノイド９０Ｌをさらに小形にすることができる。
【０１１２】
図１７に示す弁装置２０Ｌのその他の構成は、図１〜図３の弁装置２０と同様であり、同様の効果を達成する。
【０１１３】
上述の実施の形態は、本発明の例示に過ぎず、本発明の範囲内で構成を変更することができる。たとえば図４、図５、図６、図１１、図１２、図１３および図１４に示す弁装置２０Ａ，２０Ｂ，２０Ｃ，２０Ｆ，２０Ｇ，２０Ｈ，２０Ｉにおいて、電磁ソレノイド９０を、図１７に示す電磁ソレノイド９０Ｌに代えるようにしてもよい。またハウジング２１と筒状部材２４とは一体に形成されてもよい。また用途は、上述の消防士が背負うタンク以外の高圧タンクに設けてもよく、たとえば電気自動車などに搭載される燃料電池を構成するためのガスを収容するタンクに設けるようにしてもよい。またタンク以外の流体圧装置に設けるようにしてもよい。流体は、気体であってもよいし、液体であってもよい。
【０１１４】
【発明の効果】
請求項１記載の本発明によれば、軸線方向寸法および半径方向寸法を小さくして、小形の弁装置を実現することができるので、圧力装置、圧力容器および圧力配管などへの装着が容易になるうえ、取扱も容易になる。また小形にすることによって、外部から振動が与えられても大きく振動することがなく、耐振性を高くすることができ、たとえば可搬形の圧力装置および圧力容器に好適に用いることができる。また小形にすることによって、高圧容器に設ける場合に、高圧容器に容易に内蔵することが可能になり、高圧容器の外部に高圧流体が流下する配管を設ける必要がなく、高い安全性および取扱性を達成することができる。たとえば高圧タンクなどの高圧容器に減圧弁を内蔵して用いる場合、高圧容器の強度の観点から高圧容器の外径を小さく抑える必要があり、このような用途には、特に効果を発揮して、好適に用いることができる。また全体の質量を小さくすることができ、これによっても取扱性を容易にすることができる。また前述のような一体化構造によって、弁装置の部品点数を少なくすることができ、製造コストを低くすることができる。
【０１１５】
請求項２記載の本発明によれば、一次圧力の変化量に対する二次圧力の変化量を、大幅に低減することができる。しかも最大許容流量が大きい場合であっても、半径方向寸法を小さく抑えかつ二次圧力の変化量を小さく抑えることができる。したがって極めて利便性の高い減圧弁部を備える弁装置が得られる。
【０１１６】
請求項３記載の本発明によれば、一次圧力を高くしても、開閉駆動手段によって開閉ピストンに与える駆動力を大きくする必要がない。また開閉駆動手段よって開閉ピストンに与える駆動力を大きくすることなく、最大許容流量を大きくすることができる。したがって極めて利便性の高い開閉弁部を備える弁装置が得られる。
【０１１７】
請求項４記載の本発明によれば、開閉弁部が閉じた状態では、減圧弁部に高圧の一次圧力が働くことがなく、耐久性を高くすることができる。また開閉弁部を閉じた状態で長時間放置した後に、開閉弁部を開放しても、高圧のガスが吐出されてしまうことが防がれる。
【図面の簡単な説明】
【図１】本発明の実施の一形態の弁装置２０を示す断面図である。
【図２】弁装置２０の各部の寸法を説明するために示す断面図である。
【図３】弁装置２０の二次圧Ｐ２を示すグラフである。
【図４】本発明の実施の他の形態の弁装置２０Ａを示す断面図である。
【図５】本発明の実施のさらに他の形態の弁装置２０Ｂを示す断面図である。
【図６】本発明の実施のさらに他の形態の弁装置２０Ｃを示す断面図である。
【図７】本発明の実施のさらに他の形態の弁装置２０Ｄを示す断面図である。
【図８】本発明の実施のさらに他の形態の弁装置２０Ｅを示す断面図である。
【図９】タンク８０に設けられるタンク内蔵型の弁装置の分類の一例を示す図である。
【図１０】配管１５０途中に設けられるインライン型の弁装置の分類の一例を示す図である。
【図１１】本発明の実施のさらに他の形態の弁装置２０Ｆを示す断面図である。
【図１２】本発明の実施のさらに他の形態の弁装置２０Ｇを示す断面図である。
【図１３】本発明の実施のさらに他の形態の弁装置２０Ｈを示す断面図である。
【図１４】本発明の実施のさらに他の形態の弁装置２０Ｉを示す断面図である。
【図１５】本発明の実施のさらに他の形態の弁装置２０Ｊを示す断面図である。
【図１６】本発明の実施のさらに他の形態の弁装置２０Ｋを示す断面図である。
【図１７】本発明の実施のさらに他の形態の弁装置２０Ｌを示す断面図である。
【図１８】従来の技術の弁装置１を示す断面図である。
【図１９】弁装置１を示す構成回路図である。
【図２０】従来の技術の減圧弁部３の構成を簡略化して模式的に示す断面図である。
【図２１】従来技術の減圧弁部３の二次圧力ｐ２を示すグラフである。
【符号の説明】
２０，２０Ａ〜２０Ｌ弁装置
２１ハウジング
２２減圧ピストン
２３減圧ばね部材
２４筒状部材
２８一次ポート
３０二次ポート
５５減圧背圧力室
６３オリフィス
８５開閉ピストン
８６開閉駆動手段
１０６開閉背圧力室[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve device provided in, for example, a fluid pressure device.
[0002]
[Prior art]
FIG. 18 is a cross-sectional view showing a conventional valve device 1. FIG. 19 is a configuration circuit diagram showing the valve device 1. The valve device 1 is a regulator device provided in a tank 2 of a natural gas vehicle, and is shown in US Pat. No. 6,041,762. The valve device 1 includes a pressure reducing valve portion 3 for reducing the pressure of the gas in the tank 2 and discharging the gas to the outside of the tank 2, an on-off valve portion 4 for discharging and stopping the discharge of the gas in the tank 2, and a safety valve portion for emergency opening. 5, the pressure reducing valve portion 3 is provided in the tank 2, and the on-off valve portion 4 and the safety valve portion 5 are provided outside the tank 2. A detection sensor 6 for detecting the pressure and temperature for operating the safety valve unit 5 is provided outside the tank 2. The on-off valve portion 4 is provided on the downstream side of the pressure reducing valve portion 3.
[0003]
FIG. 20 is a cross-sectional view schematically showing the configuration of the pressure reducing valve portion 3 of the prior art in a simplified manner. The pressure-reducing valve portion 3 is configured such that a piston 8 is held in a housing 7 so as to be displaceable in an axial direction, and a spring member 9 is provided to apply a spring force to the piston 8 toward one axial direction x1. The housing 7 is formed with a primary port 10 and a secondary port 11, and a protruding piece 12 is formed surrounding the primary port 10, and the protruding piece 12 and the seat portion 13 of the piston 8 facing the protruding piece 12, An orifice 14 for pressure reduction is formed. In this way, the inside of the housing 7 is partitioned into a primary pressure chamber 15 that is continuous with the primary port 10 and a secondary pressure chamber 16 that is continuous with the secondary port 11. The pressure reducing valve unit 3 reduces the fluid of the primary pressure (hereinafter referred to as “primary pressure”) p1 supplied to the primary port 10 to the secondary pressure (hereinafter referred to as “secondary pressure”) p2 by passing through the orifice 14. , And can be discharged from the secondary port 11.
[0004]
[Problems to be solved by the invention]
In the valve device 1, since the pressure reducing valve portion 3 and the on-off valve portion 4 are provided in tandem in the gas flow direction, the valve device 1 is increased in size. Further, in the configuration in which the on-off valve portion 4 is provided on the downstream side of the pressure reducing valve portion 3, when the on-off valve portion 4 is left closed for a long time, the secondary pressure of the pressure reducing valve portion 3 is the same as the primary pressure. In this case, high-pressure gas is discharged immediately after opening the on-off valve portion 4.
[0005]
FIG. 21 is a graph showing the secondary pressure p2 of the pressure reducing valve portion 3 of the prior art. In the pressure-reducing valve unit 3, the secondary pressure p2 is expressed by the following equation (1) using the primary pressure p1.
[0006]
[Expression 1]

[0007]
Here, a1 is a pressure receiving area that receives the primary pressure p1 in one axial direction x1, a2 is a pressure receiving area that receives the secondary pressure p2 in one axial direction x1, and a3 is a secondary in the other axial direction x2. The pressure receiving area that receives the pressure p2. K is a spring constant of the spring member 9, and Δh is a deflection amount of the spring member 9 in an initial state. Z is the amount of displacement of the piston 3 from the initial state, and is expressed as a function of the primary pressure p1 and the flow rate q of the fluid flowing down the pressure reducing valve section 3, as represented by the equation (2). The
[0008]
In the pressure reducing valve portion 3, the piston 8 is configured to receive the primary pressure p1 only on one side x1 in the axial direction on the pressure receiving surface of the area a1, and the expression (1) representing the secondary pressure p2 is expressed by the first term and the second term on the right side. Both terms are equations that change as the primary pressure p1 changes. In particular, the second term on the right side of Equation (1) is a term that changes greatly with changes in the primary pressure p1. Therefore, as shown in FIG. 21, when the primary pressure p1 changes, the secondary pressure p2 changes greatly.
[0009]
Further, in order to increase the flow capacity of the pressure reducing valve portion 3, that is, the maximum allowable flow rate, it is necessary to increase the diameter of the protruding piece 12. When the diameter of the protruding piece 12 is increased, the pressure receiving area a1 is increased, and the change amount Δp2 of the secondary pressure p2 with respect to the change amount Δp1 of the primary pressure p1 is increased. In order to suppress the amount of change Δp2 of the secondary pressure p2 to be small, it is necessary to increase the pressure receiving area a3 in order to increase the denominator of the second term on the right side of Equation (1), and the maximum outer diameter of the piston 8 is growing. Along with this, the spring member 9 also needs to have a larger outer diameter. Accordingly, the radial dimension of the pressure reducing valve portion 3 is increased.
[0010]
Although the pressure reducing valve portion 3 has been specifically described, in the open / close valve portion 4 as well as the pressure reducing valve portion 3, the radial dimension of the open / close valve portion 4 increases when the maximum allowable flow rate is increased.
[0011]
The objective of this invention is providing the valve apparatus which can suppress the dimension of a radial direction small.
[0012]
Moreover, the objective of this invention is providing the valve apparatus which can suppress the change of the secondary pressure accompanying the change of the primary pressure small in a pressure-reduction valve part.
[0013]
Another object of the present invention is to provide a valve device that can increase durability and prevent discharge of high-pressure fluid even if the on-off valve portion is opened after the on-off valve portion is closed and left for a long period of time. Is to provide.
[0014]
[Means for Solving the Problems]
 The present invention according to claim 1 includes a housing in which a primary port and a secondary port are formed;
 Provided in the housing,A pressure reducing valve portion for reducing the secondary pressure of the fluid in the secondary port to be lower than the primary pressure in the primary port;
 It is provided by inserting the pressure reducing valve part coaxially,Connection status between primary port and secondary portOpenOpen / close valve that switches between the closed state and the closed stateAndIt is a valve apparatus characterized by including.
[0015]
 According to the present invention, the on-off valve portion that switches the connection state between the primary port and the secondary portBut,Secondary pressure is greater than primary pressureDecompressionPressure reducing valveThroughProvided. Compared to the case where the on-off valve part and the pressure reducing valve part are simply provided in cascade in this way,axisThe dimension in the line direction can be reduced. Moreover, the on-off valve part and the pressure reducing valve part are provided coaxially, and the on-off valve partButPressure reducing valveThe part to be insertedThen, the housing can be shared, compared to the case where the on-off valve part and the pressure reducing valve part are simply provided in parallel.HalfThe dimension in the radial direction can be reduced. Thus, a small valve device can be realized by reducing the axial dimension and the radial dimension.
[0016]
In the present invention according to claim 2, the pressure reducing valve portion is
The housing is slidably held in the axial direction, and the housing is partitioned into a primary pressure chamber connected to the primary port and a secondary pressure chamber connected to the secondary port. A primary pressure receiving surface that receives the primary pressure, a back pressure receiving surface that receives the primary pressure from the fluid in the decompression back pressure chamber held in the primary pressure in the axial direction to the other in the axial pressure receiving area, and a secondary pressure. A pressure-reducing piston formed with a secondary pressure-receiving surface that receives a secondary pressure directed in the other axial direction from the fluid in the chamber, and a pressure-reducing spring force generating means that applies a pressure-reducing spring force directed in the axial direction to the pressure-reducing piston. Features.
[0017]
According to the present invention, the back pressure receiving surface having the same back pressure receiving area as the primary pressure receiving area is formed on the pressure reducing piston, and the back pressure receiving surface is configured to receive the primary pressure from the pressure reducing back pressure chamber. The primary pressure receiving surface and the back pressure receiving surface receive primary pressure from opposite directions in the axial direction. Based on the primary pressure, the axial force due to the primary pressure acting on the decompression piston can be canceled by balancing the force acting on the decompression piston in one axial direction and the force acting on the decompression piston in the other axial direction. As a result, the secondary pressure can be made less susceptible to the influence of the primary pressure. Therefore, the change amount of the secondary pressure with respect to the change amount of the primary pressure can be greatly reduced.
[0018]
In order to further increase the maximum allowable flow rate, even if the primary pressure receiving area of the pressure reducing piston that receives the primary pressure is increased, the change in the primary pressure receiving area does not greatly affect the change in the secondary pressure. There is no need to increase the maximum outer diameter of the decompression piston in order to suppress the amount of change in the next pressure. Therefore, it is possible to realize a valve device that can keep the radial dimension small, increase the maximum allowable flow rate, and keep the change amount of the secondary pressure small.
[0019]
As for this invention of Claim 3, an on-off valve part is
An open / close piston that is held in a housing so as to be displaceable in an axial direction, and that switches between a connection state between a primary port and a secondary port by being seated and separated from a valve seat formed in the housing. A closed pressure receiving surface that receives the primary pressure in the direction in which it is seated in the closed pressure receiving area, and an open / close pressure surface that receives the primary pressure in the direction away from the valve seat from the valve seat in the same open pressure area as the closed pressure receiving area. A piston,
An opening / closing driving means is provided that applies an axial driving force to the opening / closing piston to switch the connection state between the primary port and the secondary port between the open state and the closed state.
[0020]
According to the present invention, the open / close piston is formed with a closed pressure receiving surface having a closed pressure receiving area and an open pressure receiving surface having the same open pressure receiving area as the closed pressure receiving area, and the closed pressure receiving surface seats the open / close piston on the valve seat. A primary pressure is received in the direction, and the open / close pressure surface is configured to receive the primary pressure in a direction separating the open / close piston from the valve seat. The closed pressure receiving surface and the open pressure receiving surface receive primary pressure from opposite directions in the axial direction. Based on the primary pressure, the axial force due to the supply pressure acting on the open / close piston can be canceled by balancing the force acting on the open / close piston in one axial direction with the force acting on the open / close piston in the other axial direction. Therefore, the driving force in the axial direction applied to the opening / closing piston can be reduced because the opening / closing driving means switches the connection state between the primary port and the secondary port regardless of the magnitude of the primary pressure.
[0021]
In order to further increase the maximum allowable flow rate, even if the closed and open pressure areas of the open / close piston receiving the primary pressure are increased, the closed pressure area and the open pressure area are formed to be the same, thereby making it based on the primary pressure. Thus, the axial force due to the primary pressure acting on the piston can be offset by balancing the force acting on the open / close piston in one axial direction and the force acting on the open / close piston in the other axial direction. Accordingly, it is possible to easily realize a valve device that does not require a large driving force to drive the open / close piston and can increase the maximum allowable flow rate without increasing the open / close drive means.
[0022]
The present invention according to claim 4 is characterized in that the open / close position of the flow path in the open / close valve portion is arranged on the upstream side in the fluid flow direction as compared with the reduced pressure position in the pressure reducer valve portion.
[0023]
According to the present invention, the open / close position of the flow path in the open / close valve portion is arranged on the upstream side in the fluid flow direction as compared with the reduced pressure position in the pressure reducer portion. As a result, when the on-off valve portion is closed, a high-pressure primary pressure does not act on the pressure reducing valve portion, and durability can be increased. In addition, the fluid that has passed through the on-off valve part is surely reduced in pressure by the pressure-reducing valve part, and even if the on-off valve part is opened after leaving the on-off valve part closed for a long time, the secondary pressure is The pressure is reduced. Thus, high pressure gas is prevented from being discharged.
[0024]
DETAILED DESCRIPTION OF THE INVENTION
FIG. 1 is a cross-sectional view showing a valve device 20 according to an embodiment of the present invention. The valve device 20 is interposed in a flow path in which fluid flows down from the primary side to the secondary side, and supplies the supplied primary pressure (hereinafter referred to as “primary pressure”) P1 fluid to the secondary pressure (lower than the primary pressure P1) ( This is a valve device that discharges by reducing pressure to P2 (hereinafter referred to as “secondary pressure”). In the present embodiment, the valve device 20 is attached to an opening 81 of a high-pressure tank (hereinafter sometimes simply referred to as “tank”) 200 that is a high-pressure vessel, and is moved out of the tank 200 for fluid stored in the tank 200. Used to control the discharge and stop of discharge. Therefore, the primary side is inside the tank 200 and the secondary side is outside the tank 200, and the flow of fluid from the inside of the tank 200 to the outside of the tank 200 is controlled.
[0025]
The valve device 20 includes a housing 21, a decompression piston 22, a decompression spring member 23, a tubular member 24, an opening / closing piston 85, and an opening / closing drive means 86. The open / close piston 85 includes an open / close valve body 87 and a shaft body 88, and the open / close drive means 86 includes a drive spring member 89 and an electromagnetic solenoid 90. A pressure reducing valve portion is configured including at least the pressure reducing spring member 23 and the cylindrical member 24, and an opening / closing valve portion is configured including at least the opening / closing piston 85 and the opening / closing driving means 86.
[0026]
In the valve device 20, at least the housing 21, the decompression piston 22, the decompression spring member 23, the tubular member 24, the opening / closing piston 85, and the drive spring member 89 are provided coaxially with each other. In the present embodiment, the electromagnetic solenoid 90 and the like are provided coaxially, and each axis coincides with the device axis L 1 of the valve device 20.
[0027]
The housing 21 has a bottomed cylindrical housing body 25 and a cap member 27 that is inserted into the open end portion 26 of the housing body 25 and attached. The cap member 27 is rotated around the device axis L1 with respect to the housing body 25 and is screwed and screwed along the device axis L1 so that the position in the axial direction can be adjusted. The cap member 27 has a bottomed cylindrical shape, and the open end 91 is disposed on the bottom 29 side of the housing body 25, and thus the bottom 92 is disposed on the axial end portion 31 side of the housing 21. It is disposed on the other end 32 side in the axial direction. Sealing is achieved between the inner periphery of the housing body 25 and the outer periphery of the cap member 27 over the entire circumference.
[0028]
The cap member 27 is formed with a primary port 28 that passes through the bottom portion 92 along the device axis L 1, and a bottom port 29 of the housing body 25 is formed with a secondary port 30 that is offset from the device axis L 1. As described above, the housing 21 has the primary port 28 formed at the one axial end portion 31 and the secondary port 30 formed at the other axial end portion 32. The primary port 28 and the secondary port 30 are formed in the housing 21. A valve space 94 that communicates with each other is formed.
[0029]
Further, the cap member 27 is formed with a flange-shaped inward convex portion 93 that protrudes inward in the radial direction and extends in the entire circumferential direction at a portion near the open end portion 91. The inwardly projecting portion 93 tapers in the axial direction one X1 toward the bottom 29 of the housing body 25 on the end surface of the axial body X1 and thus on the end surface facing the bottom 29 of the housing body 25. An annular projection piece 38 that protrudes and extends in the entire circumferential direction is formed. Further, the valve seat 112 is formed on the inwardly convex portion 93 of the cap member 27 on the end surface portion of the other axial direction X 2, and thus on the end surface portion facing the bottom portion 92 of the cap member 27.
[0030]
Such a housing 21 has an outer peripheral portion screwed into an inner peripheral portion of the opening portion 81 of the tank 200 such that the primary port 28 opens in the tank 200 and the secondary port 30 opens outside the tank 200. Screwed. Sealing is achieved over the entire circumference in the circumferential direction between the outer circumference of the housing 21 and the inner circumference of the opening 81 of the tank 200. One axial direction X 1 is a direction from one axial end 31 of the housing 21 toward the other end 32.
[0031]
The decompression piston 22 is formed in a bottomed cylindrical shape, and the bottom 35 side that is one end in the axial direction is disposed on the one end 31 side in the axial direction of the housing 21, and the open end 36 that is the other end in the axial direction is disposed in the housing. 21 is disposed on the other end 32 side in the axial direction and is held in the housing 21. In this state, the decompression piston 22 is displaceable along the device axis L1 to one axial direction X1 and the other opposite axial direction X2.
[0032]
A flange-shaped inward convex portion 40 that protrudes inward in the radial direction and extends in the entire circumferential direction is formed at the axial intermediate portion 39 between the

axial end portions

31, 32 of the housing 21, and this inward convex portion. The outer peripheral portion of the axially intermediate portion 37 between the bottom portion 35 and the open end portion 36 of the decompression piston 22 is in contact with the inner peripheral portion of the pressure reducing piston 22 in a state where a seal is achieved. The open end 36 of the decompression piston 22 is formed with a flange-like outward convex portion 41 that protrudes outward in the radial direction and extends in the entire circumferential direction. The outer peripheral portion of the outward convex portion 41 is the housing 21. In the axial direction intermediate portion 39, the inner peripheral portion of the portion closer to the other end portion 32 in the axial direction than the inward convex portion 40 is in contact with the seal.
[0033]
The decompression spring member 23, which is a decompression spring force generating means, is a compression coil spring, and the housing 21 and the decompression piston 22 are disposed in an annular spring accommodating space 43 formed at an interval in the radial direction to reduce the pressure. It is provided in the housing 21 in a state of being fitted on the piston 22. The spring accommodating space 43 is formed between the inward convex portion 40 and the outward convex portion 41, and is opened to the atmosphere by an atmospheric opening hole 44 formed in the housing 21.
[0034]
The decompression spring member 23 has one axial end 45 supported by the inward convex portion 40 of the housing body 25 and the other axial end 46 supported by the outward convex portion 41 of the opening / closing piston 22. With the pressure-reducing spring member 23, a spring force directed in the axial direction X 1 with respect to the housing 21 can be applied to the pressure-reducing piston 22.
[0035]
The cylindrical member 24 is generally cylindrical and is held by the housing 21, and a portion on the axial one end 48 side is disposed in the decompression piston 22 along the device axis L 1 with respect to the decompression piston 22. It is inserted so as to be displaceable in one axial direction X1 and the other axial direction X2. The cylindrical member 24 is provided in a state where at least the axial other end 51 protrudes from the decompression piston 22, and the axial other end 51 is formed to have a larger outer diameter than the remaining portion. The open end 36 of the decompression piston 22 is configured to be supported in the axial direction.
[0036]
A fitting recess 50 that is concave toward the open end 26 (in the other axial direction X2) is formed at one end 31 in the axial direction of the housing 21, and thus at the bottom 29 of the housing body 25. The tubular member 24 is held with the other axial end 51 fitted in the fitting recess 50.
[0037]
One end 48 in the axial direction of the cylindrical member 24 abuts the outer peripheral portion of the cylindrical member 24 on the inner peripheral portion of the decompression piston 22 in a sealed state, and cooperates with the open / close piston 85 to cooperate with the decompression piston 22 and the cylindrical member 24. A decompression back pressure chamber 55 is formed between the two. The cylindrical member 24 is a portion excluding the one axial end 48, and the outer peripheral portion of the portion inserted into the decompression piston 22 is spaced apart from the inner periphery of the decompression piston 22 in the radial direction. An annular piston inner space 56 is formed.
[0038]
The open / close valve body 87 of the open / close piston 85 has a bottomed cylindrical valve body portion 95 and a power transmission portion 96 that projects coaxially from the bottom portion of the valve body portion 95. In this on-off valve body 87, the valve body portion 95 is disposed on the axial end portion 31 side of the housing 21, the power transmission portion 96 is disposed on the axial end portion 32 side of the housing 21, and the valve body portion 95 is In a state where the cap member 27 fits into the valve body chamber 97 sandwiched between the bottom portion 92 and the inward convex portion 93 and the power transmission portion 96 is gently inserted through the inner side of the inward convex portion 93 of the cap member 27. Is held in the housing 21. Further, a through hole 71 is formed in the bottom 35 of the decompression piston 22 so as to pass through the bottom 35 along the device axis L1. The power transmission unit 96 gently inserts the through hole 71 into the decompression piston. 22 extends into the interior.
[0039]
In the state in which the opening / closing valve body 87 is provided as described above, the opening / closing seat portion 99 formed on the bottom of the valve body portion 95 is seated on the valve seat 112, and the opening / closing seat portion 99 is separated from the valve seat 112. Over the open position, it is displaceable along the device axis L1 to one axial direction X1 and the other axial direction X2. When the on-off valve body 87 is in the open position, the primary port 28 and the pressure-reducing piston primary pressure receiving space 100 are opened, and when the on-off valve body 87 is in the closed position, the primary port 28 and the pressure-reducing piston primary pressure receiving pressure. The space 100 is closed. The pressure-reducing piston primary pressure receiving space portion 100 is sandwiched between the inward convex portion 93 of the cap member 27 and the bottom portion 35 of the decompression piston 22, and is formed on the projecting piece 38 formed on the inward convex portion 93 of the cap member 27. It is a space inward in the radial direction.
[0040]
The shaft body 88 of the open / close piston 85 is substantially cylindrical, and is held by the housing 21 so as to be displaceable in the axial direction one X1 and the other axial direction X2 along the device axis L1. This axial body 88 is displaceable in the axial direction one end 101 side in the cylindrical member 24, with respect to the cylindrical member 24, along the apparatus axis L1, to one axial direction X1 and the other axial direction X2. Has been inserted.
[0041]
The shaft body 88 is provided in a state where at least the other axial end portion 102 protrudes from the tubular member 24. An insertion hole 104 is formed at the other end 32 in the axial direction of the housing 21, specifically, at the bottom 29 of the housing body 25, and is inserted along the device axis L 1. The shaft body 88 is formed through the insertion hole 104. The other end 102 in the axial direction extends so as to protrude outside the housing 21.
[0042]
The axial end portion 101 of the shaft body 88 abuts the outer peripheral portion of the shaft body 88 on the inner peripheral portion of the cylindrical member 24 in a sealed state, thereby forming the above-described decompression back pressure chamber 55. Further, the shaft body 88 is formed with a step portion 105 having a larger outer diameter at a portion on the axial direction one end portion 101 side than a portion on the other end portion 102 side in the axial direction. On both sides in the axial direction of 105, the outer peripheral portion is in contact with the inner peripheral portion facing the insertion hole 104 of the housing body 25 in a state where a seal is achieved.
[0043]
In this way, the housing body 25 and the shaft body 88 form an open / close back pressure chamber 106 where the stepped portion 105 of the shaft body 88 faces, and the open / close back pressure chamber 106 is formed in the communication passage formed in the housing body 25. 107 communicates with the tank 200 to guide the primary pressure P1. A space 123 is formed by the housing 21, the cylindrical member 24, and the shaft body 88, and the space 123 is opened to the atmosphere by the atmosphere opening hole 44.
[0044]
The on-off valve body 87 and the shaft body 88 can transmit a force in one axial direction X1 from the on-off valve body 87 to the shaft body 88 while being in contact with each other. The force in the other axial direction X2 can be transmitted to 87. Therefore, the on-off piston 85 gives a driving force in one axial direction X1 to the on-off valve body 87 in a state where the on-off valve body 87 and the shaft body 88 are in contact with each other, and is integrally displaced in one axial direction X1. It is possible to apply a driving force to the shaft body 88 in the other axial direction X2 so that the shaft body 88 can be integrally displaced in the other axial direction X2.
[0045]
The drive spring member 89 of the opening / closing drive means 86 is a compression coil spring, is disposed in the valve body chamber 97, and is provided to be at least partially inserted into the valve body portion 95 of the opening / closing valve body 87. This drive spring member 89 as drive spring force generating means has one axial end 110 supported by the bottom 92 of the cap member 27 and the other axial end 111 near the bottom of the valve body 95 (including the bottom). Supported. By this drive spring member 89, a spring force for displacing and driving the housing 21 in the axial direction along the device axis L1, specifically, a spring force directed toward one side X1 in the axial direction, the valve body 95 is moved. A spring force in the closing direction for seating on the valve seat 112 can be applied to the open / close piston 85.
[0046]
The electromagnetic solenoid 90 of the opening / closing drive means 86 is disposed outside the housing 21 and is provided in the bottom 29 of the housing body 25 so as to cover the insertion hole 104 from the outside. The electromagnetic solenoid 90, which is an electromagnetic drive source, includes a drive member 120 and a drive coil that are slidably held in the axial direction one X1 and the other axial direction X2 along the device axis L1. A space 122 formed by the electromagnetic solenoid 90 and the housing 21 and facing the shaft member 88 is opened to the atmosphere by the atmosphere opening hole 44.
[0047]
By switching between energization and non-energization of the drive coil, the drive member 120 is displaced in the axial direction along the device axis L1, and the shaft member 88 is pressed by the drive member 120, so that the device axis is against the housing 21. The electromagnetic driving force for driving displacement in the axial direction along L1, specifically, the electromagnetic driving force toward the other X2 in the axial direction, and the electromagnetic driving force in the opening direction that separates the valve body 95 from the valve seat 112 Can be applied to the open / close piston 85. The electromagnetic driving force by the electromagnetic solenoid 90 is larger than the spring force of the driving spring member 89.
[0048]
In such a valve device 20, as described above, the outer peripheral portion of the decompression piston 22 is in contact with the inner peripheral portion of the housing 21 at two locations in a state where a seal is achieved over the entire circumference in the circumferential direction. In the housing 21, a bottomed cylindrical first space 60 is formed between the housing 21 and the decompression piston 22 on the other X2 side in the axial direction than the inward convex portion 40 of the housing body 25. An annular second space 61 connected to the secondary port 30 is formed on the X1 side in the axial direction from the outward projecting portion 41 of the decompression piston 22.
[0049]
The decompression piston 22 is formed with a decompression sheet portion 62 made of a special resin extending in the entire circumferential direction on an end surface portion of one end portion in the axial direction, and the decompression sheet portion 62 is opposed to the protruding piece 38 of the cap member 27 in the axial direction. Thus, an annular orifice 63 extending in the entire circumference is formed. The first space 60 has two

space portions

100 and 65 that are connected via an orifice 63. A region located radially inward from the orifice 63 is the above-described pressure-reducing piston primary pressure receiving space 100 connected to the primary port 28.
[0050]
Further, the decompression piston 22 is formed with an insertion hole 67 that is inserted into the inside and outside at a portion closer to the open end portion 36 than a portion that contacts the axial direction one end portion 48 of the cylindrical member 24 in the axial direction intermediate portion 37. Through the insertion hole 67, the outer space portion 65 radially outward from the orifice 63 in the first space 60 and the piston inner space 56 communicate with each other.
[0051]
In addition, a communication hole is opened in the axial direction other end portion 51 of the cylindrical member 24 and in the vicinity thereof at one end portion inserted into the decompression piston 22 and the other end portion projecting from the decompression piston 22. 68 is formed. Through this communication hole 68, the second space 61 and the piston inner space 56 are communicated with each other, and the second space 61 and the piston inner space 56 are communicated with the secondary port 30. A secondary pressure chamber 70 connected to the secondary port 30 is configured including the outer space 65, the second space 61, the piston inner space 56, the insertion hole 67, and the communication hole 68 on the radially outer side from the orifice 63. The
[0052]
The valve body 95 of the on-off valve body 87 is formed with an insertion hole 115 that is inserted into the inside and outside. The insertion hole 115 can prevent a sealed region from being formed in the valve body chamber 97. The valve body chamber 97 and the pressure reducing piston primary pressure receiving space portion 100 are connected via an annular communication space 121 between the inward convex portion 93 of the cap member 27 and the power transmission portion 96 of the on-off valve body 87. The valve body chamber 97 and the pressure reducing piston primary pressure receiving space 100 are communicated with the primary port 28. A primary pressure chamber 64 connected to the primary port 28 is configured including the valve body chamber 97, the decompression piston primary pressure receiving space portion 100, and the communication space 121.
[0053]
The on-off valve body 87 can switch between the valve body chamber 97 and the pressure-reducing piston primary pressure receiving space 100 between an open state for opening and a closed state for closing. In the closed state, the primary pressure P1 is not guided to the decompression piston primary pressure receiving space portion 100 and the communication space 121, but in the open state, the primary pressure P1 is guided to the entire primary pressure chamber 64. Further, the primary port 28 and the secondary port 30 are opened by switching between the valve body chamber 97 and the pressure reducing piston primary pressure receiving space portion 100 between an open state in which the valve body chamber 97 is closed and a closed state in which it is closed. The connection state between the primary port 28 and the secondary port 30 is switched between the open state and the closed state.
[0054]
Further, the bottom 35 of the decompression piston 22 is formed with a through hole 71 through which the bottom 35 is inserted along the device axis L1. Through the through hole 71, the reduced pressure piston primary pressure receiving space 100 of the primary pressure chamber 64 and the reduced pressure back pressure chamber 55 communicate with each other, and the reduced pressure back pressure chamber 55 is held at the primary pressure P1.
[0055]
In such a valve device 20, in a non-energized state where no drive current is applied to the drive coil of the electromagnetic solenoid 90, the open / close piston 85 is moved by the spring force in the closing direction toward the one axial direction X 1 of the drive spring member 89. The on-off valve body 87 is disposed at the first position in the closed position where the on-off seat portion 99 is seated on the valve seat 112 as shown in FIG. In this state, the valve device 20 prevents the fluid from flowing from the primary port 28 to the secondary port 30 and stops discharging the fluid from the tank 200 to the outside of the tank 200.
[0056]
Further, in the valve device 20, in the energized state in which a drive current is applied to the drive coil of the electromagnetic solenoid 90, the drive spring member is generated by the electromagnetic force generated by the electromagnetic solenoid 90 and in the opening direction toward the other axial direction X2. The open / close piston 85 is displaced from the first position in FIG. 1 to the second axial direction X2 against the spring force of 89, and thus the open / close valve body 87 opens the open / close seat portion 99 away from the valve seat 112. It is arranged at the second position. In this state, the valve device 20 allows the fluid to flow from the primary port 28 to the secondary port 30 and releases the discharge of the fluid from the tank 200 to the outside of the tank 200.
[0057]
As described above, the on / off valve portion is configured so that the electromagnetic solenoid 90 and the drive spring member 89 cooperate with each other by supplying and stopping supply of the drive current to the electromagnetic solenoid 90, and at least one of electromagnetic force and spring force is applied to the open / close piston 85. One of them can be actuated to drive the opening / closing piston 85 so that the communication between the primary port 28 and the secondary port 30 can be controlled. In the present embodiment, the driving force of the open / close piston 85 includes a spring force by the drive spring member 89 and an electromagnetic force by the electromagnetic solenoid 90.
[0058]
In the valve device 20, the decompression piston 22 partitions the inside of the housing 21 into a primary pressure chamber 64 and a secondary pressure chamber 70 that are connected by an orifice 63. In a state where the on-off valve portion is open, the fluid supplied to the primary port 28 passes from the primary pressure chamber 64 through the orifice 63 to the secondary pressure chamber 70, specifically, the outer space of the first space 60. It flows down to the portion 65, flows through the insertion hole 67, the piston inner space 56 and the communication hole 68 to the secondary port 30 and is discharged from the secondary port 30. Thus, when the fluid flows down the valve device 20, the decompression piston 22 is spaced apart in the axial direction from the other axial end portion 51 of the cylindrical member 24.
[0059]
As the fluid passes through the orifice 63, the pressure of the fluid is reduced. In other words, the fluid is depressurized from the primary pressure chamber by passing through the orifice 63 and flows down to the secondary pressure chamber 70. Therefore, the fluid in the primary port 28, the primary pressure chamber 64, and the decompression back pressure chamber 55 has the primary pressure P1, and the fluid in the secondary port 30 and the secondary pressure chamber 70 is decompressed lower than the primary pressure P1. Secondary pressure P2.
[0060]
FIG. 2 is a cross-sectional view shown for explaining the dimensions of each part of the valve device 20. The open / close valve body 87 of the open / close piston 85 has its outer surface facing the primary pressure chamber 64 and the decompression back pressure chamber 55 held at the primary pressure P1, and the shaft body 88 is a decompression back pressure held at the primary pressure P1. It faces the chamber 55 and the open / close back pressure chamber 106. Such an open / close piston 85 has a closed pressure receiving surface 130 having a closed pressure receiving area A1 that effectively receives the primary pressure P1 in the direction in which the open / close piston 85 is seated on the valve seat 112. The closed pressure receiving area A1 is determined from the pressure receiving area where the opening / closing piston 85 receives the primary pressure P1 in the axial direction X1 by the fluid in the primary pressure chamber 64 and the decompression back pressure chamber 55, and the opening / closing piston 85 has the primary pressure chamber 64 and the decompression back pressure. The primary pressure P1 received from the fluid in the primary pressure chamber 64 and the decompression back pressure chamber 55, which is the area obtained by subtracting the pressure receiving area that receives the primary pressure P1 in the other axial direction X2 by the fluid in the chamber 55, is applied to the open / close piston 85. It is an area that works effectively as a force in one axial direction X1. In the present embodiment, the diameter D4 of the cross section perpendicular to the device axis L1 of the axial one end 101 facing the decompression back pressure chamber 55 of the shaft 88 is formed to be the same as the outer diameter D1 of the tip of the valve seat 112. ing. Therefore, the open / close piston 85 has a closed pressure receiving area A1 regardless of whether the open / close valve portion is open or closed, and whether the open / close valve body 87 and the shaft body 88 are in contact with or separated from each other. It becomes the area of the circle of the same outer diameter as the outer diameter D1 of the front-end | tip part of the valve seat 112, and is represented by following Formula (3).
[0061]
[Expression 2]

[0062]
Here, an area A4 of a cross section perpendicular to the apparatus axis L1 at the axial end portion 101 of the shaft body 88 is expressed by the following equation (4) and is the same as the closed pressure receiving area A1.
[0063]
[Equation 3]

[0064]
Further, the opening / closing piston 85 is configured such that the stepped portion 105 is formed in the shaft body 88 as described above, and the stepped portion 105 is provided in the opening / closing back pressure chamber 106. Accordingly, the open / close piston 85 has an open / close pressure surface 131 having an open / close pressure area A7-A8 that effectively receives the primary pressure P1 in the direction away from the valve seat 112. The open / close pressure area A7-A8 is determined from the pressure receiving area where the open / close piston 85 receives the primary pressure P1 in the other axial direction X2 by the fluid in the open / close back pressure chamber 105, and the open / close piston 85 axially by the fluid in the open / close back pressure chamber 106. On the other hand, an area obtained by subtracting the pressure receiving area for receiving the primary pressure P1 from X1, and the area where the primary pressure P1 received from the fluid in the opening / closing back pressure chamber 106 effectively acts on the opening / closing piston 85 as a force in the other axial direction X2. It is.
[0065]
In the present embodiment, a pressure-receiving pressure surface 131 is formed in the stepped portion 105 of the shaft body 88, and the cross section perpendicular to the device axis L1 is a portion of the stepped portion 105 having a large outer diameter on the axial end portion 101 side. This is an area obtained by subtracting the area A8 of the cross section perpendicular to the device axis L1 of the portion having a small outer diameter on the side of the other end 102 in the axial direction in the stepped portion 105 from the area A7. Therefore, the open pressure pressure area A7-A8 is the outer diameter D7 of the step portion 105 having a large outer diameter on the one end portion 101 side in the axial direction and the portion of the step portion 105 having a small outer diameter on the other end portion 102 in the axial direction. It represents with following Formula (5) using the outer diameter D8.
[0066]
[Expression 4]

[0067]
In the present embodiment, the open pressure area A7-A8 is the same as the closed pressure area A1 (= A4). The open / close piston 85 does not face the secondary pressure chamber 70 held at the secondary pressure P2, and does not receive the secondary pressure P2.
[0068]
Atmospheric pressure also acts on the open / close piston 85, but since the influence on the operation of the open / close piston 85 is small, for convenience, if the force due to atmospheric pressure is ignored, the axial force F1 acting on the open / close piston 85 is one X1 in the axial direction. When the force of is positive, it is expressed as the following formula (6).
F1 = Fk + {A1- (A7-A8)} P1-Fs (6)
Fk = K1 (ΔH1 + Z1) (7)
[0069]
Here, Fk is a spring force by the drive spring member 89, K1 is a spring constant of the drive spring member 89, and ΔH1 is a natural force of the drive spring member 89 when the on-off valve body 87 is in the closed position. Z1 is the amount of displacement from the closed position of the on-off valve element 87 in the axial direction to one side X1. Fs is an electromagnetic force generated by the electromagnetic solenoid 90.
[0070]
In the open / close valve portion of the present embodiment, in the above equation (6), the open / close back pressure chamber 106 is formed so that the open / close piston 85 receives the primary pressure P1 at the open pressure area A7-A8 in the other axial direction X2. Thus, the force (A1 × P1) due to the primary pressure P1 received by the open / close piston 85 in the one axial direction X1 and the force due to the primary pressure P1 received by the open / close piston 85 in the other axial direction X2 {(A7−A8) × P1} and the axial force due to the primary pressure P1 acting on the open / close piston 85 can be offset, that is, {A1- (A7-A8)} P1 = 0.
[0071]
In the conventional configuration, when the primary pressure is increased, in order to stably seat the opening / closing piston on the valve seat, a spring that gives the opening / closing piston a spring force large enough to resist the force acting on the opening / closing piston by the primary pressure. It is necessary to use a drive spring member with a large force, and when separating the opening / closing piston from the valve seat, the electromagnetic solenoid must be enlarged so that a large electromagnetic force can be applied against such a large spring force. . On the other hand, in the on-off valve portion in the valve device 20 of the present embodiment, the axial force due to the primary pressure P1 acting on the on-off piston 85 is canceled out, so that even if the primary pressure P1 is increased, it is stable. Since the open / close seat portion 99 of the open / close piston 85 is seated on the valve seat 112 and closed, it is not necessary to increase the spring force of the drive spring member 89. Accordingly, in order to open the opening / closing seat 99 of the opening / closing piston 85 away from the valve seat 112, it is not necessary to increase the electromagnetic force applied to the opening / closing piston 85, and the electromagnetic solenoid 90 is downsized. And the size of the on-off valve portion can be kept small.
[0072]
Further, in order to increase the flow capacity, that is, the maximum allowable flow rate, even if the closed pressure receiving area A1 that receives the primary pressure P1 is increased, the axial force due to the primary pressure P1 acting on the opening / closing piston 85 is canceled, and the drive spring Since the member 89 closes the primary port 28 and the secondary port 30, the spring force applied to the open / close piston 85 can be reduced. As a result, the electromagnetic solenoid 90 does not increase the electromagnetic force applied to the open / close piston 85 in order to open the primary port 28 and the secondary port 30.
[0073]
Further, the decompression piston 22 has a primary pressure receiving surface 75 of a primary pressure receiving area A2 that effectively receives the primary pressure P1 from the fluid in the primary pressure chamber 64 toward the one axial direction X1. The primary pressure receiving area A2 is such that the pressure reducing piston 22 receives the primary pressure P1 in one axial direction X1 by the fluid in the primary pressure chamber 64, and the pressure reducing piston 22 is primary in the other axial direction X2 by the fluid in the primary pressure chamber 64. It is an area obtained by subtracting the pressure receiving area that receives the pressure P1, and the primary pressure P1 received from the fluid in the primary pressure chamber 64 is an area that effectively acts as a force in the axial direction one X1 on the decompression piston 22.
[0074]
The decompression piston 22 faces the primary pressure chamber 64 only from one axial direction X1 and receives the primary pressure P1 from the fluid in the primary pressure chamber 64 only in one axial direction X1. The primary pressure receiving area A 2 is determined using the diameter D 2 of the tip of the projection piece 38 that forms the orifice 63 in cooperation with the pressure reducing sheet portion 62 and the diameter D 10 of the through hole 71 formed in the pressure reducing piston 22. It is represented by Formula (8).
[0075]
[Equation 5]

[0076]
The decompression back pressure chamber 55 is formed by inserting one axial end 48 of the cylindrical member 24 into the decompression piston 22 as described above. The decompression piston 22 is formed in the decompression back pressure chamber 55. It has a back pressure receiving surface 76 having a back pressure receiving area A3 that effectively receives the primary pressure P1 from the fluid in the other axial direction X2. The back pressure receiving area A3 is determined by the pressure receiving area where the pressure reducing piston 22 receives the primary pressure P1 in the other axial direction X2 from the fluid in the pressure reducing back pressure chamber 55, and the pressure receiving piston A is in the axial direction X1 from the fluid in the pressure reducing back pressure chamber 55. Is the area obtained by subtracting the pressure receiving area that receives the primary pressure P1, and the primary pressure P1 received from the fluid in the reduced pressure back pressure chamber 55 is an area that effectively acts as a force on the pressure reducing piston 22 in the other axial direction X2. . This back pressure receiving area A3 is expressed by the following equation (9) using the outer diameter D3 of the axial end 48 of the cylindrical member 24 and the diameter D10 of the through hole 71 formed in the decompression piston 22. .
[0077]
[Formula 6]

[0078]
The diameter D2 of the tip end portion of the protrusion piece 38 and the outer diameter D3 of the axial direction one end portion 48 of the cylindrical member 24 are the same. Therefore, the primary pressure receiving area A2 and the effective back pressure receiving area A3 are the same. As described above, the pressure reducing piston 22 has the primary back pressure receiving area A3 that is the same as the primary pressure receiving area A2 of the primary pressure receiving surface 75 that receives the primary pressure P1 from the fluid in the primary pressure chamber 64 in one axial direction X1. The back pressure receiving surface 76 which receives the primary pressure P1 which goes to the other axial direction X2 from the fluid in the pressure chamber 55 is provided.
[0079]
The decompression piston 22 has a secondary pressure receiving surface 80 having a pressure receiving area A6-A5 that effectively receives the secondary pressure P2 from the fluid in the secondary pressure chamber 70 toward the other axial direction X2. The pressure receiving area A6 where the pressure reducing piston 22 receives the secondary pressure P2 in the other axial direction X2 from the fluid in the secondary pressure chamber 70 is the outward convex portion which is the maximum outer diameter of the portion facing the second space 61 of the pressure reducing piston 22 The area of the cross section perpendicular to the device axis L1 of the axial direction one end portion 48 of the cylindrical member 24 from the area of the circle having the outer diameter D6 of 41 (= (π / 4) D3²), And is represented by the following equation (10).
[0080]
[Expression 7]

[0081]
Further, the pressure receiving area A5 where the pressure reducing piston 22 receives the secondary pressure P2 in the axial direction X1 from the fluid in the secondary pressure chamber 70 has a maximum outer diameter D5 of the portion facing the outer space 65 of the pressure reducing piston 22 as a diameter. The area obtained by subtracting the area of a circle having the same diameter as the diameter D2 of the tip of the protrusion piece 38 from the area of the circle, and is represented by the following equation (11).
[0082]
[Equation 8]

[0083]
FIG. 3 is a graph showing the secondary pressure P2 of the valve device 20. FIG. 3 (1) shows the relationship between the primary pressure P1 and the secondary pressure P2, and FIG. The relationship with the secondary pressure P2 is shown. In the valve device 20, the balance of forces acting on the decompression piston 22 is expressed by the following equation (12).
[0084]
[Equation 9]

[0085]
Here, K2 is a spring constant of the pressure reducing spring member 23, and ΔH is a deflection amount from the natural state in the initial state of the pressure reducing spring member 23 shown in FIG. This initial state is a state in which, for example, the decompression piston 22 is disposed at the most axial direction X1 and is supported by the cylindrical member 24 in the axial direction. Z2 is the amount of displacement of the decompression piston 22 from the initial state shown in FIG. 1 toward the other axial direction X2, and flows down the primary pressure P1 and the valve device 20 as expressed by the equation (13). Expressed as a function of the fluid flow rate Q.
[0086]
From the balance equation of the equation (12), the secondary pressure P2 is expressed as the following equation (14).
[0087]
[Expression 10]

[0088]
In the valve device 20 of the present embodiment, the decompression back pressure chamber 55 is formed as described above, and the decompression piston 22 is configured to receive the primary pressure P1 at the back pressure receiving area A3 in the other axial direction X2. Thus, the force due to the primary pressure P1 received by the pressure reducing piston 22 on the one axial direction X1 and the force caused by the primary pressure P1 received by the pressure reducing piston 22 on the other axial direction X2 can be balanced and offset. That is, the primary pressure receiving area A2 and the back pressure receiving area A3 can be made the same, and the numerator of the second term on the right side in the above equation (14) can be made zero (A2-A3 = 0), and even if the primary pressure P1 changes, The value of the second term on the right side in equation (14) can be set to a constant value (= 0) so that only the first term on the right side changes (P2 = ε). Therefore, as shown in FIG. 3 (1), the amount of change ΔP2 of the secondary pressure P2 with respect to the amount of change ΔP1 of the primary pressure P1 is greatly reduced as compared with the conventional configuration in which the back pressure receiving surface 76 is not formed on the decompression piston 22. can do.
[0089]
Further, in the valve device 20, in order to increase the flow capacity, that is, the maximum allowable flow rate, the diameter D1 of the tip of the protruding piece 38 is increased, and the back pressure receiving area A3 is increased even if the primary pressure receiving area A2 is increased. Then, the change amount ΔP2 of the secondary pressure P2 with respect to the change amount ΔP1 of the primary pressure P1 can be suppressed to be small. Therefore, in order to increase the maximum allowable flow rate, there is no need to increase the pressure receiving area A6 that receives the secondary pressure P2 of the pressure reducing piston 22 on the other axial direction X2 as in the case where the back pressure receiving surface 76 is not formed on the pressure reducing piston 22. It is not necessary to increase the outer diameter D6 of the outward convex portion 41, which is the maximum outer diameter of the decompression piston 22. Accordingly, the radial dimension of the valve device 20 can be kept small. In this way, regardless of the flow rate Q, the radial dimension of the valve device 20 can be kept small, and the change amount ΔP2 of the secondary pressure P2 with respect to the change amount ΔP1 of the primary pressure P1 can be kept small.
[0090]
Further, by providing the tubular member 24 and partially inserting it into the decompression piston 22, the decompression back pressure chamber 55 can be formed with a simple construction, and the valve device 20 capable of obtaining the above-described effect can be easily obtained. Can be realized. Further, by using the piston inner space 56 between the decompression piston 22 and the cylindrical member 24 as a passage through which fluid flows, the outer space portion 65 of the first space 60 and the second space 61 communicate with the decompression piston 22. Therefore, it is not necessary to drill a passage extending in the axial direction, and the configuration is simple, and no complicated processing is required, so that it can be easily manufactured. Further, since the strength of the decompression piston 22 does not decrease with the passage of the passage, the thickness (radial dimension) of the decompression piston 22 can be kept small, and this also reduces the radial dimension of the valve device 20. Can do. Needless to say, a configuration in which a passage extending in the axial direction for communicating the outer space portion 65 and the second space 61 with the decompression piston 22 is also included in the present invention.
[0091]
The on-off valve portion that switches the connection state between the primary port 28 and the secondary port 30 and the pressure-reducing valve portion that reduces the secondary pressure P2 below the primary pressure P1 are mutually at least partially configured to flow down the fluid. Arranged at positions overlapping in the direction. In the present embodiment, the on-off valve portion is configured to pass through the pressure reducing valve portion. As a result, it is possible to reduce the size in the flow-down direction, specifically in the axial direction, as compared with the case where the on-off valve portion and the pressure reducing valve portion are simply provided in tandem. Moreover, the on-off valve portion and the pressure reducing valve portion are provided coaxially, and the housing 21 can be shared in a region where the on-off valve portion and the pressure reducing valve portion partially overlap, and the on-off valve portion and the pressure reducing valve portion can be shared. Compared with the case where the portions are simply provided in parallel, the dimension crossing the flow-down direction, specifically, the dimension in the radial direction can be reduced. Thus, the small valve device 20 can be realized by reducing the axial dimension and the radial dimension.
[0092]
Therefore, it is easy to attach to a pressure device, a pressure vessel, a pressure pipe, etc., and handling is also easy. Further, by making it small in size, it does not vibrate greatly even if vibration is applied from the outside, and the vibration resistance can be increased. For example, it can be suitably used for a portable pressure device and pressure vessel. In addition, by making it small, it can be easily built into the high-pressure vessel when it is installed in the high-pressure vessel, and there is no need to provide piping for the high-pressure fluid to flow outside the high-pressure vessel. Can be achieved. For example, when a pressure reducing valve is built in a high pressure vessel such as a high pressure tank, it is necessary to keep the outer diameter of the high pressure vessel small from the viewpoint of the strength of the high pressure vessel. It can be used suitably. Further, the overall mass can be reduced, and this also facilitates handling. In addition, with the integrated structure as described above, the number of parts of the valve device 20 can be reduced, and the manufacturing cost can be reduced.
[0093]
Furthermore, the open / close position of the flow path in the open / close valve portion is arranged on the upstream side in the fluid flow direction as compared with the reduced pressure position in the pressure reducer valve portion. As a result, when the on-off valve portion is closed, a high-pressure primary pressure does not act on the pressure reducing valve portion, and durability can be increased. In addition, the fluid that has passed through the on-off valve portion is always depressurized by the pressure-reducing valve portion. Even if the on-off valve portion is opened after leaving the on-off valve portion closed for a long time, the secondary pressure P2 remains. The pressure is reduced compared to the primary pressure. Thus, high pressure gas is prevented from being discharged.
[0094]
In the present embodiment, since the position of the cap member 27 on which the projection piece 38 is formed can be adjusted in the axial direction relative to the housing body 25, the axial distance between the projection piece 38 and the decompression sheet portion 62 of the decompression piston 22 is set. The pressure reduction ratio of the secondary pressure P2 to the primary pressure P1 can be adjusted.
[0095]
Such a valve device 20 is provided, for example, in a high-pressure tank such as a tank containing oxygen carried by a firefighter at a fire site or the like, and is used as a pressure-reducing valve for discharging the oxygen in the high-pressure tank to the outside while reducing the pressure. Can do. When used in such a high-pressure tank, the high-pressure tank needs to have a small radial dimension from the viewpoint of strength, and the valve device 20 that can keep the radial dimension small as described above is suitable. is there.
[0096]
Further, the opening / closing piston 85 in the opening / closing valve portion is configured by separating the opening / closing valve body 87 and the shaft body 88, and the opening / closing valve body 87 is remotely driven by the electromagnetic solenoid 90 via the shaft body 88. As a result, high-pressure fluid does not act on the components of the electromagnetic solenoid 90, and the tube (casing) of the electromagnetic solenoid 90 does not need to be formed firmly. Further, the sealing performance for preventing fluid leakage can be enhanced without increasing the machining accuracy of the electromagnetic solenoid 90.
[0097]
FIG. 4 is a sectional view showing a valve device 20A according to another embodiment of the present invention. The valve device 20A of the present embodiment is similar to the valve device 20 of the embodiment shown in FIGS. 1 to 3, and the same components are denoted by the same reference numerals, description thereof is omitted, and different configurations are provided. Just explain. The valve device 20A of the present embodiment further includes an operation handle 140 for manually opening / closing the opening / closing valve portion. The operation handle 140 is screwed into the casing of the electromagnetic solenoid 90, and is rotated to be screwed and screwed, whereby the drive member 120 can be displaced. Thus, by manually operating the operation handle 140, the open / close piston 85 can be driven to move in cooperation with the drive spring member 89.
[0098]
Such a valve device 20A can achieve the effect of manually operating the on-off valve unit in addition to the effect of the valve device 20 of FIGS. If the on-off valve portion can be manually operated in this way, the on-off valve portion can be operated even if a situation occurs in which the electromagnetic solenoid 90 cannot be electrically operated for some reason.
[0099]
FIG. 5 is a cross-sectional view showing a valve device 20B according to still another embodiment of the present invention. The valve device 20B of the present embodiment is similar to the valve device 20 of the embodiment shown in FIGS. 1 to 3, and the same components are denoted by the same reference numerals, description thereof is omitted, and different configurations are provided. Just explain. The valve device 20B of the present embodiment has a configuration in which the open / close back pressure chamber 106 is not formed with respect to the open / close valve portion. In such a configuration, the open / close back pressure chamber 106 and the communication passage 107 are provided in the open / close piston 85, although the force acting in the one axial direction X1 due to the primary pressure P1 cannot be canceled (cancelled) as described above. Since it is not necessary and the stepped portion 105 does not need to be formed in the opening / closing piston 85, the configuration can be simplified. This valve device 20B has the same effect as that of the valve device 20 of FIGS. 1 to 3 except that the force acting on the open / close piston 85 in the axial direction X1 due to the primary pressure P1 is canceled as described above. Can be achieved.
[0100]
FIG. 6 is a cross-sectional view showing a valve device 20C according to still another embodiment of the present invention. The valve device 20C of the present embodiment is similar to the valve device 20B of the embodiment shown in FIG. 5, and the same components are denoted by the same reference numerals, description thereof is omitted, and only different components are described. . The valve device 20C of the present embodiment is provided with an operation handle 140 similar to the valve device 20A shown in FIG. 4 in addition to the configuration of the valve device 20B of FIG. Thereby, in addition to the effect of the valve device 20B of FIG. 5, the effect of the operation handle 14 described in the valve device 20A of FIG. 4 can be similarly achieved.
[0101]
FIG. 7 is a cross-sectional view showing a valve device 20D according to still another embodiment of the present invention. The valve device 20D of the present embodiment is similar to the valve device 20A of the embodiment shown in FIG. 4, and the same components are denoted by the same reference numerals, description thereof is omitted, and only different components are described. . The valve device 20D of the present embodiment has a configuration in which the electromagnetic solenoid 90 is removed from the configuration of the valve device 20A in FIG. 4, in other words, the electromagnetic solenoid 90 in the configuration of the valve device 20 in FIGS. Instead, the operation handle 140 is provided, and the operation handle 140 is screwed to the housing 21. In the valve device 20D, the opening / closing piston 85 can be directly operated by operating the operation handle 140 without using a drive permanent magnet piece. About another structure, it is the same as that of the valve apparatus 20A of FIG. 4, and effects other than the effect relevant to the electromagnetic solenoid 90 can be achieved similarly to the valve apparatus 20A of FIG.
[0102]
FIG. 8 is a cross-sectional view showing a valve device 20E according to still another embodiment of the present invention. The valve device 20E of the present embodiment is similar to the valve device 20B of the embodiment shown in FIG. 5, and the same components are denoted by the same reference numerals, description thereof is omitted, and only different components are described. . The valve device 20E of the present embodiment has a configuration in which the electromagnetic solenoid 90 is removed from the configuration of the valve device 20B of FIG. 5 in the same manner as the valve device 20D of FIG. About another structure, it is the same as that of the valve apparatus 20B of FIG. 5, and effects other than the effect relevant to the electromagnetic solenoid 90 can be achieved similarly to the valve apparatus 20B of FIG.
[0103]
FIG. 9 is a diagram illustrating an example of a classification of a tank built-in type valve device provided in the tank 200. The tank built-in

type valve devices

20, 20A to 20E are roughly classified into an electromagnetic type and a manual type. Both the electromagnetic type and the manual type can be further divided into those with a pressure cancellation mechanism and those without a pressure cancellation mechanism. In the electromagnetic type, both with a pressure canceling mechanism and without a pressure canceling mechanism can be divided into those with an emergency manual handle and those without an emergency manual handle.
[0104]
The valve device 20 shown in FIGS. 1 to 3 corresponds to a valve device that is electromagnetic and has an emergency manual handle with a pressure canceling mechanism. The valve device 20A in FIG. 4 corresponds to a valve device with an emergency manual handle that is electromagnetic and has a pressure canceling mechanism. The valve device 20B of FIG. 5 corresponds to a valve device of an electromagnetic type and without an emergency manual handle without a pressure canceling mechanism. The valve device 20C in FIG. 6 corresponds to a valve device with an emergency manual handle that is electromagnetic and does not have a pressure canceling mechanism. The valve device 20D of FIG. 7 is a manual type and corresponds to a valve device with a pressure cancellation mechanism. The valve device 20E of FIG. 8 corresponds to a manual valve device without a pressure cancellation mechanism.
[0105]
FIG. 10 is a diagram illustrating an example of classification of in-line type valve devices provided in the middle of the pipe 150. Although each

valve device

20 and 20A-20E demonstrated with reference to FIGS. 1-9 was provided in the tank 80, you may make it provide a valve device in the middle of piping. The in-line type valve devices 20F to 20K are also roughly classified into electromagnetic types and manual types. Both the electromagnetic type and the manual type can be further divided into those with a pressure cancellation mechanism and those without a pressure cancellation mechanism. In the electromagnetic type, both with a pressure canceling mechanism and without a pressure canceling mechanism can be divided into those with an emergency manual handle and those without an emergency manual handle.
[0106]
The valve device 20F in FIG. 11 corresponds to a valve device that is electromagnetic and has an emergency manual handle with a pressure canceling mechanism. The valve device 20G in FIG. 12 corresponds to a valve device with an emergency manual handle that is electromagnetic and has a pressure canceling mechanism. The valve device 20H of FIG. 13 corresponds to a valve device of an electromagnetic type and without an emergency manual handle without a pressure canceling mechanism. The valve device 20I in FIG. 14 corresponds to a valve device with an emergency manual handle that is electromagnetic and has no pressure canceling mechanism. The valve device 20J in FIG. 15 is a manual type and corresponds to a valve device with a pressure cancellation mechanism. The valve device 20K in FIG. 16 corresponds to a manual valve device without a pressure canceling mechanism. In such an in-line type valve device having a pressure cancellation mechanism, the housing main body 25 for guiding the primary pressure P1 to the open / close back pressure chamber 106 is used to cancel the primary pressure P1 in the open / close valve portion. The communication passage 107 is configured to connect the valve body chamber 97 and the open / close back pressure chamber 106.
[0107]
These in-line type valve devices 20F to 20K are not provided in the tank 200 but are provided in the middle of the pipe, the primary side portion of the pipe 150 is connected to the primary port 28, and the secondary side of the pipe 150 is connected to the secondary port 30. The parts are connected. The other in-line type valve devices 20F to 20K have the same configuration as the corresponding classification of the tank built-in

type valve devices

20 and 20A to 20E, and can achieve the same effects.
[0108]
FIG. 17 is a cross-sectional view showing a valve device 20L according to another embodiment of the present invention. The valve device 20L of the present embodiment is similar to the valve device 20 of the embodiment shown in FIGS. 1 to 3, and the same configuration is denoted by the same reference numeral, description thereof is omitted, and different configurations are provided. Just explain. In the valve device 20L of the present embodiment, instead of the electromagnetic solenoid 90 of the valve device 20 of FIGS. 1 to 3, an electromagnetic solenoid 90L that is driven not from the device axis L1 but from a direction intersecting the device axis L1 is used. Provided.
[0109]
In the valve device 20L, an operating piece housing portion 160 in which the other axial end portion 101 of the shaft body 88 is disposed is formed at the other axial end portion of the housing 21, and an L-shaped operating piece 161 is accommodated. Yes. The operating piece 161 is held at one end so as to be freely angularly displaceable around an angular displacement axis L2 perpendicular to the device axis L1.
[0110]
The electromagnetic solenoid 90L is disposed on the outer side of the housing 21 and is provided on the outer peripheral portion. The electromagnetic solenoid 90L is a solenoid that intersects the device axis L1, specifically, is perpendicular to the device axis L1 and perpendicular to the angular displacement axis L2. A drive member 164 that is displaceable along the axis and a drive coil are provided. The electromagnetic solenoid 90L displaces the drive member 164 along the solenoid axis by switching between energization and de-energization of the drive coil, and the drive member 164 causes the operating piece 161 to be angularly displaced. This is an electromagnetic driving force that presses and moves the valve body 95 along the device axis L1 in the axial direction, specifically, in the direction toward the other X2 in the axial direction, and the valve body 95 is seated. An electromagnetic driving force in the opening direction that is separated from 112 can be applied to the open / close piston 85.
[0111]
In such a configuration, the dimension in the direction of the apparatus axis L1 can be further reduced by shifting the electromagnetic solenoid 90L in the radial direction. Further, the distance between the input position (force point) to the operating piece 161 by the driving member 164 and the angular displacement axis (fulcrum) of the operating piece 161 is the pressing position (operating point) at which the operating piece 161 presses the shaft body 88 and the operating piece. 161 is larger than the distance from the angular displacement axis. Thus, according to this principle, the electromagnetic force of the electromagnetic solenoid 90L can be amplified and applied to the shaft body 88. As a result, the electromagnetic solenoid 90L can be further reduced in size.
[0112]
The other configuration of the valve device 20L shown in FIG. 17 is the same as that of the valve device 20 of FIGS. 1 to 3 and achieves the same effect.
[0113]
The above-described embodiment is merely an example of the present invention, and the configuration can be changed within the scope of the present invention. For example, in the

valve devices

20A, 20B, 20C, 20F, 20G, 20H, and 20I shown in FIGS. 4, 5, 6, 11, 12, 13, and 14, the electromagnetic solenoid 90 is replaced by the electromagnetic solenoid shown in FIG. The solenoid 90L may be used instead. Moreover, the housing 21 and the cylindrical member 24 may be integrally formed. Further, the use may be provided in a high-pressure tank other than the tank carried by the above-mentioned firefighter, for example, in a tank containing gas for constituting a fuel cell mounted on an electric vehicle or the like. Moreover, you may make it provide in fluid pressure apparatuses other than a tank. The fluid may be a gas or a liquid.
[0114]
【The invention's effect】
According to the first aspect of the present invention, it is possible to realize a small valve device by reducing the axial dimension and the radial dimension. Moreover, handling becomes easy. Further, by making it small in size, it does not vibrate greatly even if vibration is applied from the outside, and the vibration resistance can be increased. For example, it can be suitably used for a portable pressure device and pressure vessel. In addition, by making it small, it can be easily built into the high-pressure vessel when it is installed in the high-pressure vessel, and there is no need to provide piping for the high-pressure fluid to flow outside the high-pressure vessel. Can be achieved. For example, when a pressure reducing valve is built in a high pressure vessel such as a high pressure tank, it is necessary to keep the outer diameter of the high pressure vessel small from the viewpoint of the strength of the high pressure vessel. It can be used suitably. Further, the overall mass can be reduced, and this also facilitates handling. In addition, with the integrated structure as described above, the number of parts of the valve device can be reduced, and the manufacturing cost can be reduced.
[0115]
According to the second aspect of the present invention, the change amount of the secondary pressure with respect to the change amount of the primary pressure can be significantly reduced. Moreover, even when the maximum allowable flow rate is large, the radial dimension can be kept small and the amount of change in the secondary pressure can be kept small. Therefore, it is possible to obtain a valve device including a pressure reducing valve portion that is extremely convenient.
[0116]
According to the third aspect of the present invention, even if the primary pressure is increased, it is not necessary to increase the driving force applied to the open / close piston by the open / close drive means. Further, the maximum allowable flow rate can be increased without increasing the driving force applied to the open / close piston by the open / close drive means. Therefore, it is possible to obtain a valve device having an extremely convenient on-off valve portion.
[0117]
According to the fourth aspect of the present invention, in a state where the on-off valve portion is closed, a high-pressure primary pressure does not act on the pressure reducing valve portion, and durability can be increased. Moreover, even if the on-off valve portion is opened after leaving the on-off valve portion closed for a long time, high-pressure gas is prevented from being discharged.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a valve device 20 according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view for explaining the dimensions of each part of the valve device 20;
FIG. 3 is a graph showing a secondary pressure P2 of the valve device 20;
FIG. 4 is a cross-sectional view showing a valve device 20A according to another embodiment of the present invention.
FIG. 5 is a cross-sectional view showing a valve device 20B according to still another embodiment of the present invention.
FIG. 6 is a cross-sectional view showing a valve device 20C according to still another embodiment of the present invention.
FIG. 7 is a cross-sectional view showing a valve device 20D according to still another embodiment of the present invention.
FIG. 8 is a cross-sectional view showing a valve device 20E according to still another embodiment of the present invention.
FIG. 9 is a diagram showing an example of a classification of a tank built-in type valve device provided in the tank 80;
10 is a diagram showing an example of classification of in-line type valve devices provided in the middle of a pipe 150. FIG.
FIG. 11 is a cross-sectional view showing a valve device 20F according to still another embodiment of the present invention.
FIG. 12 is a sectional view showing a valve device 20G according to still another embodiment of the present invention.
FIG. 13 is a cross-sectional view showing a valve device 20H according to still another embodiment of the present invention.
FIG. 14 is a cross-sectional view showing a valve device 20I according to still another embodiment of the present invention.
FIG. 15 is a sectional view showing a valve device 20J according to still another embodiment of the present invention.
FIG. 16 is a cross-sectional view showing a valve device 20K according to still another embodiment of the present invention.
FIG. 17 is a cross-sectional view showing a valve device 20L according to still another embodiment of the present invention.
18 is a cross-sectional view showing a conventional valve device 1. FIG.
FIG. 19 is a configuration circuit diagram showing the valve device 1;
FIG. 20 is a cross-sectional view schematically showing a configuration of a pressure reducing valve portion 3 of a conventional technique in a simplified manner.
FIG. 21 is a graph showing a secondary pressure p2 of the pressure reducing valve portion 3 of the prior art.
[Explanation of symbols]
20, 20A-20L valve device
21 Housing
22 decompression piston
23 Pressure reducing spring member
24 Tubular member
28 Primary port
30 Secondary port
55 Depressurized back pressure chamber
63 Orifice
85 Open / close piston
86 Opening and closing drive means
106 Open / close back pressure chamber

Claims

A housing in which primary and secondary ports are formed;
A pressure reducing valve portion provided in the housing and configured to reduce the secondary pressure of the fluid in the secondary port more than the primary pressure in the primary port;
A valve device comprising an on-off valve portion that is provided by coaxially inserting a pressure reducing valve portion and switches a connection state between a primary port and a secondary port between an open state and a closed state.

The pressure reducing valve is
The housing is slidably held in the axial direction, and the housing is partitioned into a primary pressure chamber connected to the primary port and a secondary pressure chamber connected to the secondary port. A primary pressure receiving surface that receives the primary pressure, a back pressure receiving surface that receives the primary pressure from the fluid in the decompression back pressure chamber held in the primary pressure in the axial direction to the other in the axial pressure receiving area, and a secondary pressure. A pressure-reducing piston formed with a secondary pressure receiving surface that receives a secondary pressure from the fluid in the chamber toward the other axial direction;
2. The valve device according to claim 1, further comprising a decompression spring force generating means for applying a decompression spring force directed in one axial direction to the decompression piston.

The on-off valve is
An open / close piston that is held in a housing so as to be displaceable in an axial direction, and that switches between a connection state between a primary port and a secondary port by being seated and separated from a valve seat formed in the housing. A closed pressure receiving surface that receives the primary pressure in the direction in which it is seated in the closed pressure receiving area, and an open / close pressure surface that receives the primary pressure in the direction away from the valve seat from the valve seat in the same open pressure area as the closed pressure receiving area. A piston,
3. An opening / closing drive means for applying an axial driving force to the opening / closing piston to switch the connection state between the primary port and the secondary port between an open state and a closed state. The valve device described.

The valve device according to any one of claims 1 to 3, wherein the open / close position of the flow path in the open / close valve portion is arranged on the upstream side in the fluid flow direction compared to the reduced pressure position in the pressure reducing valve portion. .