JP4462858B2

JP4462858B2 - Automatic adjustment valve device

Info

Publication number: JP4462858B2
Application number: JP2003203423A
Authority: JP
Inventors: 邦雄小倉; 正博河本; 浩一政重; 研二高橋
Original assignee: 株式会社横田製作所
Priority date: 2003-07-29
Filing date: 2003-07-29
Publication date: 2010-05-12
Anticipated expiration: 2023-07-29
Also published as: JP2005048796A

Description

【０００１】
【発明の属する技術分野】
本発明は、流体輸送管路に設置する自動調整弁装置に関するものであり、より詳しくは、主弁上流側の管路内圧力を自動的に所定値に維持する１次圧力調整弁に関するものである。なお、本明細書中、「水」や「液」の語は流体を総称的に代表するものとする。
【０００２】
【従来の技術】
従来から、中高層ビルの空調、冷暖房設備においては、地下に設置された熱交換器によって製造された冷水や温水を、ポンプによって各階の空調機器に循環させることが、一般的に行われている。
その一例として、循環回路が開放回路（回路の一部が大気開放されている）の場合を示したのが図８である。この場合、各階の空調機器１０１の温度コントロール（空調機器１０１に付随する開閉弁１０２の開閉調節）によって循環回路の負荷が変動しても、熱交換器１０３やポンプ１０４が定流量で運転できるようにしておくことが必要であり、このため、循環回路の往路１０７と帰路１０８の圧力を一定に保つための装備として、往路１０７と帰路１０８にそれぞれ１次圧力調整弁を設置することが多い。
【０００３】
このうち、往路１０７側に設置する１次圧力調整弁Ｖ’は、ポンプ１０４の運転中に所定限度を超えた圧力上昇分を循環回路外に逃がして、往路１０７内の圧力を一定に保つという役割があるので、一般的に「リリーフ弁」とも称されており、一方、帰路１０８側に設置する１次圧力調整弁Ｖは、ポンプ１０４の運転中に各階の空調機器１０１経過後の帰路１０８の圧力を一定に保つという役割と共に、ポンプ１０４の停止時に帰路１０８中の冷温水が地下の貯液槽１１０に抜け落ちるのを防止し、ひいてはポンプ１０４の再起動時の配管ウォーターハンマーを防止するという役割もあるので、一般的に「落水防止弁」とも称されている。
【０００４】
従来から一般的に、１次圧力調整弁としては、主弁上流側の管路内圧力（１次圧力）を検知し、例えばニードル弁のような固定的な絞り調節流路で流量を絞りながら作用させたパイロット弁によって、主弁駆動用のピストンやダイヤフラムを作動させる構造のものが広く用いられて来た。
【０００５】
従来の１次圧力調整弁の典型的な構成は、図９に示したように、主弁装置Ｍにおいては、入口流路ａと出口流路ｃとその連通流路中に主弁座４を備えた主弁箱１の内部に、一体的に組み合わされた主弁体５と該主弁体５より大きい受圧面積を持つ主弁駆動部材６とが主弁軸７を介して進退自在に設けられ、主弁駆動部材６は主弁箱の円筒状壁部３に対して滑動自在に嵌装されて、該壁部３及び主弁箱蓋２との間に主弁駆動圧力室ｄを形成し、そして、主弁上流側圧力が所定値より高くなれば開通し、低くなれば閉鎖するパイロット弁装置Ｐが付設され、主弁駆動圧力室ｄは、固定絞り調節弁１０を介して主弁上流側の入口流路ａに連通されると共に、パイロット弁装置Ｐを介して主弁下流側の出口流路ｃに連通されている。パイロット弁装置Ｐにおいては、受圧板を挟んだ一方には主弁上流側圧力が導入され、反対側には所定圧力手段としてのばねが装着されて、その主弁上流側圧力とばね付勢力とのバランスによって作動する弁体がパイロット流路を開閉するようになっている。
そしてこの構成によって、主弁上流側圧力が所定値より高くなった場合には、パイロット弁装置Ｐが開通し、主弁駆動圧力室ｄの内圧が主弁下流側圧力に向かって低下し、主弁体５が開弁作動し、一方、主弁上流側圧力が所定値より低くなった場合には、パイロット弁装置Ｐが閉鎖し、主弁駆動圧力室ｄの内圧が主弁上流側圧力に向かって上昇し、主弁体５が閉鎖作動し、これらの自動開閉作動によって主弁装置Ｍの通過流量を調節して主弁上流側圧力を一定に保つというものである。
【０００６】
【発明が解決しようとする課題】
しかし、この従来技術による１次圧力調整弁には、次のような問題がある。
（１）主弁駆動部材６が円筒状壁部３に接する部分のシール部材６ｓは、主弁締切り時において漏れを許さない完璧な密封性を要する構造のものが多く、種々のシール手段を追求し、更にベローズやダイヤフラム等を採用してその課題を解決しようとしているが、特に大型化・高圧化するほど、シール部分の耐久性や加工精度に困難を生じ、また、保守管理上も煩わしさが残る。即ち、主弁締切り時の下流側への液漏れが発生しやすい。
（２）１次圧力調整中の急激な流動変化による圧力脈動の影響（いわゆる「チャタリング」や「ハンチング」）を防止するために、従来技術のものでは、主弁上流側の液を導入する連通路の途中に、例えばニードル弁のような固定絞り調節弁１０を必要とし、この固定した精細な流路がスケール・異物等の目詰まり事故の原因となる。そのためにストレーナー等が必要で、清浄液以外では扱いにくいものである。
（３）所定の１次圧力を設定するための調節が、ニードル弁等の固定絞り調節弁１０とパイロット弁装置Ｐの２箇所の兼ね合いを見ながらの調節となり、運転・保守管理上の手が掛かる。
（４）主弁駆動圧力室ｄの圧力増減制御は、専らパイロット弁装置Ｐを介して出口流路ｃに排出するパイロット液の増減制御によってなされており、その間も、固定絞り調節弁１０を介して入口流路ａから常にパイロット液が流入しているため、主弁駆動圧力室ｄの圧力増減制御が迅速には行いにくい。
（５）しかも、この固定絞り調節弁１０を介して流入している流量は、少量に固定されているから、前述のようなポンプ停止時に管内水の抜け落ち防止のために急速に主弁を閉鎖しなくてはならない場合には、主弁駆動圧力室ｄへのパイロット液の供給が遅すぎて対応できず、「落水防止」という要求を満たすことができない。
【０００７】
なお、このパイロット弁装置と主弁装置を一体化した「直動型」の１次圧力調整弁も広く用いられているが、この直動型においても、同様の技術的思想に依拠しているため、やはり上記（１）〜（５）の問題を有している。
【０００８】
上記問題の内の（５）の点に関しては、ポンプ停止時の主弁閉鎖時間を短縮する方法として、図１０に示したような、主弁駆動圧力室ｄへのパイロット液の補給を行うサブパイロット弁装置Ｓを追加装備したものも広く使用されている。
即ち、主弁駆動圧力室ｄは、固定絞り調節弁１０よりも大きい通路を備えたサブパイロット弁装置Ｓを介して主弁上流側の入口流路ａに連通されている。サブパイロット弁装置Ｓにおいては、受圧板を挟んだ一方には主弁上流側圧力が導入され、反対側には所定圧力手段としてのばねが装着されて、その主弁上流側圧力とばね付勢力とのバランスによって作動する弁体がパイロット流路を開閉するようになっている。
そしてこの構成によって、主弁上流側圧力が所定値より高い場合には、サブパイロット弁装置Ｓが閉鎖状態を維持しているが、主弁上流側圧力が所定値より低くなった場合には、サブパイロット弁装置Ｓが開通し、その通過流量が固定絞り調節弁１０よりも大きいことから主弁駆動圧力室ｄの内圧が主弁上流側圧力に向かって速く上昇し、主弁体５が速く閉鎖作動して、落水防止の機能を果たすというものである。
【０００９】
しかし、この装置は、追加のサブパイロット弁装置Ｓを十分に大きくするならば上記（５）の問題を一応解決できるとはいうものの、スペースをとる上、このサブパイロット弁装置Ｓによるパイロット液の補給が、上記（２）に述べた固定絞り調節弁１０によるパイロット液の流入規制の効果を減殺してチャタリングやハンチングを引き起こす原因となりかねないため、安定的な運転のためには、サブパイロット弁装置Ｓの圧力設定や流量設定が極めて微妙となるなどの煩わしさが残る。そして、いずれにしても、残る（１）〜（４）の問題は未解決のまま残している。
【００１０】
そこで、本発明は、１次圧力調整弁としての優れた自動調整機能を発揮するのみならず、締切り密封機能も完璧であり、パイロット弁装置部からニードル弁等の固定的な絞り調節流路を排除し、パイロット弁装置部の自掃作動による目詰まり防止機能も備え、作動が迅速でありながらチャタリングやハンチングが起こりにくく、更には、給液ポンプの停止などによって主弁上流側圧力が急速に低下した場合にはただちに閉鎖して液の流過を阻止する「落水防止弁」としての機能も発揮する、取扱い簡単で便利な自動調整弁装置を得ることを目的とする。
【００１１】
【課題を解決するための手段】
上記の目的を達成するために、本発明は、
主流路を開閉する主弁装置がパイロット弁装置に連係して駆動される自動調整弁装置において、
主弁装置は、主弁箱の内部に一体的に組み込まれた主弁体と該主弁体より大きい受圧面積を持つ主弁駆動部材とを備え、主弁体は主弁座の上流側に位置して、主弁座との間に絞り流路を形成し、主弁駆動部材は主弁箱の円筒状壁部に対して滑動自在に嵌装されて、該壁部との間に主弁駆動圧力室を形成し、
パイロット弁装置は、
前記主弁装置の上流側圧力と所定圧力手段との対向作用力のバランスによって作動し、主弁上流側圧力が所定値より高くなれば閉鎖し、低くなれば開通するパイロットＡ弁装置と、
前記主弁装置の上流側圧力と所定圧力手段との対向作用力のバランスによって作動し、主弁上流側圧力が所定値より高くなれば開通し、低くなれば閉鎖するパイロットＢ弁装置と、
前記主弁装置の上流側圧力と所定圧力手段との対向作用力のバランスによって作動し、主弁上流側圧力が所定値より高くなれば閉鎖し、低くなれば開通するパイロットＣ弁装置とからなり、
前記パイロットＡ弁装置と前記パイロットＢ弁装置とが、中間に前記主弁駆動圧力室を介して、前記主弁装置の上流側と下流側との間に連通路によって直列的に連通されると共に、前記主弁装置の主流路と前記主弁駆動圧力室との間に更に設けられた連通路中に前記パイロットＣ弁装置が介設されたことを特徴とする。
【００１２】
この発明においては、前記パイロットＡ弁装置と前記パイロットＢ弁装置の両弁体が同軸上に設けられ、前記主弁装置の上流側圧力と１個の所定圧力手段との対向作用力のバランスによって、両弁体が連動して作動する構造に構成されてもよい。
又、前記パイロットＡ弁装置、前記パイロットＢ弁装置、前記パイロットＣ弁装置の３弁体が同軸上に設けられ、前記主弁装置の上流側圧力と１個の所定圧力手段との対向作用力のバランスによって、３弁体が連動して作動する構造に構成されてもよい。
【００１３】
上記の構成に基づいて、本発明の自動調整弁装置は、主弁装置の上流側圧力の変化によって開閉するパイロットＡ弁装置とパイロットＢ弁装置とが、連動作動を行い、主弁駆動圧力室の内圧を適宜に増減して、主弁体の開度を調整しながら通過流量を自動制御し、１次圧力調整弁としての優れた自動調整機能を発揮する。又、締切り密封性も容易に達成できる。
又、パイロットＡ弁装置、Ｂ弁装置のいずれにもニードル弁等の固定的な絞り調節流路がないので、スケール・異物等による目詰まりは発生しにくく、又、万一目詰まりが発生しても、その目詰まりによって生ずる圧力変化によって、その弁体が自動的に開弁する自掃作動を行い、目詰まりを排除するという機能も備えている。
又、パイロットＡ弁装置、Ｂ弁装置の両弁体が一体的に連動して、パイロット弁装置内で主弁上流側圧力と主弁下流側圧力の混合を行い、その合成圧力を主弁駆動圧力室に送り込んで流況変化に速やかに対応する仕組みとなっているので、作動が迅速である。しかも、チャタリングやハンチングが発生しにくい。
【００１４】
そして、給液ポンプの停止などによって主弁上流側圧力が急速に低下した場合には、パイロットＡ弁装置、Ｂ弁装置、Ｃ弁装置の協動により、主弁をただちに閉鎖して、液の流過を阻止する「落水防止弁」としての機能を発揮する
【００１５】
【発明の実施の形態】
本発明の詳細を、実施例を示した図面に基づいて説明する。
なお、以下便宜上の用語として、パイロットＡ弁装置は「Ａ弁装置」、その弁体は「Ａ弁体」、パイロットＢ弁装置は「Ｂ弁装置」、その弁体は「Ｂ弁体」、パイロットＣ弁装置は「Ｃ弁装置」、その弁体は「Ｃ弁体」、主弁上流側圧力は「１次圧力」、主弁下流側圧力は「２次圧力」と呼称する。又、各図において共通の役割をする部材には共通の図面符号を付してある。
【００１６】
まず、第１実施例を示した図１に基づいて説明すると、その主弁装置Ｍの図においては、１は入口流路ａから出口流路ｃへの主流路を備えた主弁箱を示し、２は主弁箱蓋を示す。４は主弁座である。主弁箱１の中には、主弁座４に対して上流側に設けられた主弁体５と、主弁箱１の円筒状壁部３に対してシール部材６ｓ（このシールは逸流阻止程度の粗雑な密封性で充分である）を介して滑動自在に嵌装された主弁駆動部材６と、両部材５；６を一体的に組み合わせる主弁軸７とを備えている。この主弁軸７は軸受９によって進退自在に支持されている。そして、主弁駆動部材６と円筒状壁部３及び主弁箱蓋２に包まれて袋室状の主弁駆動圧力室ｄが形成されており、その内圧の増減により主弁体５が駆動され、主弁座４との間の主弁開口部ｂを開閉する。主弁体５と主弁駆動部材６との受圧面積の関係は、主弁駆動部材６の方を大きめに設定する。
なお、図中の主弁ばね８は、最初の通液時の主弁体５の作動の安定上は望ましいものではあるが、以後の作動には特に関係がないので省略してもよい。
【００１７】
そして、１次圧力の変化に対応して、その１次圧力が所定値より高くなれば閉鎖し、低くなれば開通するＡ弁装置と、１次圧力が所定値より高くなれば開通し、低くなれば閉鎖するＢ弁装置とが、その中間に主弁駆動圧力室ｄを介して、主弁上流側と主弁下流側との間に連通路によって直列的に連通され、更に、１次圧力が所定値より高くなれば閉鎖し、低くなれば開通するＣ弁装置が、主流路（本実施例においては主弁上流側）と主弁駆動圧力室ｄとの間に別途設けられた連通路中に介設されることによって、主弁駆動圧力室ｄが主弁駆動の作動圧力室として機能するよう構成されている。
【００１８】
パイロットＡ弁装置及びＢ弁装置の図においては、２１は弁箱、２２は弁箱蓋を示す。弁箱２１の中には、Ａ弁装置のＡ弁室ｆ、Ｂ弁装置のＢ弁室ｈ、Ａ弁装置とＢ弁装置の間の中間室ｇ、１次圧力室ｋが形成されている。Ａ弁室ｆの中にはＡ弁体２４が配設され、Ｂ弁室ｈの中にはＢ弁体２５が配設され、Ａ弁室ｆとＢ弁室ｈの間に中間室ｇが配設されている。そして、Ａ弁体２４とＢ弁体２５は同軸上にあって連動し、且つ、互いに相手の作動を妨げないよう、シリンダー・ピストン様式の弁開閉機構が適用されている。又、その作動時に、一方が開き一方が閉鎖するという状態のみならず、両弁体２４；２５共にほぼ閉鎖する状態も生み出し得る位置間隔に配設されている。２３は受圧板、２３ｓはシール部材、２６は両弁体２４；２５を受圧板２３と一体的に組み合わせる弁軸を示す。又、弁箱蓋２２の側には所定圧力手段としてのばね２７（例示したものは圧縮コイルばね）が付設されている。
なお、Ｂ弁体２５については、閉鎖時の厳密な密封性を示すため、シール部材が図示されている。そして、Ａ弁体２４については、閉鎖時の厳密な密封性は必要なく、幾分洩れ気味であってもよいことが図示されている。勿論、Ａ弁体２４にも厳密な密封性を付加しても何ら差し支えない。又、締切り密封機能を必要としない仕様の場合には、両弁体２４；２５共に、閉鎖時の厳密な密封性は必要ない。
【００１９】
１次圧力室ｋは連通路ｒにより入口流路ａの１次圧力に連通されている。Ａ弁室ｆは連通路ｐにより入口流路ａに連通され、中間室ｇは連通路ｍにより主弁駆動圧力室ｄに連通され、そしてＢ弁室ｈは連通路ｑにより出口流路ｃに連通されている。
【００２０】
パイロットＣ弁装置の図においては、３１は弁箱、３２は弁箱蓋を示す。弁箱３１の中には、Ｃ弁室ｉ、室ｊ、１次圧力室ｋ’が形成されている。Ｃ弁室ｉの中にはＣ弁体３４が配設されている。３３は受圧板、３３ｓはシール部材、３６はＣ弁体３４を受圧板３３と一体的に組み合わせる弁軸を示す。又、弁箱蓋３２の側には所定圧力手段としてのばね３７（例示したものは圧縮コイルばね）が付設されている。
Ｃ弁体３４については、シール部材が図示されており、Ｃ弁体３４の開閉作動を明解にするためにはこのようなシール部材を装着することが好ましいものの、主弁体５の閉鎖時の厳密な水密性は、主弁体５のシール部材５ｓとＢ弁体２５のシール部材によって達成されているので、このＣ弁体３４については、閉鎖時の厳密な密封性は必須ではなく、幾分洩れ気味であっても差し支えない。
【００２１】
１次圧力室ｋ’は連通路ｒ’により入口流路ａの１次圧力に連通されている。Ｃ弁室ｉは連通路ｐ’により入口流路ａに連通され、そして室ｊは連通路ｍ’により主弁駆動圧力室ｄに連通されている。この連通路配管は、逆向きに（即ちＣ弁室ｉを主弁駆動圧力室ｄに、室ｊを入口流路ａに）連通させてもよいことは勿論である。
【００２２】
なお、このＣ弁装置の弁体３４および連通路ｐ’；ｍ’は、Ａ弁装置；Ｂ弁装置の弁体２４；２５および連通路ｐ；ｍ；ｑよりも口径を大きく設定するほうが、本装置の「落水防止弁」としての明解な作動のためには好ましく、図中においても、連通路ｐ’；ｍ’の方を連通路ｐ；ｍ；ｑよりも太い一点鎖線にて表示している。
又、ばね２７；３７の力は、所要の１次圧力と均衡できる範囲値のものを選定しておくことは勿論であるが、本装置の明解な作動のためにはＣ弁装置のばね３７の設定圧力をＡ弁装置；Ｂ弁装置のばね２７の設定圧力よりも低めに設定しておくことが好ましい。
【００２３】
次に、本発明の作用について説明する。
図８に例示された循環回路（貯液槽１１０及び熱交換器１０３→ポンプ１０４、逆止弁１０５、開閉弁１０６等の送液機器→循環往路１０７→空調機器１０１、開閉弁１０２、空気抜き弁１０９等の各階設備→循環帰路１０８→貯液槽１１０及び熱交換器１０３）において、循環往路１０７と循環帰路１０８の圧力を一定に維持するために、往路１０７のバイパス配管と帰路１０８に第１実施例（図１）の自動調整弁装置をそれぞれ介設して、その作動を観察するものとする。
なお、ポンプ運転時には、帰路１０８側の弁装置Ｖはほぼ開弁しているのに対し、往路１０７側の弁装置Ｖ’はほぼ閉鎖しているのが通常状態であるから、両弁装置の設定１次圧力には若干の差を設けておく（Ｖ’の方をＶより高めにする）のが通常である。
【００２４】
まず、循環帰路１０８に介設された自動調整弁装置Ｖの方について観察する。
ポンプの運転を開始してから１次圧力が未だ所定値に達していない段階では、パイロットＡ弁装置；Ｂ弁装置においては、ばね２７の力が１次圧力室ｋの内圧（１次圧力）に勝っており、受圧板２３は、ばね２７が伸びる方向（即ち図中の右方向）に押されている。従って、Ａ弁体２４は開通、Ｂ弁体２５は閉鎖している。又、Ｃ弁装置においては、ばね３７の力が１次圧力室ｋ’の内圧（１次圧力）に勝っており、受圧板３３は、ばね３７が伸びる方向（即ち図中の下方向）に押されている。従って、Ｃ弁体３４は開通している。
これら弁体２４；２５；３４の働きにより、主弁駆動圧力室ｄは入口流路ａとは連通され、出口流路ｃとは遮断され、主弁駆動圧力室ｄの内圧は１次圧力となっているので、主弁体５はその前後面に作用する圧力の差によって閉鎖し、主弁体５のシール部材５ｓとＢ弁体２５のシール部材が密封性を保っている。
【００２５】
次に、１次圧力が上昇して所定値に達すると、パイロットＡ弁装置；Ｂ弁装置においては、１次圧力室ｋの内圧（１次圧力）が、ばね２７の力に勝ち、受圧板２３は、ばね２７を縮める方向（即ち図中の左方向）に押し返される。従って、Ａ弁体２４は閉鎖、Ｂ弁体２５は開通する。又、Ｃ弁装置においては、１次圧力室ｋ’の内圧（１次圧力）が、ばね３７の力に勝ち、受圧板３３は、ばね３７を縮める方向（即ち図中の上方向）に押し返される。従って、Ｃ弁体３４は閉鎖する。
これら弁体２４；２５；３４の働きにより、主弁駆動圧力室ｄは入口流路ａとはほぼ遮断され、出口流路ｃとは連通され、主弁駆動圧力室ｄの内圧は２次圧力に向かって低下するので、主弁体５とそれより大きい受圧面積を持つ主弁駆動部材６との面積差に伴う推力の差により、主弁体５は推し開かれ、流れは入口流路ａ→主弁開口部ｂ→出口流路ｃの方向に流動を始める。
【００２６】
１次圧力が所定値に達した後は、各階の空調機器での使用流量の多寡などにより変化する１次圧力の変化を受けて、Ａ弁体２４とＢ弁体２５が応動し、主弁駆動圧力室ｄの内圧を適宜に増減して、主弁体５の開度を調整しながら所定の１次圧力を維持する。
Ａ弁体２４とＢ弁体２５は、一本の弁軸２６上に揃えて設けられ、一個の所定圧力手段（ばね２７）に対して一体的に連動して、パイロット弁装置内で１次圧力と２次圧力の混合を行い、その合成圧力を主弁駆動圧力室ｄに送り込んで流況変化に速やかに対応するという、簡明かつ合理的な仕組みとなっており、このため作動が迅速である。しかも両弁体２４；２５は、作動時に、一方が開通し一方が閉鎖するという状態のみならず、両弁体共にほぼ閉鎖する状態も生み出し得る位置間隔に配設され、流況が安定しているときは、両弁体共にほぼ閉鎖の状態で安定する仕組みとなっており、このため、弁体が振動するチャタリングやハンチングは発生しにくい。これらによって、本装置は１次圧力調整弁としての優れた自動調整機能を発揮する。
【００２７】
Ａ弁装置；Ｂ弁装置のいずれにも、ニードル弁等の固定的な絞り調節流路がないので、スケール・異物等による目詰まりは発生しにくい。又、万一目詰まりが発生しても、その目詰まりによって生ずる圧力変化によって、その弁体２４；２５が自動的に開弁する自掃作動を行う。即ち、例えばＡ弁体２４に目詰まりが発生したとすると、連通路ｐから主弁駆動圧力室ｄへの１次圧力の導入が妨げられるので、主弁駆動圧力室ｄの内圧は低下し、主弁体５は開弁方向に作動して通過流量が増大し、それによって１次圧力が減少し、その結果、Ａ弁体２４が開弁方向に移動して、目詰まりを自動的に排除する。この自掃作動によって目詰まりを排除するという優れた機能を備えているので、細目のストレーナー等は不要であり、保守管理も容易である。
【００２８】
このＡ弁装置；Ｂ弁装置が１次圧力調整作動を行っているとき、Ｃ弁装置においては、Ｃ弁体３４は閉鎖状態を維持しており、Ａ弁体２４；Ｂ弁体２５の１次圧力調整作動には干渉しない。特に、前述のようにＣ弁装置のばね３７の設定圧力をＡ弁装置；Ｂ弁装置のばね２７の設定圧力よりも低めに設定しておくと、１次圧力に若干の変動があってもＣ弁体３４は確実に閉鎖状態を維持しているので、安定的かつ精妙な調整作動を行えるＡ弁装置；Ｂ弁装置に専ら１次圧力調整の役割を担わせることができ、スムーズな調整ができて好都合である。
【００２９】
ポンプの運転を停止したときには、１次圧力は急速に低下するが、このとき、パイロットＡ弁装置；Ｂ弁装置においては、受圧板２３は、ばね２７が伸びる方向（即ち図中の右方向）に押され、Ａ弁体２４は開通、Ｂ弁体２５は閉鎖する。又、Ｃ弁装置においては、受圧板３３は、ばね３７が伸びる方向（即ち図中の下方向）に押され、Ｃ弁体３４は開通する。
これら弁体２４；２５；３４の働きにより、主弁駆動圧力室ｄは入口流路ａとは連通され、出口流路ｃとは遮断され、主弁駆動圧力室ｄの内圧は１次圧力に向かって急速に上昇するので、主弁体５はただちに閉鎖し、液の流過を阻止する。
【００３０】
本発明においては、パイロットＡ弁装置；Ｂ弁装置が連動開閉するという構成によって、Ａ弁装置；Ｂ弁装置のみでも主弁閉鎖は十分に迅速に作動するものであるが、特にＣ弁装置を設けてあるので、このＣ弁装置がパイロット作動液を主流路（入口流路ａ）から一気に主弁駆動圧力室ｄに追加供給することとなり、極めて迅速に主弁閉鎖を行うことができ、「落水防止弁」として高度な性能を発揮することとなる。
なお、本発明におけるＣ弁装置は、既に主弁閉鎖を十分に迅速に作動させ得るＡ弁装置；Ｂ弁装置の働きを加勢するものであるから、従来技術の主弁閉鎖加速用サブパイロット弁装置に比べればコンパクトで済むことは言うまでもない。
【００３１】
主弁体５の閉鎖時に、厳密に密封性の機能を果たす部分は、主弁体５のシール部材５ｓとＢ弁体２５のシール部材であり、これらは従来技術によって容易に密封性を達成できる部材である。一方、主弁駆動部材６のシール部材６ｓその他のシール部材は、粗雑な密封性のままにしておいても、下流側への液漏れの原因とはならない。
【００３２】
以上の作動によって、循環帰路１０８に介設した自動調整弁装置Ｖは、各階の空調機器１０１経過後の帰路１０８の圧力を一定に保つという「１次圧力調整弁」としての優れた自動調整機能を果たすと共に、ポンプ１０４の停止時に帰路１０８中の冷温水が貯液槽１１０に抜け落ちるのを防止するという「落水防止弁」としての的確な機能も果たすものである。
【００３３】
なお、ばね２７；３７を調整ねじ２８；３８にてワンタッチで調整することにより、所要の圧力設定値を調整することができる。
又、連通路ｑ中に介設されている開閉弁２９は、パイロット弁装置の作動に拘わりなく別途強制的に主弁装置Ｍを閉鎖させたい場合に用いるもので、常時は開通状態にしておく。主弁装置Ｍを閉鎖させたい場合は、開閉弁２９を閉弁操作すればよく、それによって主弁駆動圧力室ｄの内圧は１次圧力に向かって上昇し、主弁体５を閉鎖させる。この開閉弁２９は、手動操作でもよいし、各種アクチュエーター等を用いて遠隔操作してもよい。一方、別途強制的に主弁装置Ｍを開弁させる必要がある場合は、図示は省略したが、主弁駆動圧力室ｄと出口流路ｃとの間に別途の開閉弁を介設しておき（常時は閉鎖状態にしておく）、それを開弁操作すればよい。
【００３４】
一方、図８に例示された循環往路１０７のバイパス配管に介設された自動調整弁装置Ｖ’の方は、帰路１０８側に介設された自動調整弁装置Ｖと同じ開閉作動を行うが、その役割は若干異なっており、主弁装置Ｍは上流側圧力（１次圧力）が所定値範囲に納まっているときにはほぼ閉鎖しているが、１次圧力が上昇して所定値を超えそうな状態になったときには、主弁体５が推し開かれ、流れが入口流路ａ→主弁開口部ｂ→出口流路ｃの方向に流れて、１次圧力の上昇を抑える。即ち、往路１０７内の所定値以上の圧力上昇分をバイパスして逃がす「リリーフ弁」の役割をすることによって、往路１０７内の圧力を一定に保つという「１次圧力調整弁」としての機能を果たす。
【００３５】
なお、往路１０７側は、帰路１０８側とは異なり、ポンプ停止時に往路１０７中の冷温水が貯液槽１１０に抜け落ちるのを防止するという「落水防止」の機能は逆止弁１０５によって容易に達成できるので、この自動調整弁装置Ｖ’には特にパイロットＣ弁装置が装着されていなくても用は足りることとなる。勿論、Ｃ弁装置が装着されていても差し支えないので、説明の簡単のために図８中では、帰路１０８側の弁装置Ｖと同型のものを例示している。
【００３６】
次に、その他の実施例について説明する。
図２の第２実施例は、第１実施例のＡ弁体２４とＢ弁体２５を中間室ｇの中に同居させたものである。その部分的変更に伴って、連通路配管も第１実施例のものとは若干異なっているが、その他の構成及び作用効果は第１実施例と同様なので、詳述は省略する。
なお、この図２中のＣ弁装置については、各室ｉ；ｊ内でＣ弁体３４周りに発生する偏圧を解消して、設定圧力に対してＣ弁装置を正確に反応作動させるために、弁軸３６およびＣ弁体３４を完全バランス構造にする一例が示してある。
【００３７】
図３の第３実施例は、第１実施例の主弁駆動部材６を、第１実施例のものとは逆に主弁座４の下流側に設け、ばね２７の作動方向を第１実施例のものとは逆向きにしたものである。それらの部分的変更に伴って、主弁駆動部材６及び主弁体５の作動方向が第１実施例のものとは逆向きになり（主弁体５は、主弁駆動圧力室ｄの内圧が１次圧力に向かって上昇したときに開弁し、内圧が２次圧力に向かって低下したときに閉鎖する）、Ａ弁装置とＢ弁装置の配置及び入口流路ａと出口流路ｃへの夫々の連通路配管も第１実施例のものとは逆になり、そして、Ｃ弁装置の設置位置も、連通路ｍ’；ｑ’を介して主弁駆動圧力室ｄと出口流路ｃとの間となる（落水防止の際は、Ｃ弁装置がパイロット作動液を主弁駆動圧力室ｄから一気に出口流路ｃに排出させることによって主弁体５を急閉鎖させることとなる）など、各構成要素の配設位置や作動方向が第１実施例の場合とは異なってくるが、その作用効果は第１実施例と同じであり、その他の構成も第１実施例と同様なので、詳述は省略する。
【００３８】
図４の第４実施例は、第１実施例のＡ；Ｂ弁装置とＣ弁装置とを向かい合わせに合体して、Ａ；Ｂ；Ｃ連合パイロット弁装置としたものである。但し、Ａ弁体２４；Ｂ弁体２５の弁軸２６とＣ弁体３４の弁軸３６とは、相互に独立した運動ができ、所要の圧力設定値も調整ねじ２８；３８によって夫々独立して調整できる構造にしてある。Ａ；Ｂ；Ｃ連合パイロット弁装置に合体したのに伴って、夫々の連通路配管も第１実施例のものとは若干異なっているが、その他の構成及び作用効果は第１実施例と同様なので、詳述は省略する。
【００３９】
図５の第５実施例は、第４実施例のＡ弁体２４とＢ弁体２５を中間室ｇの中に同居させたものである。その部分的変更に伴い、ばね２７の作動方向が第４実施例のものとは逆向きになり、連通路配管も第４実施例のものとは若干異なっているが、その他の構成及び作用効果は第４実施例と同様なので、詳述は省略する。
【００４０】
図６の第６実施例は、第４実施例のＡ；Ｂ；Ｃ連合パイロット弁装置の弁軸を１つにし、所定圧力手段も１つのものを共有させることによって、第４実施例のものと同様の機能を果たさせつつ、更にコンパクトな装置にしたものである。
Ａ弁体２４；Ｂ弁体２５；Ｃ弁体３４は同軸上に設けられ、１次圧力とばね２７との対向作用力のバランスによって、この３弁体２４；２５；３４が連動して作動し、且つ互いの作動を妨げない仕組みとなっている。即ち、Ｃ弁体３４及び対応する弁座もシリンダー・ピストン様式としてある。又、前述のように、Ｃ弁体３４の作動のための圧力設定値は、Ａ弁体２４；Ｂ弁体２５の圧力設定値とは若干の差異をもたせるのが通常であるが、本実施例においては、その差異は、Ｃ弁体３４の開閉位置とＡ弁体２４；Ｂ弁体２５の開閉位置に若干の「ずれ」を設けることによって実現している。この「ずれ」の度合は、ねじ等によって調整可能にしてもよいことは勿論である。
以上によって、第４実施例のものと同様の制御が可能となるものである。その他の構成及び作用効果は第４実施例と同様なので、詳述は省略する。
【００４１】
図７の第７実施例は、第６実施例のＡ弁体２４とＢ弁体２５を中間室ｇの中に同居させたものである。その部分的変更に伴い、ばね２７の作動方向が第６実施例のものとは逆向きになり、連通路配管も第６実施例のものとは若干異なっているが、その他の構成及び作用効果は第６実施例と同様なので、詳述は省略する。
なお、この図７には、主弁体５と主弁駆動部材６を一体構造にした例が図示され、又、点検・保守等のために主弁駆動圧力室ｄの中の水抜きを適時に行えるように、開閉弁１１付きのサイフォン配管を付設した例も図示されている。
【００４２】
次に、本発明の各実施例に共通の事項について説明する。
パイロットＡ弁装置；Ｂ弁装置については、いずれの実施例においても、Ａ弁体２４とＢ弁体２５が連動し、且つ、互いに相手の作動を妨げないようにする仕組みの一例として、シリンダー・ピストン様式の弁開閉機構が例示されているが、このシリンダー・ピストン様式以外の様式を用いてもよいし、Ａ弁装置；Ｂ弁装置を分けて弁体２４；２５を別個の弁軸上に夫々設けてもよい。
Ｃ弁装置についても同様に、Ａ弁装置；Ｂ弁装置と協動し、且つ、互いに相手の作動を妨げないよう、Ａ弁装置；Ｂ弁装置とは別個の弁軸上に設けてもよいし、図６〜図７のようなシリンダー・ピストン様式の弁開閉機構を用いてもよいし、目的に叶う適宜の様式を用いてよい。
Ａ弁装置；Ｂ弁装置；Ｃ弁装置いずれについても、弁体周りに発生する偏圧を解消して設定圧力に対して正確に反応作動させるために、図２のＣ弁装置において例示したような完全バランス構造を適用してもよい。
その他にも、パイロット弁装置の各室ｆ；ｇ；ｈ；ｉ；ｊ；ｋ；ｋ’の配置（位置関係）及び組み合わせ、それに伴う連通路配管等、この発明の趣旨の範囲内で設計変更可能であり、パイロット弁装置の構造を前記の各実施例に限定するものではない。
【００４３】
パイロット弁装置の所定圧力手段については、各実施例のようなばね２７；３７を用いる方法の他にも、他の弾性部材を用いたり、重錘にリンクしたり、倍力機構を付加したり、気圧、液圧装置等の適用が容易にできることは勿論である。
【００４４】
主弁装置Ｍについては、各実施例においては、主弁体５にリフト弁形式を適用しているが、この発明の趣旨の範囲内で、その他の形式の開閉弁（例えば、バタフライ弁、ゲート弁、ボール弁等）を適用してもよい。又、図７に例示したような主弁体５と主弁駆動部材６の一体構造を適用してもよい。なお、各実施例においては、主弁装置Ｍの構造を簡明にするために、ａ→ｂ→ｃの主流路部と主弁駆動圧力室ｄの両方を主弁箱１内にコンパクトに収めたものを図示したが、その他にも、この主流路部と主弁駆動圧力室ｄを、２つに分割した主弁箱の夫々に収め、この２つの弁箱を貫通させた主弁軸の両端に主弁体５と主弁駆動部材６を装着する等の構造にしても差し支えない。
【００４５】
仕様条件によっては、１次圧力調整作動中の不意の流動変化による圧力脈動の影響（チャタリングやハンチング）を防止する必要があるが、その対処方法の例として、各実施例に示したように、主弁開口部ｂの形状を流量変化をスムーズにする鋸歯状の流路としたり、その他にも、パイロットＡ弁装置；Ｂ弁装置に制動装置を設けたり、適宜にＡ弁装置；Ｂ弁装置の連通路を絞るなどしてもよい。なお、「落水防止弁」としての急閉鎖作動を阻害しない範囲で主弁装置Ｍを緩徐に作動させることが必要となる場合には、主弁装置Ｍに片効きの制動装置（主弁の開弁方向のみ制動）を設けてもよい。それらの対処方法は、いずれかを単独で採用しても、いくつかを組み合わせて採用してもよいし、それが必要とされない仕様条件下においては省略してもよい。
【００４６】
各実施例にわたり、密封性を要する箇所に装着されるシール部材については、現地の仕様に合わせて適宜にＯリング、シールリング、ダイヤフラム、ベローズ等を適用してよく、又、直接接触により良好な密封性を保持できる場合は、該シール部材を省略してもよい。なお、高速流が通過する可能性のある箇所には、キャビテーション防止等の目的で櫛歯状突起や整流格子等を形成してもよいことは勿論である。
その他、この発明における弁装置を構成する各部材にわたり、従来技術の援用は何ら妨げるものではなく、又、この発明の趣旨の範囲内で種々設計変更可能であり、この発明を前記の各実施例に限定するものではない。
【００４７】
【発明の効果】
本発明の自動調整弁装置は、１次圧力調整弁としての優れた自動調整機能を発揮するのみならず、締切り密封機能も完璧であり、又、パイロット弁装置部にニードル弁等の固定的な絞り調節流路がなく、且つパイロット弁装置部が目詰まりしてもその弁体が自動的に開弁する自掃作動を行うので、スケール・異物等による目詰まり事故を防止するメンテナンス・フリーの利点も備えている。又、作動が迅速でありながらチャタリングやハンチングが起こりにくい。更には、給液ポンプの停止などによって主弁上流側圧力（１次圧力）が急速に低下した場合にはただちに閉鎖して液の流過を阻止する「落水防止弁」としての的確な機能も発揮する。そして、パイロット弁装置部をはじめ構造が簡潔で、大型化や高圧化も容易であり、所要の１次圧力設定・調整もワンタッチで簡単に行なえ、設計・製作・運転・保守管理に苦慮すべき部分もなく、信頼性と経済性の高い便利な自動調整弁装置を得ることができたものであり、その実施効果は極めて大きい。
【図面の簡単な説明】
【図１】本発明の第１実施例を示す縦断面図である。
【図２】本発明の第２実施例を示す縦断面図である。
【図３】本発明の第３実施例を示す縦断面図である。
【図４】本発明の第４実施例を示す縦断面図である。
【図５】本発明の第５実施例を示す縦断面図である。
【図６】本発明の第６実施例を示す縦断面図である。
【図７】本発明の第７実施例を示す縦断面図である。
【図８】１次圧力調整弁の設置例を示す説明図である。
【図９】従来技術の１次圧力調整弁の一例を示す縦断面図である。
【図１０】従来技術の１次圧力調整弁の他の一例を示す縦断面図である。
【符号の説明】
Ｖ…自動調整弁装置Ｖ’…自動調整弁装置
Ｍ…主弁装置
１…主弁箱２…主弁箱蓋
３…円筒状壁部
４…主弁座５…主弁体５ｓ…シール部材
６…主弁駆動部材６ｓ…シール部材
７…主弁軸８…主弁ばね
９…軸受１０…固定絞り調節弁１１…開閉弁
Ａ…パイロットＡ弁装置Ｂ…パイロットＢ弁装置
２１…弁箱２２…弁箱蓋
２３…受圧板２３ｓ…シール部材
２４…Ａ弁体２５…Ｂ弁体
２６…弁軸２７…ばね２８…調整ねじ
２９…開閉弁
Ｃ…パイロットＣ弁装置
３１…弁箱３２…弁箱蓋
３３…受圧板３３ｓ…シール部材
３４…Ｃ弁体
３６…弁軸３７…ばね３８…調整ねじ
ａ…入口流路ｂ…主弁開口部
ｃ…出口流路ｄ…主弁駆動圧力室
ｆ…Ａ弁室ｇ…中間室ｈ…Ｂ弁室
ｉ…Ｃ弁室ｊ…室
ｋ；ｋ’…１次圧力室
ｍ；ｍ’；ｐ；ｐ’；ｑ；ｑ’；ｒ；ｒ’…連通路
Ｐ…パイロット弁装置Ｓ…サブパイロット弁装置
１０１…空調機器１０２…開閉弁
１０３…熱交換器１０４…ポンプ
１０５…逆止弁１０６…開閉弁
１０７…循環往路１０８…循環帰路
１０９…空気抜き弁１１０…貯液槽[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an automatic adjustment valve device installed in a fluid transportation pipeline, and more particularly to a primary pressure adjustment valve that automatically maintains a pressure in a pipeline on the upstream side of a main valve at a predetermined value. is there. In the present specification, the terms “water” and “liquid” generically represent fluids.
[0002]
[Prior art]
2. Description of the Related Art Conventionally, in air conditioning and heating / cooling facilities for high-rise buildings, it is common practice to circulate cold water or hot water produced by a heat exchanger installed underground to the air conditioning equipment on each floor by a pump.
As an example, FIG. 8 shows a case where the circulation circuit is an open circuit (a part of the circuit is open to the atmosphere). In this case, the heat exchanger 103 and the pump 104 can be operated at a constant flow rate even if the load on the circulation circuit fluctuates due to temperature control of the air conditioning equipment 101 on each floor (opening / closing control of the on / off valve 102 associated with the air conditioning equipment 101). For this reason, primary pressure regulating valves are often installed in the forward path 107 and the return path 108 as equipment for maintaining a constant pressure in the forward path 107 and the return path 108 of the circulation circuit.
[0003]
Among these, the primary pressure regulating valve V ′ installed on the forward path 107 side releases the pressure increase exceeding the predetermined limit during the operation of the pump 104 to the outside of the circulation circuit, and keeps the pressure in the forward path 107 constant. The primary pressure regulating valve V installed on the return path 108 side is generally referred to as a “relief valve” because of its role. In addition to keeping the pressure of the pump 104 constant, the hot and cold water in the return path 108 is prevented from dropping into the underground storage tank 110 when the pump 104 is stopped, thereby preventing a piping water hammer when the pump 104 is restarted. Since it also has a role, it is generally referred to as a “fall prevention valve”.
[0004]
In general, as a primary pressure regulating valve, a pressure in a pipe line (primary pressure) on the upstream side of a main valve is detected and the flow rate is throttled by a fixed throttle adjusting flow path such as a needle valve. A structure in which a piston or a diaphragm for driving a main valve is operated by an actuated pilot valve has been widely used.
[0005]
As shown in FIG. 9, a typical configuration of a conventional primary pressure regulating valve is such that, in the main valve device M, the main valve seat 4 is disposed in the inlet channel a, the outlet channel c, and the communication channel. A main valve body 5 and a main valve driving member 6 having a pressure receiving area larger than the main valve body 5 are provided in a main valve box 1 provided in an integrated manner through a main valve shaft 7 so as to freely advance and retract. The main valve driving member 6 is slidably fitted to the cylindrical wall portion 3 of the main valve box to form a main valve driving pressure chamber d between the wall portion 3 and the main valve box lid 2. A pilot valve device P is provided that opens when the pressure on the upstream side of the main valve becomes higher than a predetermined value and closes when the pressure becomes lower. The main valve driving pressure chamber d is connected to the main valve via the fixed throttle control valve 10. It communicates with the upstream inlet passage a and also with the outlet passage c downstream of the main valve via the pilot valve device P. In the pilot valve device P, the main valve upstream pressure is introduced into one side of the pressure receiving plate, and a spring as a predetermined pressure means is mounted on the opposite side, and the main valve upstream pressure and the spring biasing force are A valve element that operates according to the balance of the valve opens and closes the pilot flow path.
With this configuration, when the main valve upstream pressure becomes higher than a predetermined value, the pilot valve device P is opened, and the internal pressure of the main valve drive pressure chamber d decreases toward the main valve downstream pressure, When the valve body 5 is opened, on the other hand, when the main valve upstream pressure becomes lower than a predetermined value, the pilot valve device P is closed, and the internal pressure of the main valve driving pressure chamber d becomes the main valve upstream pressure. The main valve body 5 is closed, and the automatic valve opening / closing operation adjusts the flow rate of the main valve device M to keep the main valve upstream pressure constant.
[0006]
[Problems to be solved by the invention]
However, the conventional primary pressure regulating valve has the following problems.
(1) The seal member 6s where the main valve drive member 6 is in contact with the cylindrical wall portion 3 has many structures that require a perfect sealing property that does not allow leakage when the main valve is closed, and pursues various sealing means. In addition, we are trying to solve the problem by adopting bellows and diaphragms, but the larger the size and the higher the pressure, the more difficult the durability and processing accuracy of the seal part, and the more troublesome maintenance management is. Remains. That is, liquid leaks to the downstream side easily when the main valve is closed.
(2) In order to prevent the influence of pressure pulsation (so-called “chattering” or “hunting”) due to a sudden flow change during the primary pressure adjustment, the conventional technology uses a continuous introduction of liquid upstream of the main valve. A fixed throttle control valve 10 such as a needle valve is required in the middle of the passage, and this fixed fine flow path causes a clogging accident such as a scale or a foreign substance. For this reason, a strainer or the like is necessary, and it is difficult to handle other than the cleaning liquid.
(3) The adjustment for setting a predetermined primary pressure is an adjustment while observing the balance between the fixed throttle control valve 10 such as a needle valve and the pilot valve device P. It takes.
(4) The pressure increase / decrease control of the main valve drive pressure chamber d is performed exclusively by the increase / decrease control of the pilot liquid discharged to the outlet flow path c via the pilot valve device P, and during that time also via the fixed throttle control valve 10 Since the pilot liquid always flows from the inlet channel a, the pressure increase / decrease control of the main valve driving pressure chamber d is difficult to perform quickly.
(5) In addition, since the flow rate flowing through the fixed throttle control valve 10 is fixed to a small amount, the main valve is quickly closed to prevent the pipe water from falling off when the pump is stopped as described above. In the case where it is necessary to supply the pilot fluid to the main valve drive pressure chamber d, the supply of the pilot fluid is too slow to cope with it, and the requirement of “prevention of falling water” cannot be satisfied.
[0007]
A “direct acting” primary pressure regulating valve in which the pilot valve device and the main valve device are integrated is also widely used, but this direct acting type relies on the same technical idea. Therefore, it still has the problems (1) to (5).
[0008]
Regarding the point (5) among the above problems, as a method of shortening the main valve closing time when the pump is stopped, the sub-supply for supplying the pilot fluid to the main valve driving pressure chamber d as shown in FIG. Those equipped with an additional pilot valve device S are also widely used.
That is, the main valve drive pressure chamber d is communicated with the inlet flow path a on the upstream side of the main valve via the sub pilot valve device S having a passage larger than the fixed throttle control valve 10. In the sub-pilot valve device S, the main valve upstream pressure is introduced into one side of the pressure receiving plate, and a spring as a predetermined pressure means is mounted on the opposite side, and the main valve upstream pressure and the spring biasing force are installed. A valve element that operates according to the balance with the valve opens and closes the pilot flow path.
And, by this configuration, when the main valve upstream pressure is higher than a predetermined value, the sub pilot valve device S maintains a closed state, but when the main valve upstream pressure becomes lower than the predetermined value, Since the sub-pilot valve device S is opened and its passing flow rate is larger than that of the fixed throttle control valve 10, the internal pressure of the main valve drive pressure chamber d rises rapidly toward the upstream pressure on the main valve, and the main valve body 5 becomes faster. It closes and performs the function of preventing water fall.
[0009]
However, although this device can solve the problem (5) once if the additional sub-pilot valve device S is made sufficiently large, it takes up space and the pilot liquid by the sub-pilot valve device S can be reduced. Since replenishment may cause chattering and hunting by reducing the effect of the pilot fluid inflow restriction by the fixed throttle control valve 10 described in (2) above, the sub pilot valve is necessary for stable operation. Troubles such as the pressure setting and flow rate setting of the device S becoming very delicate remain. In any case, the remaining problems (1) to (4) remain unsolved.
[0010]
Therefore, the present invention not only exhibits an excellent automatic adjustment function as a primary pressure adjustment valve, but also has a perfect sealing function, and a fixed throttle adjustment flow path such as a needle valve is provided from the pilot valve device. Equipped with a function to prevent clogging due to the self-sweep operation of the pilot valve device part, chattering and hunting are unlikely to occur while the operation is quick, and the main valve upstream pressure is rapidly increased by stopping the feed pump, etc. The purpose is to obtain an easy-to-use and easy-to-use self-regulating valve device that also functions as a “falling prevention valve” that immediately closes to prevent the liquid from flowing through when it drops.
[0011]
[Means for Solving the Problems]
In order to achieve the above object, the present invention provides:
In the automatic adjustment valve device in which the main valve device that opens and closes the main flow path is driven in conjunction with the pilot valve device,
The main valve device includes a main valve body integrated into the main valve box and a main valve driving member having a larger pressure receiving area than the main valve body, and the main valve body is located upstream of the main valve seat. And a throttle flow path is formed between the main valve seat and the main valve drive member. The main valve drive member is slidably fitted to the cylindrical wall portion of the main valve box, and the main valve drive member is interposed between the main wall and the main valve seat. Forming a valve-driven pressure chamber,
The pilot valve device
A pilot A valve device that operates by the balance of the opposing acting force between the upstream pressure of the main valve device and the predetermined pressure means, and closes when the main valve upstream pressure becomes higher than a predetermined value, and opens when the pressure becomes lower;
A pilot B valve device that operates according to the balance of the opposing acting force between the upstream pressure of the main valve device and the predetermined pressure means, and opens when the main valve upstream pressure becomes higher than a predetermined value, and closes when the pressure becomes lower;
The pilot C valve device is operated by the balance of the counter acting force between the upstream pressure of the main valve device and the predetermined pressure means, and is closed when the main valve upstream pressure becomes higher than a predetermined value, and opened when the pressure becomes lower. ,
The pilot A valve device and the pilot B valve device are connected in series by a communication path between the upstream side and the downstream side of the main valve device via the main valve driving pressure chamber in the middle. The pilot C valve device is interposed in a communication path further provided between the main flow path of the main valve device and the main valve driving pressure chamber.
[0012]
In the present invention, both valve bodies of the pilot A valve device and the pilot B valve device are provided on the same axis, and the balance of the counter acting force between the upstream pressure of the main valve device and one predetermined pressure means is provided. The valve body may be configured to operate in conjunction with each other.
Further, the three valve bodies of the pilot A valve device, the pilot B valve device, and the pilot C valve device are provided on the same axis, and the opposing action force between the upstream pressure of the main valve device and one predetermined pressure means. Depending on the balance, the three valve bodies may be configured to operate in conjunction with each other.
[0013]
Based on the above configuration, in the automatic adjustment valve device of the present invention, the pilot A valve device and the pilot B valve device that are opened and closed by a change in the upstream pressure of the main valve device perform an interlocking operation, and the main valve drive pressure chamber The internal flow pressure is appropriately increased and decreased, and the passage flow rate is automatically controlled while adjusting the opening of the main valve body, thereby exhibiting an excellent automatic adjustment function as a primary pressure adjustment valve. Moreover, the cut-off hermeticity can be easily achieved.
Also, since neither the pilot A valve device nor the B valve device has a fixed throttle adjustment flow path such as a needle valve, clogging due to scale and foreign matter is unlikely to occur, and clogging may occur. However, it also has a function of eliminating clogging by performing a self-cleaning operation in which the valve body automatically opens due to a pressure change caused by the clogging.
In addition, the pilot A valve device and the B valve device are integrated together to mix the main valve upstream pressure and the main valve downstream pressure in the pilot valve device, and drive the resultant pressure to the main valve. The system is quick to respond to changes in flow conditions by sending it to the pressure chamber. In addition, chattering and hunting are less likely to occur.
[0014]
When the main valve upstream pressure drops rapidly due to the stoppage of the feed pump, etc., the main valve is immediately closed by the cooperation of the pilot A valve device, the B valve device, and the C valve device. Demonstrates the function of a “falling prevention valve” that prevents flowover
[0015]
DETAILED DESCRIPTION OF THE INVENTION
The details of the present invention will be described with reference to the drawings showing examples.
For convenience, the pilot A valve device is “A valve device”, the valve body is “A valve body”, the pilot B valve device is “B valve device”, the valve body is “B valve body”, The pilot C valve device is called “C valve device”, its valve body is called “C valve body”, the main valve upstream pressure is called “primary pressure”, and the main valve downstream pressure is called “secondary pressure”. In addition, members having a common role in the respective drawings are denoted by common drawing symbols.
[0016]
First, referring to FIG. 1 showing the first embodiment, in the figure of the main valve device M, 1 shows a main valve box having a main flow path from an inlet flow path a to an outlet flow path c. Reference numeral 2 denotes a main valve box lid. 4 is a main valve seat. In the main valve box 1, a main valve body 5 provided on the upstream side with respect to the main valve seat 4 and a seal member 6 s (this seal is a current flow) with respect to the cylindrical wall portion 3 of the main valve box 1. The main valve drive member 6 is slidably fitted via a main valve shaft 7 in which the two members 5; 6 are integrally combined. The main valve shaft 7 is supported by a bearing 9 so as to freely advance and retract. The main valve drive member 6, the cylindrical wall 3 and the main valve box cover 2 are wrapped to form a bag-like main valve drive pressure chamber d, and the main valve body 5 is driven by increasing or decreasing the internal pressure. Then, the main valve opening b between the main valve seat 4 is opened and closed. The relationship of the pressure receiving area between the main valve body 5 and the main valve driving member 6 is set so that the main valve driving member 6 is larger.
The main valve spring 8 in the figure is desirable for the stability of the operation of the main valve body 5 at the time of the first liquid passage, but may be omitted because it is not particularly related to the subsequent operation.
[0017]
In response to a change in the primary pressure, the A valve device is closed when the primary pressure becomes higher than a predetermined value, and opened when the primary pressure becomes lower, and opened when the primary pressure becomes higher than the predetermined value. In this case, the B valve device to be closed is communicated in series between the upstream side of the main valve and the downstream side of the main valve via the main valve driving pressure chamber d in the middle thereof, and further the primary pressure. The C valve device that closes when the pressure becomes higher than a predetermined value and opens when the pressure becomes lower is a communication path separately provided between the main flow path (in the present embodiment, the main valve upstream side) and the main valve driving pressure chamber d. By being interposed inside, the main valve drive pressure chamber d is configured to function as a main valve drive operating pressure chamber.
[0018]
In the drawings of the pilot A valve device and the B valve device, 21 indicates a valve box, and 22 indicates a valve box lid. In the valve box 21, an A valve chamber f of the A valve device, a B valve chamber h of the B valve device, an intermediate chamber g between the A valve device and the B valve device, and a primary pressure chamber k are formed. . An A valve body 24 is disposed in the A valve chamber f, a B valve body 25 is disposed in the B valve chamber h, and an intermediate chamber g is provided between the A valve chamber f and the B valve chamber h. It is arranged. The A-valve body 24 and the B-valve body 25 are coaxial and interlocked, and a cylinder / piston style valve opening / closing mechanism is applied so as not to interfere with each other's operation. Further, at the time of the operation, not only the state in which one is opened but the other is closed, as well as the state in which both the valve bodies 24; Reference numeral 23 denotes a pressure receiving plate, 23 s denotes a seal member, and 26 denotes a valve shaft for combining both valve bodies 24; 25 integrally with the pressure receiving plate 23. Further, a spring 27 (the illustrated example is a compression coil spring) as a predetermined pressure means is attached to the valve box cover 22 side.
In addition, about the B valve body 25, in order to show the exact sealing performance at the time of closing, the sealing member is illustrated. Further, it is shown that the A valve body 24 does not need to be strictly sealed when closed and may be somewhat leaky. Of course, there is no problem even if a strict sealing property is added to the A valve body 24. Further, in the case of a specification that does not require the shut-off sealing function, both the valve bodies 24; 25 do not require strict sealing when closed.
[0019]
The primary pressure chamber k communicates with the primary pressure of the inlet channel a through the communication path r. The A valve chamber f communicates with the inlet flow path a through the communication path p, the intermediate chamber g communicates with the main valve drive pressure chamber d through the communication path m, and the B valve chamber h communicates with the outlet flow path c through the communication path q. It is communicated.
[0020]
In the figure of the pilot C valve device, 31 indicates a valve box and 32 indicates a valve box lid. A C valve chamber i, a chamber j, and a primary pressure chamber k ′ are formed in the valve box 31. A C valve element 34 is disposed in the C valve chamber i. Reference numeral 33 denotes a pressure receiving plate, 33 s denotes a seal member, and 36 denotes a valve shaft that combines the C valve body 34 with the pressure receiving plate 33 integrally. A spring 37 (illustrated is a compression coil spring) as a predetermined pressure means is attached to the valve box cover 32 side.
For the C valve body 34, a seal member is shown, and in order to clarify the opening and closing operation of the C valve body 34, it is preferable to install such a seal member, but when the main valve body 5 is closed. Strict water tightness is achieved by the seal member 5s of the main valve body 5 and the seal member of the B valve body 25. Therefore, the strict sealability at the time of closing is not essential for the C valve body 34. It doesn't matter if it is leaking.
[0021]
The primary pressure chamber k ′ is communicated with the primary pressure of the inlet channel a through the communication path r ′. The C valve chamber i communicates with the inlet channel a through the communication passage p ′, and the chamber j communicates with the main valve drive pressure chamber d through the communication passage m ′. Of course, this communication pipe may be communicated in the opposite direction (that is, the C valve chamber i communicates with the main valve drive pressure chamber d and the chamber j communicates with the inlet channel a).
[0022]
The valve body 34 and the communication passage p ′; m ′ of the C valve device are set to have a larger diameter than the valve body 24; 25 and the communication passage p; m; q of the A valve device; This device is preferable for clear operation as a “falling prevention valve” of the present apparatus, and in the figure, the communication path p ′; m ′ is indicated by a dashed line thicker than the communication path p; m; q. ing.
Of course, the force of the springs 27 and 37 is selected so that the force can be balanced with the required primary pressure, but for the clear operation of the device, the spring 37 of the C valve device is used. Is preferably set lower than the set pressure of the spring 27 of the A valve device; B valve device.
[0023]
Next, the operation of the present invention will be described.
The circulation circuit illustrated in FIG. 8 (liquid storage tank 110 and heat exchanger 103 → pump 104, check valve 105, open / close valve 106 and other liquid feeding equipment → circulation forward path 107 → air conditioner 101, open / close valve 102, air vent valve 109, etc. → circulation return path 108 → storage tank 110 and heat exchanger 103), in order to keep the pressure of the circulation forward path 107 and the circulation return path 108 constant, the bypass pipe of the forward path 107 and the return path 108 are first The automatic adjustment valve device of the embodiment (FIG. 1) is interposed, and the operation thereof is observed.
During the pump operation, the valve device V on the return path 108 side is almost open, whereas the valve device V ′ on the forward path 107 side is almost closed. Usually, a slight difference is set in the set primary pressure (V ′ is made higher than V).
[0024]
First, the automatic adjustment valve device V provided in the circulation return path 108 is observed.
In the stage where the primary pressure has not yet reached the predetermined value since the start of the pump operation, in the pilot A valve device; the B valve device, the force of the spring 27 is the internal pressure (primary pressure) of the primary pressure chamber k. The pressure receiving plate 23 is pushed in the direction in which the spring 27 extends (that is, in the right direction in the figure). Accordingly, the A valve body 24 is opened and the B valve body 25 is closed. In the C valve device, the force of the spring 37 is greater than the internal pressure (primary pressure) of the primary pressure chamber k ′, and the pressure receiving plate 33 extends in the direction in which the spring 37 extends (ie, downward in the figure). It has been pushed. Therefore, the C valve body 34 is opened.
By the action of these valve bodies 24; 25; 34, the main valve drive pressure chamber d is communicated with the inlet flow path a, is disconnected from the outlet flow path c, and the internal pressure of the main valve drive pressure chamber d is the primary pressure. Therefore, the main valve body 5 is closed by the difference in pressure acting on the front and back surfaces thereof, and the seal member 5s of the main valve body 5 and the seal member of the B valve body 25 maintain the sealing performance.
[0025]
Next, when the primary pressure rises and reaches a predetermined value, in the pilot A valve device; B valve device, the internal pressure (primary pressure) of the primary pressure chamber k wins over the force of the spring 27, and the pressure receiving plate 23 is pushed back in the direction in which the spring 27 is contracted (that is, in the left direction in the figure). Therefore, the A valve body 24 is closed and the B valve body 25 is opened. Further, in the C valve device, the internal pressure (primary pressure) of the primary pressure chamber k ′ overcomes the force of the spring 37, and the pressure receiving plate 33 pushes the spring 37 in the contracting direction (that is, upward in the figure). returned. Therefore, the C valve body 34 is closed.
By the action of these valve bodies 24; 25; 34, the main valve driving pressure chamber d is substantially cut off from the inlet flow path a, and is communicated with the outlet flow path c. The internal pressure of the main valve driving pressure chamber d is the secondary pressure. Therefore, the main valve body 5 is pushed open by the difference in thrust due to the difference in area between the main valve body 5 and the main valve drive member 6 having a larger pressure receiving area, and the flow flows into the inlet channel a. → Starts flow in the direction of the main valve opening b → the outlet channel c.
[0026]
After the primary pressure reaches a predetermined value, the A valve body 24 and the B valve body 25 react in response to changes in the primary pressure that change due to the amount of flow used in the air conditioning equipment on each floor, and the main valve A predetermined primary pressure is maintained while adjusting the opening degree of the main valve body 5 by appropriately increasing / decreasing the internal pressure of the driving pressure chamber d.
The A valve body 24 and the B valve body 25 are provided so as to be aligned on a single valve shaft 26, and are integrally linked to a predetermined pressure means (spring 27) so as to be primary in the pilot valve device. It is a simple and rational mechanism that mixes the pressure and secondary pressure and sends the combined pressure to the main valve drive pressure chamber d to quickly respond to changes in the flow state. is there. In addition, both valve bodies 24; 25 are arranged at a position interval that can produce not only a state in which one is opened and the other is closed but also a state in which both the valve bodies are almost closed during operation, so that the flow condition is stable. When the valve body is in a closed state, both valve bodies are stabilized in a substantially closed state, and therefore chattering and hunting in which the valve bodies vibrate are unlikely to occur. By these, this apparatus exhibits the outstanding automatic adjustment function as a primary pressure regulation valve.
[0027]
Neither the A-valve device nor the B-valve device has a fixed throttle adjustment channel such as a needle valve, so clogging due to scale, foreign matter, etc. is unlikely to occur. In addition, even if clogging occurs, a self-cleaning operation is performed in which the valve bodies 24; 25 are automatically opened due to a pressure change caused by the clogging. That is, for example, if the A valve body 24 is clogged, the introduction of the primary pressure from the communication path p to the main valve driving pressure chamber d is hindered, so that the internal pressure of the main valve driving pressure chamber d decreases, The main valve body 5 operates in the valve opening direction to increase the passage flow rate, thereby reducing the primary pressure, and as a result, the A valve body 24 moves in the valve opening direction to automatically eliminate clogging. To do. Since this self-cleaning operation has an excellent function of eliminating clogging, a fine strainer or the like is unnecessary and maintenance management is easy.
[0028]
When the A valve device; B valve device is performing the primary pressure adjustment operation, the C valve body 34 is kept closed in the C valve device, and the A valve body 24; It does not interfere with the next pressure adjustment operation. In particular, as described above, if the set pressure of the spring 37 of the C valve device is set lower than the set pressure of the A valve device; the spring 27 of the B valve device, even if there is a slight fluctuation in the primary pressure. Since the C-valve element 34 is securely maintained in the closed state, the A valve device capable of performing a stable and precise adjustment operation; the B valve device can exclusively play the role of primary pressure adjustment, and smooth adjustment Is convenient.
[0029]
When the operation of the pump is stopped, the primary pressure rapidly decreases. At this time, in the pilot A valve device; the B valve device, the pressure receiving plate 23 extends in the direction in which the spring 27 extends (that is, in the right direction in the figure). The A valve body 24 is opened, and the B valve body 25 is closed. In the C valve device, the pressure receiving plate 33 is pushed in the direction in which the spring 37 extends (that is, the downward direction in the figure), and the C valve body 34 is opened.
By the action of these valve bodies 24; 25; 34, the main valve drive pressure chamber d communicates with the inlet flow path a, is disconnected from the outlet flow path c, and the internal pressure of the main valve drive pressure chamber d becomes the primary pressure. The main valve body 5 immediately closes to prevent the liquid from flowing through.
[0030]
In the present invention, the pilot A valve device; the B valve device opens and closes in an interlocked manner, so that the main valve closing operation can be performed sufficiently quickly with only the A valve device; the B valve device. Since the C valve device is provided, the pilot hydraulic fluid is additionally supplied from the main flow path (inlet flow path a) to the main valve drive pressure chamber d at once, and the main valve can be closed very quickly. It will exhibit advanced performance as a “fall-off prevention valve”.
The C-valve device according to the present invention has already added the function of the A-valve device; B-valve device that can operate the main valve closing sufficiently quickly. It goes without saying that it is compact compared to the device.
[0031]
When the main valve body 5 is closed, the portion that strictly functions as a seal is the seal member 5s of the main valve body 5 and the seal member of the B valve body 25, which can easily achieve the sealability according to the prior art. It is a member. On the other hand, even if the sealing member 6s and other sealing members of the main valve driving member 6 are left with a rough sealing property, they do not cause liquid leakage downstream.
[0032]
By the above operation, the automatic adjustment valve device V interposed in the circulation return path 108 has an excellent automatic adjustment function as a “primary pressure adjustment valve” that keeps the pressure of the return path 108 constant after the passage of the air-conditioning equipment 101 on each floor. In addition to the above, it also serves an accurate function as a “water fall prevention valve” that prevents the cold / hot water in the return path 108 from falling into the liquid storage tank 110 when the pump 104 is stopped.
[0033]
In addition, a required pressure set value can be adjusted by adjusting the springs 27; 37 with the adjustment screws 28;
The on-off valve 29 provided in the communication path q is used when the main valve device M is forcibly closed separately regardless of the operation of the pilot valve device, and is always open. . In order to close the main valve device M, the on-off valve 29 may be closed, whereby the internal pressure of the main valve drive pressure chamber d increases toward the primary pressure, and the main valve body 5 is closed. This on-off valve 29 may be operated manually or remotely using various actuators. On the other hand, when it is necessary to forcibly open the main valve device M separately, although not shown, a separate on-off valve is interposed between the main valve drive pressure chamber d and the outlet flow path c. It is sufficient to keep the valve closed (always closed) and open it.
[0034]
On the other hand, the automatic adjustment valve device V ′ interposed in the bypass piping of the circulation forward path 107 illustrated in FIG. 8 performs the same opening / closing operation as the automatic adjustment valve device V interposed on the return path side. The roles are slightly different, and the main valve device M is almost closed when the upstream pressure (primary pressure) is within the predetermined value range, but the primary pressure is likely to rise and exceed the predetermined value. When the state is reached, the main valve body 5 is pushed forward and the flow flows in the direction of the inlet flow path a → the main valve opening b → the outlet flow path c, thereby suppressing an increase in the primary pressure. In other words, it functions as a “primary pressure regulating valve” that keeps the pressure in the forward path 107 constant by acting as a “relief valve” that bypasses and releases the pressure increase in the forward path 107 beyond a predetermined value. Fulfill.
[0035]
Note that, unlike the return path 108 side, the “prevention of water falling” function for preventing the cold / hot water in the forward path 107 from falling into the liquid storage tank 110 when the pump is stopped is easily achieved by the check valve 105. Therefore, the automatic adjustment valve device V ′ is sufficient even if the pilot C valve device is not particularly mounted. Of course, since the C valve device may be mounted, for the sake of simplicity, FIG. 8 shows the same type as the valve device V on the return path 108 side.
[0036]
Next, other embodiments will be described.
In the second embodiment of FIG. 2, the A valve body 24 and the B valve body 25 of the first embodiment are coexisting in an intermediate chamber g. With this partial change, the communication passage pipe is slightly different from that of the first embodiment, but the other configurations and functions and effects are the same as those of the first embodiment, so detailed description thereof will be omitted.
In addition, with respect to the C valve device in FIG. 2, the bias pressure generated around the C valve body 34 in each chamber i; j is eliminated, and the C valve device reacts accurately with respect to the set pressure. 1 shows an example in which the valve shaft 36 and the C-valve body 34 are made to have a perfect balance structure.
[0037]
In the third embodiment of FIG. 3, the main valve drive member 6 of the first embodiment is provided on the downstream side of the main valve seat 4 contrary to that of the first embodiment, and the operating direction of the spring 27 is the first embodiment. It is the reverse of the example. With these partial changes, the operating directions of the main valve drive member 6 and the main valve body 5 are opposite to those of the first embodiment (the main valve body 5 is the internal pressure of the main valve drive pressure chamber d). Is opened when the pressure increases toward the primary pressure, and is closed when the internal pressure decreases toward the secondary pressure), the arrangement of the A valve device and the B valve device, and the inlet flow path a and the outlet flow path c. The communication passage pipes to each other are also opposite to those in the first embodiment, and the installation position of the C valve device is also connected to the main valve drive pressure chamber d and the outlet passage via the communication passages m ′; q ′. (When water is prevented from falling, the C valve device causes the pilot valve fluid to be discharged from the main valve drive pressure chamber d to the outlet passage c at once, thereby closing the main valve body 5 abruptly). Although the arrangement positions and operating directions of the respective components are different from those in the first embodiment, the operational effects are the same as those in the first embodiment. Ri, since other configurations similar to the first embodiment, detailed description thereof is omitted.
[0038]
In the fourth embodiment of FIG. 4, the A; B valve device and the C valve device of the first embodiment are combined face to face to form an A; B; C combined pilot valve device. However, the valve shaft 26 of the A valve body 24; the B valve body 25 and the valve shaft 36 of the C valve body 34 can move independently of each other, and the required pressure set values are also independent by the adjusting screws 28; 38, respectively. Can be adjusted. As each of the A, B, and C combined pilot valve devices is combined, each of the communication passage pipes is slightly different from that of the first embodiment, but the other configurations and operational effects are the same as those of the first embodiment. Therefore, detailed description is omitted.
[0039]
In the fifth embodiment of FIG. 5, the A valve body 24 and the B valve body 25 of the fourth embodiment are coexisting in the intermediate chamber g. With the partial change, the operating direction of the spring 27 is opposite to that of the fourth embodiment, and the communication passage piping is slightly different from that of the fourth embodiment. Since is the same as that of the fourth embodiment, detailed description thereof is omitted.
[0040]
The sixth embodiment of FIG. 6 is the same as that of the fourth embodiment by having one valve shaft of the A; B; C combined pilot valve device of the fourth embodiment and sharing one predetermined pressure means. The device is made more compact while performing the same function as the above.
The A valve body 24; the B valve body 25; and the C valve body 34 are provided on the same axis, and the three valve bodies 24; 25; And it is a mechanism that does not interfere with each other's operation. That is, the C valve body 34 and the corresponding valve seat are also in a cylinder / piston manner. In addition, as described above, the pressure set value for the operation of the C valve body 34 is usually slightly different from the pressure set values of the A valve body 24 and the B valve body 25. In the example, the difference is realized by providing a slight “deviation” between the opening / closing position of the C valve body 34 and the opening / closing position of the A valve body 24; Of course, the degree of this “deviation” may be adjustable by a screw or the like.
As described above, the same control as that of the fourth embodiment is possible. Since other configurations and operational effects are the same as those of the fourth embodiment, detailed description thereof is omitted.
[0041]
In the seventh embodiment of FIG. 7, the A valve body 24 and the B valve body 25 of the sixth embodiment are coexisting in the intermediate chamber g. With the partial change, the operating direction of the spring 27 is opposite to that of the sixth embodiment, and the communication pipe is slightly different from that of the sixth embodiment. Since this is the same as that of the sixth embodiment, detailed description thereof is omitted.
FIG. 7 shows an example in which the main valve body 5 and the main valve drive member 6 are integrated, and the drainage of the main valve drive pressure chamber d is performed at an appropriate time for inspection and maintenance. The example which attached siphon piping with the on-off valve 11 so that it can be performed is also shown in figure.
[0042]
Next, matters common to the embodiments of the present invention will be described.
As for the pilot A valve device; the B valve device, in any embodiment, as an example of a mechanism in which the A valve body 24 and the B valve body 25 are interlocked and do not interfere with each other's operation, Although a piston-type valve opening / closing mechanism is illustrated, a mode other than the cylinder / piston mode may be used, or the A valve device; the B valve device is divided and the valve body 24; 25 is placed on a separate valve shaft. Each may be provided.
Similarly, the C valve device may be provided on a separate valve shaft from the A valve device; the B valve device so as to cooperate with the A valve device; the B valve device and not interfere with each other's operation. In addition, a cylinder / piston type valve opening / closing mechanism as shown in FIGS. 6 to 7 may be used, or an appropriate type meeting the purpose may be used.
The A valve device; the B valve device; and the C valve device, as illustrated in the C valve device of FIG. A perfect balance structure may be applied.
In addition, the design of the chambers f; g; h; i; j; k; k 'of the pilot valve device is arranged (positional relationship) and combined, and associated passage pipes are designed within the scope of the present invention. It is possible, and the structure of the pilot valve device is not limited to the above embodiments.
[0043]
As for the predetermined pressure means of the pilot valve device, in addition to the method using the springs 27 and 37 as in the respective embodiments, other elastic members are used, linked to the weight, and a booster mechanism is added. Needless to say, application of an atmospheric pressure device, a hydraulic device, or the like can be easily performed.
[0044]
As for the main valve device M, the lift valve type is applied to the main valve body 5 in each embodiment, but other types of on-off valves (for example, butterfly valves, gates, etc.) are within the scope of the present invention. Valve, ball valve, etc.) may be applied. Further, an integral structure of the main valve body 5 and the main valve driving member 6 as illustrated in FIG. 7 may be applied. In each of the embodiments, in order to simplify the structure of the main valve device M, both the main flow path portion a → b → c and the main valve driving pressure chamber d are housed in the main valve box 1 in a compact manner. In addition, although the main flow path portion and the main valve drive pressure chamber d are housed in each of the main valve boxes divided into two, both ends of the main valve shaft passing through the two valve boxes are shown. Alternatively, the main valve body 5 and the main valve driving member 6 may be mounted.
[0045]
Depending on the specification conditions, it is necessary to prevent the influence of pressure pulsation (chattering and hunting) due to unexpected flow changes during the primary pressure adjustment operation, but as an example of how to deal with it, as shown in each example, The shape of the main valve opening b is a serrated flow path that makes the flow rate change smooth. Besides, a pilot A valve device; a B valve device is provided with a braking device; You may squeeze the communication path. If it is necessary to slowly operate the main valve device M within a range that does not impede the sudden closing operation as the “falling prevention valve”, the main valve device M has a one-effect braking device (opening of the main valve). (Brake only in the valve direction) may be provided. Any one of these countermeasures may be employed alone, or some may be employed in combination, or may be omitted under specification conditions where it is not required.
[0046]
Throughout each embodiment, O-rings, seal rings, diaphragms, bellows, etc. may be applied as appropriate according to local specifications for seal members that are installed in places that require tightness. If the sealing property can be maintained, the sealing member may be omitted. Needless to say, comb-shaped protrusions, rectifying grids, and the like may be formed in places where high-speed flow may pass for the purpose of preventing cavitation.
In addition, over the members constituting the valve device of the present invention, the use of the prior art is not disturbed, and various design changes can be made within the scope of the present invention. It is not limited to.
[0047]
【The invention's effect】
The automatic adjustment valve device of the present invention not only exhibits an excellent automatic adjustment function as a primary pressure adjustment valve, but also has a perfect shut-off sealing function, and is fixed to a pilot valve device portion such as a needle valve. Since there is no throttle adjustment flow path, and the pilot valve unit is clogged, the valve body automatically performs a self-cleaning operation that prevents clogging accidents due to scale, foreign matter, etc. There are also advantages. In addition, chattering and hunting hardly occur while the operation is quick. Furthermore, when the main valve upstream pressure (primary pressure) drops rapidly due to the stoppage of the feed pump, etc., it also closes immediately and prevents the liquid from flowing through. Demonstrate. The pilot valve device and other parts are simple in structure, easy to increase in size and pressure, can easily set and adjust the required primary pressure with a single touch, and should be difficult to design, manufacture, operate and maintain. There was no part, and it was possible to obtain a convenient automatic adjustment valve device that is highly reliable and economical, and its implementation effect is extremely large.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view showing a first embodiment of the present invention.
FIG. 2 is a longitudinal sectional view showing a second embodiment of the present invention.
FIG. 3 is a longitudinal sectional view showing a third embodiment of the present invention.
FIG. 4 is a longitudinal sectional view showing a fourth embodiment of the present invention.
FIG. 5 is a longitudinal sectional view showing a fifth embodiment of the present invention.
FIG. 6 is a longitudinal sectional view showing a sixth embodiment of the present invention.
FIG. 7 is a longitudinal sectional view showing a seventh embodiment of the present invention.
FIG. 8 is an explanatory view showing an installation example of a primary pressure regulating valve.
FIG. 9 is a longitudinal sectional view showing an example of a conventional primary pressure regulating valve.
FIG. 10 is a longitudinal sectional view showing another example of a primary pressure regulating valve according to the prior art.
[Explanation of symbols]
V ... Automatic adjustment valve device V '... Automatic adjustment valve device
M ... Main valve device
1 ... Main valve box 2 ... Main valve box cover
3 ... Cylindrical wall
4 ... Main valve seat 5 ... Main valve body 5s ... Seal member
6 ... Main valve drive member 6s ... Seal member
7 ... Main valve shaft 8 ... Main valve spring
9 ... Bearing 10 ... Fixed throttle control valve 11 ... Open / close valve
A ... Pilot A valve device B ... Pilot B valve device
21 ... Valve box 22 ... Valve box cover
23 ... Pressure receiving plate 23s ... Sealing member
24 ... A valve body 25 ... B valve body
26 ... Valve shaft 27 ... Spring 28 ... Adjustment screw
29 ... Open / close valve
C ... Pilot C valve device
31 ... Valve box 32 ... Valve box cover
33 ... Pressure receiving plate 33s ... Sealing member
34 ... C valve body
36 ... Valve shaft 37 ... Spring 38 ... Adjustment screw
a ... Inlet channel b ... Main valve opening
c ... Outlet channel d ... Main valve drive pressure chamber
f ... A valve chamber g ... Intermediate chamber h ... B valve chamber
i ... C valve chamber j ... Chamber
k; k '... Primary pressure chamber
m; m ′; p; p ′; q; q ′; r;
P ... Pilot valve device S ... Sub pilot valve device
101 ... Air conditioning equipment 102 ... Open / close valve
103 ... Heat exchanger 104 ... Pump
105 ... Check valve 106 ... Open / close valve
107 ... circulation outbound route 108 ... circulation return route
109 ... Air vent valve 110 ... Liquid storage tank

Claims

In the automatic adjustment valve device in which the main valve device that opens and closes the main flow path is driven in conjunction with the pilot valve device,
The main valve device includes a main valve body integrated into the main valve box and a main valve driving member having a larger pressure receiving area than the main valve body, and the main valve body is located upstream of the main valve seat. And a throttle flow path is formed between the main valve seat and the main valve drive member. The main valve drive member is slidably fitted to the cylindrical wall portion of the main valve box, and the main valve drive member is interposed between the main wall and the main valve seat. Forming a valve-driven pressure chamber,
The pilot valve device
A pilot A valve device that operates by the balance of the opposing acting force between the upstream pressure of the main valve device and the predetermined pressure means, and closes when the main valve upstream pressure becomes higher than a predetermined value, and opens when the pressure becomes lower;
A pilot B valve device that operates according to the balance of the opposing acting force between the upstream pressure of the main valve device and the predetermined pressure means, and opens when the main valve upstream pressure becomes higher than a predetermined value, and closes when the pressure becomes lower;
The pilot C valve device is operated by the balance of the counter acting force between the upstream pressure of the main valve device and the predetermined pressure means, and is closed when the main valve upstream pressure becomes higher than a predetermined value, and opened when the pressure becomes lower. ,
The pilot A valve device and the pilot B valve device are connected in series by a communication path between the upstream side and the downstream side of the main valve device via the main valve driving pressure chamber in the middle. An automatic adjustment valve device, wherein the pilot C valve device is interposed in a communication passage further provided between a main flow path of the main valve device and the main valve drive pressure chamber.

Both valve bodies of the pilot A valve device and the pilot B valve device are provided on the same axis, and both valve bodies are formed by the balance of the counteracting force between the upstream pressure of the main valve device and one predetermined pressure means. 2. The automatic adjustment valve device according to claim 1, wherein the automatic adjustment valve device operates in conjunction.

Three valve bodies of the pilot A valve device, the pilot B valve device, and the pilot C valve device are provided on the same axis, and the balance of the counteracting force between the upstream pressure of the main valve device and one predetermined pressure means is provided. The automatically adjusting valve device according to claim 1, wherein the three valve bodies are operated in conjunction with each other.