JP6692215B2

JP6692215B2 - Flow control valve

Info

Publication number: JP6692215B2
Application number: JP2016104831A
Authority: JP
Inventors: 原田　貴雄; 貴雄原田; 柳澤　秀; 秀柳澤; 佑樹小泉
Original assignee: Fujikoki Corp
Current assignee: Fujikoki Corp
Priority date: 2016-05-26
Filing date: 2016-05-26
Publication date: 2020-05-13
Anticipated expiration: 2036-05-26
Also published as: CN107435754B; JP2017211032A; CN107435754A

Description

本発明は、例えばヒートポンプ式冷暖房システム等において冷媒流量を調整するのに好適な流量調整弁、特に、流体（冷媒）通過時における騒音を低減し得るようにされた流量調整弁に関する。 The present invention relates to a flow rate adjusting valve suitable for adjusting the flow rate of a refrigerant in, for example, a heat pump type cooling / heating system, and more particularly to a flow rate adjusting valve configured to reduce noise when a fluid (refrigerant) passes through.

この種の流量調整弁の一例として、弁室及び弁座付き弁口（オリフィス）が設けられた弁本体と、弁座からのリフト量に応じて弁口を流れる流体の流量を変化させる弁体とを備え、弁体が、例えば特許文献１、２等に所載の如くの、雄ねじが設けられた弁軸、雌ねじが設けられた軸受部材、及びステッピングモータ等で構成されるねじ送り式昇降駆動機構により、弁座に接離又は近接離間するように昇降せしめられる電動弁が知られている。 As an example of this kind of flow rate adjusting valve, a valve body provided with a valve chamber and a valve seat-equipped valve opening (orifice), and a valve body that changes the flow rate of fluid flowing through the valve opening according to the lift amount from the valve seat. And a valve element having a screw feed type lifting drive including a valve shaft provided with a male screw, a bearing member provided with a female screw, and a stepping motor as described in Patent Documents 1 and 2, etc. A motor-operated valve is known, which is lifted up and down by a mechanism so as to come into contact with or separate from or close to a valve seat.

ところで、上記した如くの構成の流量調整弁を、例えばヒートポンプ式冷暖房システムに組み込んだ場合、前記弁口が所定開度まで開かれ、弁室に流れ込んだ冷媒が、弁室から弁体と弁口との間に形成される隙間を介して流出する際、連続的な騒音（流体通過音）が発生しやすいという問題があった。 By the way, when the flow rate adjusting valve having the above-described configuration is incorporated in, for example, a heat pump type cooling and heating system, the valve opening is opened to a predetermined opening degree, and the refrigerant flowing into the valve chamber is transferred from the valve chamber to the valve body and the valve opening. There is a problem that continuous noise (fluid passing sound) is likely to be generated when flowing out through a gap formed between and.

より詳しくは、弁口に流れ込む流体（冷媒）が気体と液体の混合状態（気液二相流）、つまり、弁室を介して弁口に向かう流体中に気泡が混じっていると、その気泡が弁口を通過する際、その流入側と流出側に急激な圧力変動を発生させ、その圧力変動によって大きな騒音が発生する。特に、小開度領域（弁開度（弁体のリフト量）が小さい領域）においては、一般に、前記弁口における流体の流路（弁体と弁口との間の隙間）が非常に狭いので、流体中の気泡の影響が大きくなり、前述の大きな騒音（流体通過音）が更に発生しやすくなる。 More specifically, when the fluid (refrigerant) flowing into the valve opening is a mixed state of gas and liquid (gas-liquid two-phase flow), that is, when bubbles are mixed in the fluid flowing through the valve chamber toward the valve opening, the bubbles When passing through the valve port, a sudden pressure fluctuation is generated on the inflow side and the outflow side, and a large noise is generated by the pressure fluctuation. In particular, in the small opening area (area where the valve opening (lift amount of the valve body) is small), the flow passage of the fluid in the valve opening (the gap between the valve body and the valve opening) is generally very narrow. Therefore, the influence of air bubbles in the fluid becomes large, and the above-mentioned loud noise (fluid passing sound) is more likely to occur.

このような問題に対し、特許文献３に所載の従来技術では、弁室内に、流体中の気泡を細分化する部材（消音部材）を介装することが提案されている。 In order to deal with such a problem, in the conventional technique disclosed in Patent Document 3, it is proposed to interpose a member (silencer member) for subdividing air bubbles in the fluid in the valve chamber.

特開２０１２−１７２８３９号公報JP2012-172839A 特開２００４−２８９９０１号公報JP 2004-289901 A 特開２００１−２８９５３８号公報JP 2001-289538 A

ところで、大開度領域（弁開度が大きい領域）においては、前記弁口における流体の流路（弁体と弁口との間の隙間）が広くなるので、前述のような大きな騒音（流体通過音）は発生しにくくなる一方、弁口を通過する流量を十分に確保する必要性が高くなる。 By the way, in the large opening area (area where the valve opening is large), the flow passage of the fluid in the valve opening (the gap between the valve body and the valve opening) becomes wide, so that the above-mentioned large noise (fluid passage) Sound) is less likely to occur, but it becomes more necessary to secure a sufficient flow rate through the valve opening.

特許文献３に所載の従来技術においては、流体中の気泡が、前記消音部材によって分解されて細分化された状態で、弁体と弁口との間の隙間に流入するので、弁口を通過する際、その流入側と流出側に急激な圧力変動は発生せず、前述の騒音を低減できる。しかし、前記消音部材は、弁室における流入口側と流出口側を常時仕切るように弁本体に固定されているので、弁口を通過する流量を確保する必要がある大開度領域において、弁口へ向かう流体の流れを阻害し、圧力損失（圧損）が大きくなり、適正な冷媒流量が得られ難いという問題があった。 In the prior art disclosed in Patent Document 3, bubbles in the fluid are decomposed by the muffling member and subdivided into the gap between the valve body and the valve opening. When passing, sudden pressure fluctuations do not occur on the inflow side and the outflow side, and the aforementioned noise can be reduced. However, since the muffling member is fixed to the valve body so as to always partition the inlet side and the outlet side of the valve chamber, in the large opening area where it is necessary to secure the flow rate passing through the valve opening, There is a problem that the flow of the fluid toward the front is obstructed, the pressure loss (pressure loss) increases, and it is difficult to obtain an appropriate refrigerant flow rate.

本発明は、上記事情に鑑みてなされたもので、その目的とするところは、流体（冷媒）通過時における騒音を効果的に低減できるとともに、大開度領域における圧力損失の低減も図ることのできる流量調整弁を提供することにある。 The present invention has been made in view of the above circumstances, and an object thereof is to effectively reduce noise when a fluid (refrigerant) passes and also to reduce pressure loss in a large opening range. It is to provide a flow control valve.

前記目的を達成すべく、本発明に係る流量調整弁は、基本的には、弁室及び第１弁口が設けられた弁本体と、前記弁室内に昇降自在に配在された弁軸と、該弁軸を昇降させるための昇降駆動部と、前記弁軸の下端部外周を包囲するように該弁軸に摺動自在に外挿され、該弁軸の昇降動作に連動して駆動される弁体と、を備え、前記弁体に、リフト量に応じて前記第１弁口を流れる流体の流量を変化させる第１弁体部が設けられ、前記弁体により前記弁軸の下端部周りに画成された連通空間を介して前記弁室と前記第１弁口とを連通する小流量通路が形成されるとともに、前記弁軸に、リフト量に応じて前記小流量通路に設けられた第２弁口を流れる流体の流量を変化させる第２弁体部が設けられ、前記第２弁体部のリフト量が所定量以下のときは、前記第１弁体部により前記第１弁口が閉じられ、前記第２弁体部の前記第２弁口に対するリフト量に応じて流量が制御される小流量制御状態をとり、前記第２弁体部のリフト量が前記所定量を超えると、前記弁軸の上昇に伴って前記弁体が上昇せしめられて前記第１弁体部が前記第１弁口を開く大流量制御状態をとるように構成され、前記小流量通路における前記第２弁口より前記弁室側及び前記第１弁口側に、前記小流量通路を流れる流体中の気泡を細分化する消音部材が配在され、前記弁体は、前記弁軸における前記第２弁体部より上側に摺動自在に外挿された筒状の連動部材と、該連動部材の下端開口に連結され、前記第１弁体部が設けられた弁体部材とで構成され、前記小流量通路が、前記弁室と前記連通空間を連通すべく前記連動部材に設けられた貫通口と、前記連通空間と、該連通空間と前記第１弁口を連通すべく前記弁体部材に設けられた連通路とから構成され、前記連通路に前記第２弁口が形成されており、前記消音部材が、前記連動部材における前記貫通口及び前記弁体部材における前記連通路に配在され、前記連動部材の内周に、筒状の消音部材が配在されていることを特徴としている。また、本発明に係る流量調整弁は、基本的には、弁室及び第１弁口が設けられた弁本体と、前記弁室内に昇降自在に配在された弁軸と、該弁軸を昇降させるための昇降駆動部と、前記弁軸の下端部外周を包囲するように該弁軸に摺動自在に外挿され、該弁軸の昇降動作に連動して駆動される弁体と、を備え、前記弁体に、リフト量に応じて前記第１弁口を流れる流体の流量を変化させる第１弁体部が設けられ、前記弁体により前記弁軸の下端部周りに画成された連通空間を介して前記弁室と前記第１弁口とを連通する小流量通路が形成されるとともに、前記弁軸に、リフト量に応じて前記小流量通路に設けられた第２弁口を流れる流体の流量を変化させる第２弁体部が設けられ、前記第２弁体部のリフト量が所定量以下のときは、前記第１弁体部により前記第１弁口が閉じられ、前記第２弁体部の前記第２弁口に対するリフト量に応じて流量が制御される小流量制御状態をとり、前記第２弁体部のリフト量が前記所定量を超えると、前記弁軸の上昇に伴って前記弁体が上昇せしめられて前記第１弁体部が前記第１弁口を開く大流量制御状態をとるように構成され、前記小流量通路における前記第２弁口より前記弁室側及び前記第１弁口側に、前記小流量通路を流れる流体中の気泡を細分化する消音部材が配在され、前記弁体は、前記弁軸における前記第２弁体部より上側に摺動自在に外挿された筒状の連動部材と、該連動部材の下端開口に連結され、前記第１弁体部が設けられた弁体部材とで構成され、前記小流量通路が、前記弁室と前記連通空間を連通すべく前記連動部材に設けられた貫通口と、前記連通空間と、該連通空間と前記第１弁口を連通すべく前記弁体部材に設けられた連通路とから構成され、前記連通路に前記第２弁口が形成されており、前記消音部材が、前記連動部材における前記貫通口及び前記弁体部材における前記連通路に配在され、前記弁体部材の前記連通路に固定され、通し穴を持つ支持部材によって、前記消音部材が前記弁体部材の前記連通路に支持固定されていることを特徴としている。また、本発明に係る流量調整弁は、基本的には、弁室及び第１弁口が設けられた弁本体と、前記弁室内に昇降自在に配在された弁軸と、該弁軸を昇降させるための昇降駆動部と、前記弁軸の下端部外周を包囲するように該弁軸に摺動自在に外挿され、該弁軸の昇降動作に連動して駆動される弁体と、を備え、前記弁体に、リフト量に応じて前記第１弁口を流れる流体の流量を変化させる第１弁体部が設けられ、前記弁体により前記弁軸の下端部周りに画成された連通空間を介して前記弁室と前記第１弁口とを連通する小流量通路が形成されるとともに、前記弁軸に、リフト量に応じて前記小流量通路に設けられた第２弁口を流れる流体の流量を変化させる第２弁体部が設けられ、前記第２弁体部のリフト量が所定量以下のときは、前記第１弁体部により前記第１弁口が閉じられ、前記第２弁体部の前記第２弁口に対するリフト量に応じて流量が制御される小流量制御状態をとり、前記第２弁体部のリフト量が前記所定量を超えると、前記弁軸の上昇に伴って前記弁体が上昇せしめられて前記第１弁体部が前記第１弁口を開く大流量制御状態をとるように構成され、前記小流量通路における前記第２弁口より前記弁室側及び前記第１弁口側に、前記小流量通路を流れる流体中の気泡を細分化する消音部材が配在され、前記第１弁体部により前記第１弁口が閉じられ、かつ、前記第２弁体部により前記第２弁口が閉じられた状態で、前記第１弁口から前記弁室へ向かう流体の流れを許容するが、前記弁室から前記第１弁口へ向かう流体の流れを遮断する逆止弁体が設けられていることを特徴としている。 In order to achieve the above-mentioned object, a flow rate control valve according to the present invention basically comprises a valve body provided with a valve chamber and a first valve opening, and a valve shaft vertically movable in the valve chamber. An elevating and lowering drive unit for elevating and lowering the valve shaft, and a slidably externally inserted to the valve shaft so as to surround the outer periphery of the lower end of the valve shaft, and driven in association with the elevating and lowering operation of the valve shaft. A valve body, the first valve body portion changing the flow rate of the fluid flowing through the first valve opening according to the lift amount, and the valve body lower end portion of the valve shaft. A small flow passage that connects the valve chamber and the first valve opening is formed through a communication space that is defined around the small flow passage, and the small flow passage is provided on the valve shaft according to the lift amount. A second valve body portion for changing the flow rate of the fluid flowing through the second valve opening is provided, and the lift amount of the second valve body portion is less than or equal to a predetermined amount. Is in a small flow rate control state in which the first valve opening is closed by the first valve body, and the flow rate is controlled according to the lift amount of the second valve body with respect to the second valve opening. 2 When the lift amount of the valve body portion exceeds the predetermined amount, the valve body is raised with the rise of the valve shaft, and the first valve body portion is in the large flow rate control state in which the first valve opening is opened. And a sound deadening member for subdividing air bubbles in the fluid flowing through the small flow passage from the second valve opening to the valve chamber side and the first valve opening side in the small flow passage. The valve body is connected to a cylindrical interlocking member slidably inserted above the second valve body section of the valve shaft and a lower end opening of the interlocking member, and the first valve body section is provided. And a valve body member provided with a valve body member, and the small flow passage is provided to communicate with the valve chamber and the communication space. The communication member includes a through-hole provided in the interlocking member, the communication space, and a communication passage provided in the valve body member so as to communicate the communication space with the first valve opening. A valve opening is formed, the muffling member is arranged in the through hole of the interlocking member and the communication passage of the valve body member, and a cylindrical muffling member is arranged on the inner periphery of the interlocking member. It is characterized by being. In addition, the flow rate control valve according to the present invention basically includes a valve main body provided with a valve chamber and a first valve opening, a valve shaft vertically arranged in the valve chamber, and the valve shaft. An elevating and lowering drive part for elevating and lowering, a valve element slidably inserted into the valve shaft so as to surround the outer periphery of the lower end part of the valve shaft, and driven in conjunction with the elevating and lowering operation of the valve shaft, The valve body is provided with a first valve body portion that changes a flow rate of the fluid flowing through the first valve opening according to a lift amount, and is defined by the valve body around a lower end portion of the valve shaft. A small flow passage that connects the valve chamber and the first valve opening is formed through the communication space, and a second valve opening provided on the valve shaft in the small flow passage according to the lift amount. A second valve body portion that changes the flow rate of the fluid flowing through the first valve body, and the lift amount of the second valve body portion is less than or equal to a predetermined amount. The first valve port is closed by a section, and a small flow rate control state in which a flow rate is controlled according to a lift amount of the second valve body section with respect to the second valve body is taken, and a lift amount of the second valve body section is taken. Is greater than the predetermined amount, the valve body is caused to rise as the valve shaft rises, and the first valve body portion is configured to take a large flow rate control state in which the first valve opening is opened. A muffling member for subdividing air bubbles in the fluid flowing through the small flow passage is arranged on the valve chamber side and the first valve opening side of the small flow passage from the second valve opening, and the valve element is A tubular interlocking member slidably inserted above the second valve body section of the valve shaft, and a valve body member provided with the first valve body section connected to a lower end opening of the interlocking member. And the small flow passage is provided in the interlocking member to connect the valve chamber and the communication space. A through-hole, the communication space, and a communication passage provided in the valve body member for communicating the communication space with the first valve opening, and the second passage is formed in the communication passage. The sound deadening member is disposed in the through hole of the interlocking member and the communication passage of the valve body member, is fixed to the communication passage of the valve body member, by a support member having a through hole, The sound deadening member is supported and fixed to the communication passage of the valve body member. In addition, the flow rate control valve according to the present invention basically includes a valve main body provided with a valve chamber and a first valve opening, a valve shaft vertically arranged in the valve chamber, and the valve shaft. An elevating and lowering drive part for elevating and lowering, a valve element slidably inserted into the valve shaft so as to surround the outer periphery of the lower end part of the valve shaft, and driven in conjunction with the elevating and lowering operation of the valve shaft, The valve body is provided with a first valve body portion that changes a flow rate of the fluid flowing through the first valve opening according to a lift amount, and is defined by the valve body around a lower end portion of the valve shaft. A small flow passage that connects the valve chamber and the first valve opening is formed through the communication space, and a second valve opening provided on the valve shaft in the small flow passage according to the lift amount. A second valve body portion that changes the flow rate of the fluid flowing through the first valve body, and the lift amount of the second valve body portion is less than or equal to a predetermined amount. The first valve port is closed by a section, and a small flow rate control state in which a flow rate is controlled according to a lift amount of the second valve body section with respect to the second valve body is taken, and a lift amount of the second valve body section is taken. Is greater than the predetermined amount, the valve body is caused to rise as the valve shaft rises, and the first valve body portion is configured to take a large flow rate control state in which the first valve opening is opened. A muffling member that subdivides air bubbles in the fluid flowing through the small flow passage is disposed on the valve chamber side and the first valve opening side of the small flow passage from the second valve opening, and the first valve body portion. Allows the flow of fluid from the first valve opening toward the valve chamber in a state where the first valve opening is closed by the second valve opening and the second valve opening is closed by the second valve body portion. A non-return valve body for blocking the flow of fluid from the valve chamber to the first valve opening is provided. It is a symptom.

前記弁体は、好ましくは、付勢部材によって前記第１弁口の閉弁方向に付勢されるとともに、前記第２弁体部のリフト量が前記所定量を超えると、前記弁軸に設けられた鍔状係止部により前記付勢部材の付勢力に抗して引き上げられるようにされる。 The valve element is preferably provided on the valve shaft when the urging member urges the valve element in the valve closing direction of the first valve opening and the lift amount of the second valve element portion exceeds the predetermined amount. The brim-shaped locking portion provided allows the urging member to be pulled up against the urging force of the urging member.

前記弁体は、好ましくは、前記弁軸における前記第２弁体部より上側に摺動自在に外挿された筒状の連動部材と、該連動部材の下端開口に連結され、前記第１弁体部が設けられた弁体部材とで構成される。 The valve body is preferably connected to a tubular interlocking member slidably inserted above the second valve body portion of the valve shaft and a lower end opening of the interlocking member, and the first valve The valve body member is provided with a body portion.

好ましい態様では、前記小流量通路が、前記弁室と前記連通空間を連通すべく前記連動部材に設けられた貫通口と、前記連通空間と、該連通空間と前記第１弁口を連通すべく前記弁体部材に設けられた連通路とから構成され、前記連通路に前記第２弁口が形成されており、前記消音部材が、前記連動部材における前記貫通口及び前記弁体部材における前記連通路に配在される。 In a preferred aspect, the small flow passage connects the through hole provided in the interlocking member to connect the valve chamber and the communication space, the communication space, and the communication space and the first valve opening. And a communication passage provided in the valve body member, the second valve opening is formed in the communication passage, and the muffling member includes the through hole in the interlocking member and the communication passage in the valve body member. Located in the aisle.

更に好ましい態様では、前記連動部材の内周に、筒状の消音部材が配在される。 In a further preferred aspect, a cylindrical silencing member is arranged on the inner circumference of the interlocking member.

更なる好ましい態様では、前記筒状の消音部材は、上端が前記連動部材に設けられた凹部に嵌め込まれ、下端が前記弁体部材と前記連動部材とで挟持されるようにして、前記連動部材の内周に配在される。 In a further preferred aspect, the cylindrical sound deadening member has an upper end fitted into a recess provided in the interlocking member, and a lower end sandwiched between the valve body member and the interlocking member, It is distributed on the inner circumference of.

別の好ましい態様では、前記弁体部材の前記連通路に固定され、通し穴を持つ支持部材によって、前記消音部材が前記弁体部材の前記連通路に支持固定される。 In another preferable aspect, the silencing member is fixed to the communication passage of the valve body member, and the silencing member is supported and fixed to the communication passage of the valve body member by a support member having a through hole.

更に好ましい態様では、前記弁軸に、前記逆止弁体が収納される収納室、該収納室と前記第１弁口とに連通するとともに前記第１弁口側と前記弁室側との差圧に応じて前記逆止弁体により開閉される逆止弁口、及び、該収納室と前記弁室とに常時連通する連通口が設けられる。 In a further preferred aspect, the valve shaft accommodates a storage chamber in which the check valve body is stored, a communication between the storage chamber and the first valve port, and a difference between the first valve port side and the valve chamber side. A check valve port that is opened and closed by the check valve body according to pressure is provided, and a communication port that always communicates with the storage chamber and the valve chamber.

本発明に係る流量調整弁では、連通空間を介して弁室と第１弁口とを連通する小流量通路における第２弁口より弁室側及び第１弁口側に、当該小流量通路を流れる流体中の気泡を細分化する消音部材が配在されているので、流体（冷媒）通過時における騒音を効果的に低減できるとともに、大開度（大流量制御）領域における圧力損失が小さくなり、適正な冷媒流量を得ることができる。 In the flow rate adjusting valve according to the present invention, the small flow passage is connected to the valve chamber side and the first valve opening side of the second valve opening in the small flow passage that communicates the valve chamber and the first valve opening via the communication space. Since the muffling member that subdivides air bubbles in the flowing fluid is distributed, noise when the fluid (refrigerant) passes can be effectively reduced, and pressure loss in the large opening (large flow rate control) region becomes small, A proper refrigerant flow rate can be obtained.

本発明に係る流量調整弁の一実施形態を示す全体断面図。The whole sectional view showing one embodiment of the flow control valve concerning the present invention. 図１に示される弁体の連動部材を消音部材とともに示す斜視図。The perspective view which shows the interlocking member of the valve body shown by FIG. 1 with a sound deadening member. 図１に示される弁体の押さえ板を消音部材とともに示す図であり、（Ａ）は斜視図、（Ｂ）は下面図。It is a figure which shows the press board of the valve body shown by FIG. 1 with a sound deadening member, (A) is a perspective view, (B) is a bottom view. 図１に示される流量調整弁における主要部（正流れ時）を示す要部断面図であり、（Ａ）は全閉状態、（Ｂ）はリフト量が小さい状態（小流量制御状態）、（Ｃ）は全開状態（大流量制御状態）を示す図。FIG. 2 is a cross-sectional view of a main part showing a main part (during normal flow) of the flow rate control valve shown in FIG. 1, where (A) is a fully closed state, (B) is a small lift amount state (small flow rate control state), FIG. 6C is a diagram showing a fully open state (large flow rate control state). 図１に示される流量調整弁における主要部（逆流れ時）を示す要部断面図であり、（Ａ）は全閉状態、（Ｂ）は差圧により逆止弁口が開いた状態、（Ｃ）は全開状態を示す図。FIG. 2 is a cross-sectional view of a main part showing a main part (at the time of reverse flow) of the flow rate control valve shown in FIG. 1, where (A) is a fully closed state, (B) is a state where a check valve port is opened due to a differential pressure, ( C) is a diagram showing a fully opened state. （Ａ）〜（Ｃ）はそれぞれ、図１に示される逆止弁構造の他例を示す要部拡大断面図。(A)-(C) is an important section expanded sectional view showing other examples of a check valve structure shown in Drawing 1, respectively. 図１に示される流量調整弁の変形形態（その１）を示す全体断面図。The whole sectional view which shows the modification (1) of the flow regulating valve shown in FIG. 図１に示される流量調整弁の変形形態（その２）を示す全体断面図。The whole sectional view which shows the modification (2) of the flow control valve shown by FIG.

以下、本発明の実施形態を図面を参照しながら説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は、本発明に係る流量調整弁の一実施形態を示す全体断面図、図２は、図１に示される弁体の連動部材を示す斜視図、図３は、図１に示される弁体の押さえ板を示す図であり、図３（Ａ）は斜視図、図３（Ｂ）は下面図である。 1 is an overall sectional view showing an embodiment of a flow rate control valve according to the present invention, FIG. 2 is a perspective view showing an interlocking member of the valve body shown in FIG. 1, and FIG. 3 is a valve shown in FIG. It is a figure which shows the pressing plate of a body, FIG.3 (A) is a perspective view and FIG.3 (B) is a bottom view.

なお、本明細書において、上下、左右、前後等の位置、方向を表わす記述は、説明が煩瑣になるのを避けるために図面に従って便宜上付けたものであり、実際の使用状態での位置、方向を指すとは限らない。 In this specification, the description of the position, direction such as up and down, left and right, front and back is added for convenience according to the drawings in order to avoid complicated description, and the position and direction in the actual use state. Does not necessarily mean.

また、各図において、部材間に形成される隙間や部材間の離隔距離等は、発明の理解を容易にするため、また、作図上の便宜を図るため、各構成部材の寸法に比べて大きくあるいは小さく描かれている場合がある。 Further, in each drawing, the gaps formed between the members and the separation distances between the members are larger than the dimensions of the respective constituent members in order to facilitate understanding of the invention and for convenience in drawing. Or it may be drawn smaller.

図示実施形態の流量調整弁１は、例えばヒートポンプ式冷暖房システム等において冷媒流量を調整するために使用される電動弁であり、前述した従来の流量調整弁と同様に、流体（冷媒）が導入導出される弁室１４及び該弁室１４に開口する弁口（第１弁口）１６付き弁座（第１弁座）１５を有する弁本体１０と、リング状のベースプレート３１を介して弁本体１０に固着された有底円筒状のキャン３０と、キャン３０に外嵌されるステータ４０及びキャン３０の内周に回転自在に配在されるロータ５０からなるステッピングモータ（昇降駆動部）６３と、ロータ５０の回転数を減速する不思議遊星歯車減速機構６０と、前記弁座１５に接離して流体の通過量を制御する（言い換えれば、弁座１５からのリフト量に応じて弁口１６を流れる流体の流量を変化させる）弁体３２が設けられた弁軸２０と、不思議遊星歯車減速機構６０の出力ギヤ５７の回転運動を直線運動に変換して弁軸２０を駆動する（昇降させる）ねじ送り機構２７と、から構成される。 The flow rate adjusting valve 1 of the illustrated embodiment is an electric valve used for adjusting the refrigerant flow rate in, for example, a heat pump type cooling and heating system, and like a conventional flow rate adjusting valve described above, a fluid (refrigerant) is introduced and derived. The valve body 10 having the valve chamber 14 and the valve seat (first valve seat) 15 with the valve port (first valve port) 16 opening to the valve chamber 14, and the valve body 10 via the ring-shaped base plate 31. A bottomed cylindrical can 30 fixed to the can 30, a stepping motor (elevating drive unit) 63 including a stator 40 externally fitted to the can 30, and a rotor 50 rotatably arranged on the inner circumference of the can 30; A mysterious planetary gear reduction mechanism 60 that reduces the rotation speed of the rotor 50 and a valve seat 15 are brought into contact with and separated from the valve seat 15 to control the amount of passage of fluid (in other words, flow through the valve port 16 according to the lift amount from the valve seat 15). Flow Of the valve shaft 20 provided with the valve element 32 (for changing the flow rate of the) and the output gear 57 of the mysterious planetary gear reduction mechanism 60 are converted into linear motions to drive (raise and lower) the valve shaft 20. And a mechanism 27.

弁本体１０における弁室１４の一側部には、管継手１１Ａが接続される流入口１１が設けられ、その底部に、管継手１２Ａが接続されるとともに、弁座１５及び円筒面からなる弁口（オリフィス）１６を持つ流出口１２が設けられている。また、弁本体１０の弁室１４の上部には、中心部下半部に雌ねじ部１３ａが形成された軸受部材１３が嵌挿され、かしめにより弁本体１０に固定されている（かしめ部１７）。弁本体１０の外周（の段差部）に固定されたベースプレート３１には、有蓋円筒状のキャン３０の下端部が突き合わせ溶接等により密封接合されている。 An inlet 11 to which the pipe joint 11A is connected is provided on one side of the valve chamber 14 in the valve body 10, and a pipe joint 12A is connected to the bottom of the inlet 11 and a valve having a valve seat 15 and a cylindrical surface. An outlet 12 having a mouth 16 is provided. Further, a bearing member 13 having a female screw portion 13a formed in a lower half portion of a central portion is fitted and inserted in an upper portion of a valve chamber 14 of the valve body 10 and is fixed to the valve body 10 by caulking (caulking portion 17). A lower end of a cylindrical can 30 having a lid is hermetically joined by butt welding or the like to a base plate 31 fixed to (the stepped portion of) the outer periphery of the valve body 10.

キャン３０の外周に装着されたステータ４０は、ヨーク４１、ボビン４２、コイル４３、樹脂モールドカバー４４等からなり、キャン３０の内部に（上下動せずに）回転自在に支持されるロータ５０は、磁性材料で作製された円筒状のロータ部材５１と樹脂材料で作製された太陽ギヤ部材５２とが一体に連結されて構成されている。太陽ギヤ部材５２の中心部にはシャフト６２が挿入され、そのシャフト６２の上部は、キャン３０の頂部内側に配置された支持部材６１により支持されている。 The stator 40 mounted on the outer periphery of the can 30 includes a yoke 41, a bobbin 42, a coil 43, a resin mold cover 44, etc., and the rotor 50 rotatably supported inside the can 30 (without moving up and down) A cylindrical rotor member 51 made of a magnetic material and a sun gear member 52 made of a resin material are integrally connected to each other. A shaft 62 is inserted in the center of the sun gear member 52, and the upper portion of the shaft 62 is supported by a support member 61 arranged inside the top of the can 30.

太陽ギヤ部材５２の太陽ギヤ５３は、出力ギヤ５７の底面上に載置されたキャリア５４に設けられたシャフト５６に回転自在に支持される複数の遊星ギヤ５５に噛み合う。遊星ギヤ５５の上半分は、弁本体１０の上部に固定された円筒部材１８の上部にかしめにより取り付けられた環状のリングギヤ（内歯固定ギヤ）５８に噛み合い、遊星ギヤ５５の下半分は、環状の出力ギヤ５７の内歯ギヤ５７ａに噛み合っている。リングギヤ５８の歯数と出力ギヤ５７の内歯ギヤ５７ａの歯数とはわずかに異なる歯数とされ、これにより、太陽ギヤ５３の回転数が大きな減速比で減速されて出力ギヤ５７に伝達される（このような歯車構成を、いわゆる不思議遊星歯車減速機構６０という）。 The sun gear 53 of the sun gear member 52 meshes with a plurality of planetary gears 55 rotatably supported by a shaft 56 provided on a carrier 54 mounted on the bottom surface of the output gear 57. The upper half of the planetary gear 55 meshes with an annular ring gear (internal tooth fixed gear) 58 mounted by caulking on the upper portion of the cylindrical member 18 fixed to the upper portion of the valve main body 10, and the lower half of the planetary gear 55 has an annular shape. Of the output gear 57 meshes with the internal gear 57a. The number of teeth of the ring gear 58 and the number of teeth of the internal gear 57a of the output gear 57 are slightly different from each other, whereby the rotation speed of the sun gear 53 is reduced at a large reduction ratio and transmitted to the output gear 57. (This kind of gear configuration is called a so-called mysterious planetary gear reduction mechanism 60).

出力ギヤ５７は、筒状の軸受部材１３の上面に摺動接触しており、その出力ギヤ５７の底部中央には段付き円筒状の出力軸５９の上部が圧入され、出力軸５９の下部が軸受部材１３の中心部上半部に形成された嵌挿穴１３ｂに回転自在に挿入されている。また、出力軸５９の上部には、シャフト６２の下部が嵌め込まれている。 The output gear 57 is in sliding contact with the upper surface of the tubular bearing member 13, the upper portion of the stepped cylindrical output shaft 59 is press-fitted into the center of the bottom portion of the output gear 57, and the lower portion of the output shaft 59 is located below. The bearing member 13 is rotatably inserted into a fitting insertion hole 13b formed in the upper half of the central portion of the bearing member 13. The lower part of the shaft 62 is fitted on the upper part of the output shaft 59.

弁軸２０は、上側から、ねじ駆動部材（ドライバともいう）２２と、段付き軸状の推力伝達軸２８と、推力伝達軸２８の下部に外嵌固定された底部付き円筒状の連結軸２９とを有し、連結軸２９の下端部外周（つまり、弁軸２０の下端部外周）を包囲するように該連結軸２９に弁体３２が摺動自在に外挿されている。 The valve shaft 20 includes a screw drive member (also referred to as a driver) 22, a stepped shaft-shaped thrust transmission shaft 28, and a bottomed cylindrical connection shaft 29 externally fitted and fixed to a lower portion of the thrust transmission shaft 28 from the upper side. The valve element 32 is slidably fitted on the connecting shaft 29 so as to surround the lower end outer circumference of the connecting shaft 29 (that is, the lower end outer circumference of the valve shaft 20).

前記軸受部材１３（の内周）に設けられた雌ねじ部１３ａには、弁軸２０を構成するねじ駆動部材２２（の外周）に設けられた雄ねじ部２２ａが螺合されており、そのねじ駆動部材２２は、出力ギヤ５７（すなわち、ロータ５０）の回転運動を雄ねじ部２２ａと雌ねじ部１３ａとからなるねじ送り機構２７により軸線Ｏ方向（昇降方向）の直線運動に変換する。ここで、出力ギヤ５７は軸線Ｏ方向の一定位置で上下動せずに回転運動しており、出力ギヤ５７に連結された出力軸５９の下端部に設けたスリット状の嵌合溝５９ｂにねじ駆動部材２２の上端部に設けた平ドライバ形状の板状部２２ｂを挿入して出力ギヤ５７の回転運動をねじ駆動部材２２側に伝達する。ねじ駆動部材２２に設けた板状部２２ｂが出力軸５９の嵌合溝５９ｂ内で軸線Ｏ方向に摺動することにより、出力ギヤ５７（ロータ５０）が回転すれば該出力ギヤ５７はその回転軸方向に移動しないにも関わらず、ねじ駆動部材２２は前記ねじ送り機構２７で軸線Ｏ方向に直線運動する。ねじ駆動部材２２の直線運動は、ボール２３と推力伝達軸２８の上部に設けられた段付き嵌合穴に嵌め込まれたボール受座２４とからなるボール状継手２５を介して推力伝達軸２８に伝達される。推力伝達軸２８に連結された連結軸２９は弁本体１０の内部に固定された段付き円筒状のばねケース１９（の下部）に摺動自在に内挿されており、弁軸２０は、当該ばねケース１９により案内されて軸線Ｏ方向に移動する。また、ばねケース１９（の上向きの段差面）と推力伝達軸２８（の下向きの段差面）との間には、弁軸２０を常時開弁方向（上方）に付勢する圧縮コイルばね２６が縮装されている。 The female screw portion 13a provided on (the inner periphery of) the bearing member 13 is screwed with the male screw portion 22a provided on (the outer periphery of) the screw driving member 22 constituting the valve shaft 20. The member 22 converts the rotational movement of the output gear 57 (that is, the rotor 50) into a linear movement in the direction of the axis O (elevating direction) by the screw feed mechanism 27 including the male screw portion 22a and the female screw portion 13a. Here, the output gear 57 is rotating at a fixed position in the direction of the axis O without vertically moving, and is screwed into a slit-shaped fitting groove 59b provided at the lower end of the output shaft 59 connected to the output gear 57. A flat driver-shaped plate-like portion 22b provided at the upper end of the driving member 22 is inserted to transmit the rotational movement of the output gear 57 to the screw driving member 22 side. When the plate-shaped portion 22b provided on the screw driving member 22 slides in the fitting groove 59b of the output shaft 59 in the direction of the axis O, and the output gear 57 (rotor 50) rotates, the output gear 57 rotates. Although not moving in the axial direction, the screw driving member 22 linearly moves in the direction of the axis O by the screw feeding mechanism 27. The linear movement of the screw drive member 22 is transmitted to the thrust transmission shaft 28 via a ball-shaped joint 25 including a ball 23 and a ball seat 24 fitted in a stepped fitting hole provided in the upper portion of the thrust transmission shaft 28. Transmitted. The connecting shaft 29 connected to the thrust transmitting shaft 28 is slidably inserted in (a lower part of) a stepped cylindrical spring case 19 fixed inside the valve body 10, and the valve shaft 20 is It is guided by the spring case 19 and moves in the direction of the axis O. Further, a compression coil spring 26 that constantly urges the valve shaft 20 in the valve opening direction (upward) is provided between the spring case 19 (upward step surface) and the thrust transmission shaft 28 (downward step surface). It is disguised.

連結軸２９（の円筒部）の下端外周には、後述する連動部材３３の天井部３３ｂ（の挿通部３３ｃ周り）に係合する鍔状係止部２９ａが（外側に向けて）突設され、その鍔状係止部２９ａの下側に、複数個の横穴からなる連通口２１ｕが設けられるとともに、連結軸２９の底部中央には、縦穴からなる逆止弁口２１ｖが設けられている。連結軸２９の内部は、円筒状空所からなる収納室２１ｂとされ、その収納室２１ｂには、流入口１１と流出口１２との差圧に応じて逆止弁口２１ｖを開閉すべく（後で詳述）、ボールからなる逆止弁体２１が軸線Ｏ方向に摺動自在に収納されている。逆止弁体２１と推力伝達軸２８との間には、その上端を推力伝達軸２８の下面に設けられた突設部２８ａに外挿するようにして、前記逆止弁体２１を常時閉弁方向（下方）に付勢する圧縮コイルばね（付勢部材）２１ａが縮装されている。連結軸２９の下端面は、後述する弁体３２に設けられた弁座３５に接離して弁口３６を開閉する逆円錐台状の第２弁体部（円錐台面部）２９ｂとされる。 A flange-shaped locking portion 29a (toward the outside) that engages with (around the insertion portion 33c of) the ceiling portion 33b of the interlocking member 33 described later is provided on the outer periphery of the lower end of (the cylindrical portion of) the connecting shaft 29. A communication port 21u composed of a plurality of lateral holes is provided below the brim-shaped engaging portion 29a, and a check valve port 21v composed of a vertical hole is provided at the center of the bottom of the connecting shaft 29. The inside of the connecting shaft 29 is a storage chamber 21b formed of a cylindrical void, and the check valve port 21v is opened and closed in the storage chamber 21b according to the pressure difference between the inflow port 11 and the outflow port 12 ( The check valve body 21 made of a ball is slidably housed in the axis O direction. Between the check valve body 21 and the thrust transmission shaft 28, the check valve body 21 is normally closed so that the upper end of the check valve body 21 is externally fitted to a protruding portion 28a provided on the lower surface of the thrust transmission shaft 28. A compression coil spring (urging member) 21a for urging in the valve direction (downward) is compressed. The lower end surface of the connecting shaft 29 is a second truncated cone-shaped second valve body portion (conical surface portion) 29b that opens and closes the valve port 36 by coming into contact with and separating from a valve seat 35 provided on a valve body 32 described later.

弁体３２は、弁軸２０を構成する連結軸２９における鍔状係止部２９ａより上側に摺動自在に外挿された天井部付き円筒状の連動部材３３と、連動部材３３の下端開口に、溶接、圧入、かしめ等により連結された短円筒状の弁体部材３８とで構成され、弁体３２（の連動部材３３と弁体部材３８）によって弁軸２０（の連結軸２９）の下端部周りに画成された空間が、連通空間３４とされている。 The valve body 32 has a cylindrical interlocking member 33 with a ceiling part slidably inserted above the brim-like engaging part 29a of the connecting shaft 29 constituting the valve shaft 20, and a lower end opening of the interlocking member 33. , A short cylindrical valve body member 38 connected by welding, press fitting, caulking, etc., and the lower end of (the connecting shaft 29 of) the valve shaft 20 by (the interlocking member 33 and the valve body member 38) of the valve body 32. The space defined around the section is a communication space 34.

連動部材３３の天井部３３ｂには、連結軸２９が摺動自在に挿通される短円筒面を持つ挿通部３３ｃが設けられている。また、連動部材３３の円筒部３３ａの下端部は、弁体部材３８の外周部に設けられた鍔状部３８ａに溶接等により固着されるとともに、連動部材３３の円筒部３３ａには、弁室１４と連通空間３４を連通する複数個の（横向きの）貫通口３３ｕが設けられている（特に、図２参照）。 The ceiling portion 33b of the interlocking member 33 is provided with an insertion portion 33c having a short cylindrical surface through which the connecting shaft 29 is slidably inserted. Further, the lower end portion of the cylindrical portion 33a of the interlocking member 33 is fixed to the flange portion 38a provided on the outer peripheral portion of the valve body member 38 by welding or the like, and the cylindrical portion 33a of the interlocking member 33 has a valve chamber A plurality of (sideways) through holes 33u are provided to connect the communication space 14 and the communication space 34 (see particularly FIG. 2).

一方、弁体部材３８の下端面は、弁本体１０の弁座１５に（上側から）接離して弁口１６を開閉する逆円錐台状の第１弁体部（円錐台面部）３８ｂとされるとともに、その弁体部材３８の中央には、弁口１６と連通空間３４を連通する段付きの縦穴からなる連通路３７が形成されている。この連通路３７における連通空間３４側は、前記した弁本体１０の弁口（第１弁口）１６より小径の円筒面からなり、連結軸２９の第２弁体部２９ｂによって開閉される弁口（第２弁口）３６とされている。 On the other hand, the lower end surface of the valve body member 38 is an inverted frustoconical first valve body portion (conical frustoconical surface portion) 38b that opens and closes the valve port 16 by contacting and separating from the valve seat 15 of the valve body 10 (from above). In addition, at the center of the valve body member 38, a communication passage 37 formed of a stepped vertical hole that connects the valve opening 16 and the communication space 34 is formed. The communication space 34 side of the communication passage 37 has a cylindrical surface having a smaller diameter than the valve opening (first valve opening) 16 of the valve body 10 described above, and is opened and closed by the second valve body portion 29b of the connecting shaft 29. (Second valve port) 36.

ここで、弁軸２０の連結軸２９に設けられた鍔状係止部２９ａと連動部材３３の天井部３３ｂとは、連結軸２９の第２弁体部２９ｂによって弁口３６が閉じられたとき（言い換えれば、連結軸２９の第２弁体部２９ｂが弁口（第２弁口）３６の上端に設けられた弁座（第２弁座）３５に着座したとき）に、軸線Ｏ方向（上下方向）で所定寸法の隙間Ｌａを持つように設定されている（後で詳述）。 Here, the collar-shaped locking portion 29a provided on the connecting shaft 29 of the valve shaft 20 and the ceiling portion 33b of the interlocking member 33 are used when the valve port 36 is closed by the second valve body portion 29b of the connecting shaft 29. (In other words, when the second valve body portion 29b of the connecting shaft 29 is seated on the valve seat (second valve seat) 35 provided at the upper end of the valve opening (second valve opening) 36), the axis O direction ( It is set so as to have a gap La of a predetermined dimension in the vertical direction (detailed later).

また、ばねケース１９（の下向きの段差面）と弁体３２を構成する連動部材３３（の天井部３３ｂの上面における挿通部３３ｃ周り）との間には、弁体３２を常時閉弁方向（下方）に付勢する圧縮コイルばね（付勢部材）３９が縮装されている。 In addition, the valve body 32 is always closed in the valve closing direction between the spring case 19 (downward step surface) and the interlocking member 33 (around the insertion portion 33c on the upper surface of the ceiling 33b of the valve body 32) forming the valve body 32 ( A compression coil spring (biasing member) 39 that urges downward is compressed.

上記構成に加えて、本実施形態では、流体中（後述する小流量通路を流れる流体中）の気泡を細分化すべく、前記連動部材３３（の円筒部３３ａ）の内周に、薄肉円筒状の金属メッシュ等からなる消音部材（弁室１４側消音部材）７１が設けられるとともに、弁体部材３８の連通路３７にも、薄肉円板状の金属メッシュ等からなる消音部材（弁口１６側消音部材）７２が設けられている。 In addition to the above-described configuration, in the present embodiment, in order to subdivide air bubbles in the fluid (in the fluid flowing through a small flow passage described later), a thin-walled cylindrical shape is formed on the inner circumference of (the cylindrical portion 33a of) the interlocking member 33. A sound deadening member (a sound deadening member on the valve chamber 14 side) 71 made of a metal mesh or the like is provided, and a sound deadening member made of a thin disk-shaped metal mesh or the like (a sound deadening member on the valve opening 16 side) is also provided in the communication passage 37 of the valve body member 38. (Member) 72 is provided.

詳しくは、消音部材７１は、上端が連動部材３３（の天井部３３ｂの下面外縁）に設けられた凹部に嵌め込まれ、下端が弁体部材３８（の外周上端）と連動部材３３（の下端）とで挟持されるようにして、連動部材３３（の貫通口３３ｕ）の内周側に配在されている。また、消音部材７２は、間に当該消音部材７２を挟んで、弁体部材３８の連通路３７の段差部に複数個（図示例では、４個）の通し穴７３ａを持つ押さえ板（支持部材）７３をかしめ等により固定することによって（図３参照）、弁体部材３８の連通路３７内に支持固定されている。 Specifically, the muffling member 71 has its upper end fitted into a recess provided in the interlocking member 33 (the outer peripheral edge of the lower surface of the ceiling portion 33b thereof), and its lower end in (the upper outer peripheral end of) the valve member 38 and (the lower end of) the interlocking member 33. It is disposed on the inner peripheral side of (the through hole 33u of) the interlocking member 33 so as to be sandwiched by and. Further, the sound deadening member 72 sandwiches the sound deadening member 72 between them, and a pressing plate (supporting member) having a plurality (four in the illustrated example) of through holes 73a in the step portion of the communication passage 37 of the valve body member 38. ) 73 is fixed by caulking or the like (see FIG. 3), and is supported and fixed in the communication passage 37 of the valve body member 38.

なお、ここでは、消音部材７１、７２として、複数の小孔を有する金属メッシュ（網状部材）を採用しているが、流体中の気泡を細分化できれば、例えば、当該消音部材７１、７２を樹脂製としても良いし、当該消音部材７１、７２自体を多孔体で形成しても良い。 Although a metal mesh (mesh-shaped member) having a plurality of small holes is adopted as the sound deadening members 71, 72, if the air bubbles in the fluid can be subdivided, the sound deadening members 71, 72 are made of resin, for example. The sound deadening members 71 and 72 themselves may be formed of a porous body.

また、連動部材３３の貫通口３３ｕの数や口径や形成位置、押さえ板７３の通し穴７３ａの数や穴径や形成位置等は、図示例に限定されないことは当然であるし、各消音部材７１、７２の固定方法等についても、図示例に限定されないことは勿論である。 Further, the number of through holes 33u of the interlocking member 33, the diameter and the forming position thereof, the number of the through holes 73a of the pressing plate 73, the diameter of the hole and the forming position thereof are not limited to the illustrated examples, and each muffling member. Needless to say, the fixing method of 71 and 72 is not limited to the illustrated example.

かかる構成の流量調整弁１では、流体（冷媒）は、双方向（流入口１１から流出口１２に向かう方向（横→下、正流れ）と、流出口１２から流入口１１に向かう方向（下→横、逆流れ）との双方向）に流されるようになっており、前記ロータ４５の回転量を制御して弁軸２０のリフト量Ｌを変化させることにより、流体（冷媒）の通過流量を調整するようになっている。 In the flow rate control valve 1 having such a configuration, the fluid (refrigerant) is bidirectional (direction from the inflow port 11 to the outflow port 12 (horizontal → down, forward flow)) and direction from the outflow port 12 to the inflow port 11 (downward). The flow rate of the fluid (refrigerant) passes by changing the lift amount L of the valve shaft 20 by controlling the rotation amount of the rotor 45. Is adjusted.

＜流量調整弁１の正流れ時の動作＞
正流れ時においては、図４（Ａ）に示される如くの全閉状態（弁軸２０のリフト量Ｌが０の状態）において、弁軸２０（の連結軸２９）の第２弁体部２９ｂが弁体３２（の弁体部材３８）の弁座３５に圧接（着座）されて弁口３６が閉じられるとともに、弁体３２（の弁体部材３８）の第１弁体部３８ｂが弁本体１０の弁座１５に圧接（着座）されて弁口１６が閉じられている。また、圧縮コイルばね２１ａにより逆止弁体２１が付勢されて弁軸２０（の連結軸２９）の逆止弁口２１ｖが閉じられている（つまり、逆止弁体２１により弁室１４から弁口１６へ向かう流体の流れは遮断されている）。このとき、弁軸２０（の連結軸２９）の鍔状係止部２９ａ（の上面）と弁体３２の連動部材３３の天井部３３ｂ（の下面）とは、軸線Ｏ方向（上下方向）で所定寸法の隙間Ｌａだけ離れて位置せしめられている。 <Operation of flow rate adjusting valve 1 when the flow is normal>
At the time of forward flow, in the fully closed state (the state where the lift amount L of the valve shaft 20 is 0) as shown in FIG. 4A, the second valve body portion 29b of the valve shaft 20 (the connecting shaft 29 thereof) is Is pressed against (seats) the valve seat 35 of (the valve body member 38 of) the valve body 32 to close the valve port 36, and the first valve body portion 38b of the (valve body member 38 of) the valve body 32 is the valve body. The valve opening 16 is closed by being pressed (seated) to the valve seat 15 of the valve 10. Further, the check valve body 21 is biased by the compression coil spring 21a to close the check valve port 21v of (the connecting shaft 29 of) the valve shaft 20 (that is, from the valve chamber 14 by the check valve body 21). The flow of fluid toward the valve port 16 is blocked). At this time, the collar-shaped locking portion 29a (the upper surface) of the valve shaft 20 (the connecting shaft 29 of the valve shaft 20) and the ceiling portion 33b (the lower surface) of the interlocking member 33 of the valve body 32 are arranged in the direction of the axis O (vertical direction). They are located apart from each other by a gap La having a predetermined dimension.

この全閉状態において、弁軸２０を上昇させると、図４（Ｂ）に示される如くに、前記所定寸法の隙間（リフト量）Ｌａまでは（小流量制御状態）、弁体３２の第１弁体部３８ｂが圧縮コイルばね３９（の付勢力）により弁本体１０の弁座１５に圧接（着座）され、かつ、逆止弁体２１が圧縮コイルばね２１ａ（の付勢力）により付勢されて弁軸２０の逆止弁口２１ｖが閉じられたままで、弁軸２０の連結軸２９が弁体３２（の連動部材３３の天井部３３ｂ）の挿通部３３ｃ内を摺動するようにして弁軸２０が移動（上昇）せしめられ、弁軸２０の第２弁体部２９ｂが弁体３２の弁座３５から離れて弁口３６が開口せしめられる。流入口１１から弁室１４に流れ込んだ流体は、弁体３２の連動部材３３（の円筒部３３ａ）の貫通口３３ｕ→連通空間３４→弁軸２０の第２弁体部２９ｂと弁体３２の弁座３５との隙間→弁体３２の弁体部材３８の連通路３７（弁口３６）（特に、その連通路３７に固定された押さえ板７３の通し穴７３ａ）を介して、その下方に続く弁口１６に流れ込み、弁軸２０の上昇に伴って、当該弁口１６に流れ込む流体の流量が次第に大きくなる。このとき、流入口１１から弁室１４に流れ込んだ流体は、（弁体３２の連動部材３３の貫通口３３ｕから連通空間３４に流れ込む際に）連動部材３３（の円筒部３３ａ）の内周に配在された消音部材７１を通過するとともに、（弁体３２の弁体部材３８の連通路３７から弁口１６に流れ込む際に）連通路３７に配在された消音部材７２を通過し、弁口３６より上流側（弁室１４側）及び下流側（弁口１６側）に配置された２つの消音部材７１、７２によって流体中の気泡が分解されて細分化された状態で、弁口１６（流出口１２）を通過することになる。そのため、小流量制御（小開度）領域（騒音が発生しやすい領域）において、流体（冷媒）通過時の騒音が確実に低減される。 In this fully closed state, when the valve shaft 20 is raised, as shown in FIG. 4B, the gap (lift amount) La of the predetermined dimension (the small flow rate control state) is maintained until the valve body 32 moves to the first position. The valve body portion 38b is pressed against (seats) the valve seat 15 of the valve body 10 by (the biasing force of) the compression coil spring 39, and the check valve body 21 is biased by (the biasing force of) the compression coil spring 21a. The check valve port 21v of the valve shaft 20 remains closed, and the connecting shaft 29 of the valve shaft 20 slides in the insertion portion 33c of the valve body 32 (the ceiling 33b of the interlocking member 33). The shaft 20 is moved (raised), the second valve body portion 29b of the valve shaft 20 is separated from the valve seat 35 of the valve body 32, and the valve port 36 is opened. The fluid that has flowed into the valve chamber 14 from the inflow port 11 passes through the through hole 33u of the interlocking member 33 (of the cylindrical portion 33a) of the valve body 32 → the communication space 34 → the second valve body portion 29b of the valve shaft 20 and the valve body 32. Gap between the valve seat 35 and the lower part thereof via the communication passage 37 (valve port 36) of the valve body member 38 of the valve body 32 (in particular, the through hole 73a of the pressing plate 73 fixed to the communication passage 37). The flow rate of the fluid flowing into the subsequent valve opening 16 gradually increases as the valve shaft 20 rises. At this time, the fluid that has flowed into the valve chamber 14 from the inflow port 11 is (when flowing into the communication space 34 from the through hole 33u of the interlocking member 33 of the valve body 32) to the inner periphery of (the cylindrical portion 33a of) the interlocking member 33. The valve passes through the silencer member 71 disposed in the communication passage 37 (when flowing into the valve port 16 from the communication passage 37 of the valve body member 38 of the valve body 32) while passing through the silencer member 71 disposed in the valve body 32. In the state where air bubbles in the fluid are decomposed and subdivided by the two silencing members 71 and 72 arranged on the upstream side (valve chamber 14 side) and the downstream side (valve port 16 side) of the mouth 36, the valve mouth 16 It will pass through (outlet 12). Therefore, in the small flow rate control (small opening) region (the region where noise is likely to occur), noise when the fluid (refrigerant) passes is reliably reduced.

ここでは、前記した弁体３２の連動部材３３（の円筒部３３ａ）の貫通口３３ｕ→連通空間３４→弁軸２０の第２弁体部２９ｂと弁体３２の弁座３５との隙間→弁体３２の弁体部材３８の連通路３７（弁口３６）を介して弁室１４と弁口１６とを連通する流路を、小流量通路と称する。 Here, the through hole 33u of (the cylindrical portion 33a of) the interlocking member 33 of the valve element 32 described above → the communication space 34 → the gap between the second valve element portion 29b of the valve shaft 20 and the valve seat 35 of the valve element 32 → the valve A flow path that connects the valve chamber 14 and the valve opening 16 via the communication path 37 (valve opening 36) of the valve body member 38 of the body 32 is referred to as a small flow path.

なお、前記リフト量Ｌａは、流体（冷媒）通過時における騒音（流体通過音）が発生しやすい流量に対応する弁軸２０のリフト量Ｌであり、実験等に基づき予め決めることができる。 The lift amount La is a lift amount L of the valve shaft 20 corresponding to a flow rate at which noise (fluid passing sound) easily occurs when a fluid (refrigerant) passes, and can be determined in advance based on experiments and the like.

弁軸２０を前記リフト量Ｌａまで上昇させた後、さらに上昇させる（つまり、リフト量Ｌが前記リフト量Ｌａを超える）と、図４（Ｃ）に示される如くに、弁軸２０（の連結軸２９）の鍔状係止部２９ａが弁体３２（の連動部材３３の天井部３３ｂ）と係合し、弁体３２は、圧縮コイルばね３９の付勢力に抗して弁軸２０とともに（一体に）移動（上昇）せしめられ、弁体３２の第１弁体部３８ｂが弁本体１０の弁座１５から離れ、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との間に（軸線Ｏ方向の）幅Ｌｂ（＝Ｌ−Ｌａ）の隙間（円環状の流路）が形成される（大流量制御状態）。流入口１１から弁室１４に流れ込んだ流体は、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との隙間を介して、その下方に続く弁口１６に流れ込み、弁軸２０の上昇に伴って、当該弁口１６に流れ込む流体の流量が次第に大きくなる。このとき、流入口１１から弁室１４に流れ込んだ流体は、一部は、前述のように弁体３２の連動部材３３（の円筒部３３ａ）の貫通口３３ｕ等を通過し、消音部材７１、７２によって流体中の気泡が分解されて細分化された状態で、弁口１６（流出口１２）を通過するものの、その大部分は、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との間に形成された隙間（流路）を通過して、弁口１６（流出口１２）に直接流れ込むことになる。そのため、弁軸２０のリフト量Ｌが比較的大きい大流量制御（大開度）領域（騒音が発生しにくい領域であって、流量を確保したい領域）において、圧力損失（圧損）が小さくなる。 When the valve shaft 20 is raised to the lift amount La and then further raised (that is, the lift amount L exceeds the lift amount La), as shown in FIG. The collar-shaped locking portion 29a of the shaft 29) engages with (the ceiling portion 33b of the interlocking member 33 of) the valve body 32, and the valve body 32 resists the biasing force of the compression coil spring 39 and the valve shaft 20 ( (Moved together), the first valve body portion 38b of the valve body 32 is separated from the valve seat 15 of the valve body 10, and the first valve body portion 38b of the valve body 32 and the valve seat 15 of the valve body 10 are moved. A gap (annular flow path) having a width Lb (= L-La) (in the direction of the axis O) is formed between (the large flow rate control state). The fluid flowing from the inflow port 11 into the valve chamber 14 flows through the gap between the first valve body portion 38b of the valve body 32 and the valve seat 15 of the valve body 10 into the valve port 16 continuing below, and the valve shaft As the valve 20 rises, the flow rate of the fluid flowing into the valve port 16 gradually increases. At this time, a part of the fluid flowing into the valve chamber 14 from the inflow port 11 passes through the through hole 33u of the interlocking member 33 (the cylindrical portion 33a thereof) of the valve body 32 as described above, and the sound deadening member 71, The air bubbles in the fluid are decomposed and fragmented by 72 and pass through the valve port 16 (outlet port 12), but most of them pass through the first valve body portion 38 b of the valve body 32 and the valve body 10. It will pass through the gap (flow path) formed between the valve seat 15 and flow directly into the valve port 16 (outflow port 12). Therefore, the pressure loss (pressure loss) is small in a large flow rate control (large opening) region (a region where noise is unlikely to occur and a flow amount is to be secured) in which the lift amount L of the valve shaft 20 is relatively large.

なお、図４（Ｃ）に示される如くの全開状態から弁軸２０を下降させ、弁口１６に流れ込む流体の流量が次第に減少する場合にも、上記と同様の作用効果が得られることは言うまでも無い。 It should be noted that, even when the valve shaft 20 is lowered from the fully opened state as shown in FIG. 4 (C) and the flow rate of the fluid flowing into the valve port 16 is gradually reduced, it is said that the same effect as the above can be obtained. There is no limit.

＜流量調整弁１の逆流れ時の動作＞
逆流れ時においては、図５（Ａ）に示される如くの全閉状態（図４（Ａ）に基づき説明した状態）において、弁口１６側（流出口１２側）と弁室１４側（流入口１１）との差圧が所定の差圧より大きくなる（言い換えれば、弁口１６側の圧力が弁室１４側の圧力より所定圧だけ高くなる）と、図５（Ｂ）に示される如くに、弁軸２０（の連結軸２９）の第２弁体部２９ｂが弁体３２（の弁体部材３８）の弁座３５に圧接（着座）され、弁体３２（の弁体部材３８）の第１弁体部３８ｂが弁本体１０の弁座１５に圧接（着座）されたままで、圧縮コイルばね２１ａの付勢力に抗して逆止弁体２１が収納室２１ｂ内で移動（上昇）せしめられ、弁軸２０（の連結軸２９）の逆止弁口２１ｖが開口せしめられる。流出口１２（の弁口１６）から流れ込んだ流体は、弁体３２の弁体部材３８の連通路３７（弁口３６）（特に、その連通路３７に固定された押さえ板７３の通し穴７３ａ）→弁軸２０の連結軸２９（の底部）の逆止弁口２１ｖ→収納室２１ｂ→連通口２１ｕ→連通空間３４→弁体３２の連動部材３３（の円筒部３３ａ）の貫通口３３ｕを介して、弁室１４に流れ込む。なお、この状態では、当該弁室１４に流れ込む流体（つまり、流入口１１へ流れ出る流体）が流通する流路の開口面積は一定である。このとき、流出口１２から流れ込んだ流体は、（弁口１６から弁体３２の弁体部材３８の連通路３７に流れ込む際に）弁体部材３８の連通路３７に配在された消音部材７２を通過するとともに、（連通空間３４から弁体３２の連動部材３３の貫通口３３ｕに流れ込む際に）連動部材３３（の円筒部３３ａ）の内周に配在された消音部材７１を通過し、弁口３６より上流側（弁口１６側）及び下流側（弁室１４側）に配置された２つの消音部材７２、７１によって流体中の気泡が分解されて細分化された状態で、弁室１４（流入口１１）を通過することになる。そのため、小流量制御領域（騒音が発生しやすい領域）において、流体（冷媒）通過時の騒音が確実に低減される。 <Operation of flow rate adjusting valve 1 at the time of reverse flow>
At the time of reverse flow, in the fully closed state as shown in FIG. 5A (the state described based on FIG. 4A), the valve port 16 side (outlet port 12 side) and the valve chamber 14 side (flow port). When the pressure difference with the inlet 11) becomes larger than a predetermined pressure difference (in other words, the pressure on the valve port 16 side becomes higher than the pressure on the valve chamber 14 side by a predetermined pressure), as shown in FIG. 5B. Then, the second valve body portion 29b of (the connecting shaft 29 of) the valve shaft 20 is pressed against (seats) the valve seat 35 of (the valve body member 38 of) the valve body 32, and (the valve body member 38 of) the valve body 32. The first check valve body 21 moves (raises) in the storage chamber 21b against the urging force of the compression coil spring 21a while the first valve body portion 38b of the valve body 10 is kept in pressure contact (seated) with the valve seat 15 of the valve body 10. The check valve port 21v of (the connecting shaft 29 of) the valve shaft 20 is opened. The fluid flowing from (the valve opening 16 of) the outflow port 12 has a communication passage 37 (valve opening 36) of the valve body member 38 of the valve body 32 (particularly, a through hole 73 a of the pressing plate 73 fixed to the communication passage 37). )-> Check valve port 21v of (the bottom of) the connecting shaft 29 of the valve shaft 20-> storage chamber 21b-> communication port 21u-> communication space 34-> through hole 33u of the interlocking member 33 (cylindrical part 33a) of the valve body 32. Through the valve chamber 14. In this state, the opening area of the flow path through which the fluid flowing into the valve chamber 14 (that is, the fluid flowing out to the inflow port 11) flows is constant. At this time, the fluid flowing from the outflow port 12 (when flowing from the valve port 16 into the communication passage 37 of the valve body member 38 of the valve body 32) is disposed in the communication passage 37 of the valve body member 38. While passing through (when flowing into the through hole 33u of the interlocking member 33 of the valve body 32 from the communication space 34) through the sound deadening member 71 disposed on the inner periphery of (the cylindrical portion 33a of) the interlocking member 33, In the state where air bubbles in the fluid are decomposed and subdivided by the two silencing members 72, 71 arranged on the upstream side (the valve opening 16 side) and the downstream side (the valve chamber 14 side) of the valve opening 36, the valve chamber 14 (inflow port 11) will be passed. Therefore, in the small flow rate control region (a region where noise is likely to occur), noise during passage of the fluid (refrigerant) is reliably reduced.

この逆止弁口２１ｖが開かれた状態において、弁軸２０を上昇させると、図５（Ｃ）に示される如くに、弁軸２０の第２弁体部２９ｂが弁体３２の弁座３５に圧接（着座）されたままで（つまり、弁軸２０の鍔状係止部２９ａと連動部材３３の天井部３３ｂとが軸線Ｏ方向で所定寸法の隙間Ｌａだけ離れて位置せしめられたままで）、弁体３２は、圧縮コイルばね３９の付勢力に抗して（すなわち、弁口１６から弁室１４に流れ込む流体の圧力が圧縮コイルばね３９の付勢力に打ち勝って）弁軸２０とともに（一体に）移動（上昇）せしめられ、弁体３２の第１弁体部３８ｂが弁本体１０の弁座１５から離れ、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との間に（軸線Ｏ方向の）幅Ｌの隙間（円環状の流路）が形成される。それに伴い、逆止弁体２１は、圧縮コイルばね２１ａの付勢力により収納室２１ｂ内で移動せしめられ、弁軸２０（の連結軸２９）の逆止弁口２１ｖが閉じられる。流出口１２（の弁口１６）に流れ込んだ流体は、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との隙間を介して、弁室１４に流れ込み、弁軸２０の上昇に伴って、当該弁室１４に流れ込む流体の流量が次第に大きくなる。このとき、流出口１２（の弁口１６）から流れ込んだ流体は、弁体３２の第１弁体部３８ｂと弁本体１０の弁座１５との間に形成された隙間（流路）を通過して、弁室１４（流入口１１）に直接流れ込むことになる。そのため、弁軸２０のリフト量Ｌが比較的大きい大流量制御領域（騒音が発生しにくい領域であって、流量を確保したい領域）において、圧力損失（圧損）が小さくなる。 When the valve shaft 20 is raised with the check valve port 21v opened, the second valve body portion 29b of the valve shaft 20 causes the valve seat 35 of the valve body 32 to rise, as shown in FIG. 5C. While being pressed against (seated to) (that is, with the collar-like locking portion 29a of the valve shaft 20 and the ceiling portion 33b of the interlocking member 33 being positioned apart from each other by a gap La of a predetermined dimension in the direction of the axis O), The valve body 32 resists the biasing force of the compression coil spring 39 (that is, the pressure of the fluid flowing from the valve opening 16 into the valve chamber 14 overcomes the biasing force of the compression coil spring 39) and the valve shaft 20 (integrally). ) The first valve body portion 38b of the valve body 32 is moved (raised) away from the valve seat 15 of the valve body 10, and the first valve body portion 38b of the valve body 32 and the valve seat 15 of the valve body 10 are separated from each other. A gap (annular flow path) having a width L (in the direction of the axis O) is formed at. Accordingly, the check valve body 21 is moved in the storage chamber 21b by the urging force of the compression coil spring 21a, and the check valve port 21v of (the connecting shaft 29 of) the valve shaft 20 is closed. The fluid that has flowed into (the valve port 16 of) the outflow port 12 flows into the valve chamber 14 through the gap between the first valve body portion 38 b of the valve body 32 and the valve seat 15 of the valve body 10, and the fluid of the valve shaft 20 As the temperature rises, the flow rate of the fluid flowing into the valve chamber 14 gradually increases. At this time, the fluid flowing in from (the valve opening 16 of) the outflow port 12 passes through a gap (flow passage) formed between the first valve body portion 38b of the valve body 32 and the valve seat 15 of the valve body 10. Then, it directly flows into the valve chamber 14 (inflow port 11). Therefore, the pressure loss (pressure loss) is small in the large flow rate control region where the lift amount L of the valve shaft 20 is relatively large (the region where noise is unlikely to occur and the flow rate is desired to be secured).

このように、本実施形態の流量調整弁１では、連通空間３４を介して弁室１４と弁口（第１弁口）１６とを連通する小流量通路における弁口（第２弁口）３６より弁室１４側（正流れ時で上流側、逆流れ時で下流側）及び弁口１６側（正流れ時で下流側、逆流れ時で上流側）、具体的には、弁体３２の連動部材３３における貫通口３３ｕ及び弁体部材３８における連通路３７に、当該小流量通路を流れる流体中の気泡を細分化する消音部材７１、７２が配在されているので、流体（冷媒）通過時における騒音を効果的に低減できるとともに、大開度（大流量制御）領域における圧力損失が小さくなり、適正な冷媒流量を得ることができる。 As described above, in the flow rate adjusting valve 1 of the present embodiment, the valve opening (second valve opening) 36 in the small flow path that connects the valve chamber 14 and the valve opening (first valve opening) 16 via the communication space 34. The valve chamber 14 side (upstream side in normal flow, downstream side in reverse flow) and the valve port 16 side (downstream side in normal flow, upstream side in reverse flow), specifically, of the valve element 32 Since the silencing members 71 and 72 for subdividing the bubbles in the fluid flowing through the small flow passage are arranged in the through hole 33u in the interlocking member 33 and the communication passage 37 in the valve body member 38, the fluid (refrigerant) passage. It is possible to effectively reduce the noise at the time, reduce the pressure loss in the large opening (large flow rate control) region, and obtain an appropriate refrigerant flow rate.

なお、弁体３２の第１弁体部３８ｂにより弁口１６が閉じられ、かつ、弁軸２０の第２弁体部２９ｂにより弁口３６が閉じられた状態で、弁口１６から弁室１４へ向かう流体の流れを許容するが、弁室１４から弁口１６へ向かう流体の流れを遮断する逆止弁体２１を用いた逆止弁構造は、上記した構造に限定されない。例えば、図６（Ａ）に示されるように、逆止弁体２１と推力伝達軸２８との間に介装される圧縮コイルばね２１ａを省略しても良い。この場合、収納室２１ｂ内での逆止弁体２１の移動量を制限するために、推力伝達軸２８の下面に形成した突設部２８ａを逆止弁体２１に近接して配置するようにしても良い。また、収納室２１ｂ内に配置した逆止弁体２１による音（衝突音）を抑えるために、例えば、図６（Ｂ）に示されるように、推力伝達軸２８の下面に形成した突設部２８ａを樹脂製あるいはゴム製の緩衝材などの別部品で形成しても良い。また、例えば、図６（Ｃ）に示されるように、逆止弁体２１を、段付き円柱状（連結軸２９の内径とほぼ同じ外径を有する円柱状）かつ逆止弁口２１ｖを開閉する円錐台面部を持つように形成し、弁軸２０の連結軸２９（の円筒部）に、収納室２１ｂにおける逆止弁体２１の背面側（逆止弁口２１ｖ側とは反対側）と弁室１４とを連通する均圧口２９ｄを形成しても良い。 The valve opening 16 is closed from the valve opening 16 with the first valve body portion 38b of the valve body 32 closing the valve opening 16 and the second valve body portion 29b of the valve shaft 20 closing the valve opening 36. The check valve structure using the check valve body 21 that allows the flow of the fluid toward the valve chamber but blocks the flow of the fluid from the valve chamber 14 toward the valve opening 16 is not limited to the above-described structure. For example, as shown in FIG. 6 (A), the compression coil spring 21a interposed between the check valve body 21 and the thrust transmission shaft 28 may be omitted. In this case, in order to limit the amount of movement of the check valve body 21 in the storage chamber 21b, the projecting portion 28a formed on the lower surface of the thrust transmission shaft 28 is arranged close to the check valve body 21. May be. Further, in order to suppress the sound (collision sound) by the check valve body 21 arranged in the storage chamber 21b, for example, as shown in FIG. 6 (B), a protruding portion formed on the lower surface of the thrust transmission shaft 28. 28a may be formed by another component such as a resin or rubber cushioning material. Further, for example, as shown in FIG. 6C, the check valve body 21 has a stepped cylindrical shape (a cylindrical shape having an outer diameter substantially the same as the inner diameter of the connecting shaft 29) and a check valve opening 21v. The connecting shaft 29 of the valve shaft 20 (the cylindrical portion thereof) has a rear side of the check valve body 21 in the storage chamber 21b (a side opposite to the check valve port 21v side). A pressure equalizing port 29d that communicates with the valve chamber 14 may be formed.

また、上記実施形態では、前記した逆止弁体２１を利用し、流体（冷媒）を、流入口１１から流出口１２に向かう方向（正流れ）と、流出口１２から流入口１１に向かう方向（逆流れ）との双方向に流すようにしているが、例えば、流体（冷媒）を一方向（流入口１１から流出口１２に向かう方向（正流れ）であって、逆止弁体２１が機能せずに当該逆止弁体２１により逆止弁口２１ｖが常時閉じられたままである方向）のみに流すシステムに適用する場合には、図７に示される流量調整弁１Ａの如くに、弁軸２０の連結軸２９を中実（段付き円柱状）に形成し、前記した逆止弁体２１及びそれに付随する構造（収納室２１ｂ、逆止弁口２１ｖ、連通口２１ｕ）を省略しても良い。なお、図７において、上記実施形態と同様の機能及び作用を有する構成には、同様の符号が付されている。かかる構成の流量調整弁１Ａでも、上記実施形態の流量調整弁１と同様の作用効果が得られることは言うまでも無い。 Further, in the above-described embodiment, the check valve body 21 is used to flow the fluid (refrigerant) from the inlet 11 to the outlet 12 (forward flow) and from the outlet 12 to the inlet 11. Although it is made to flow in both directions (reverse flow), for example, the fluid (refrigerant) is unidirectional (direction from the inlet 11 to the outlet 12 (forward flow), and the check valve body 21 is When it is applied to a system which does not function and flows only in the direction in which the check valve body 21v is always closed by the check valve body 21), a valve such as the flow rate adjusting valve 1A shown in FIG. 7 is used. The connecting shaft 29 of the shaft 20 is formed to be solid (columnar shape with steps), and the above-mentioned check valve body 21 and the structures (accommodation chamber 21b, check valve port 21v, communication port 21u) accompanying it are omitted. Is also good. Note that, in FIG. 7, configurations having the same functions and actions as those of the above-described embodiment are denoted by the same reference numerals. It goes without saying that the flow rate adjusting valve 1A having such a configuration can also obtain the same effects as the flow rate adjusting valve 1 of the above-described embodiment.

また、上記実施形態では、ロータ５０の回転数を減速する不思議遊星歯車減速機構６０を利用しているが、例えば、図８に示される流量調整弁１Ｂの如くに、不思議遊星歯車減速機構を省略し、弁軸２０（の推力伝達軸２８）の外周にベローズ２８Ｂを取り付け、推力伝達軸２８（の段差部）と連結軸２９（の上端部）で挟持されたリング状の上側ばね受け２８Ｂａと弁体３２の連動部材３３の天井部３３ｂとの間に、弁体３２を閉弁方向（下方）に付勢する付勢部材としての圧縮コイルばね３９を介装しても良い（詳細構造については、上記特許文献２も併せて参照）。なお、図８において、上記実施形態と同様の機能及び作用を有する構成には、同様の符号が付されている。かかる構成の流量調整弁１Ｂでも、上記実施形態の流量調整弁１と同様の作用効果が得られることは詳述するまでも無い。 Further, in the above-described embodiment, the mysterious planetary gear reduction mechanism 60 that reduces the rotation speed of the rotor 50 is used, but the mysterious planetary gear reduction mechanism is omitted, for example, as in the flow rate adjusting valve 1B shown in FIG. Then, a bellows 28B is attached to the outer periphery of (the thrust transmission shaft 28 of) the valve shaft 20 and a ring-shaped upper spring bearing 28Ba sandwiched between (the stepped portion of) the thrust transmission shaft 28 and (the upper end portion) of the connection shaft 29. A compression coil spring 39 as a biasing member that biases the valve body 32 in the valve closing direction (downward) may be interposed between the valve body 32 and the ceiling portion 33b of the interlocking member 33 (for detailed structure). (See also Patent Document 2 above). Note that, in FIG. 8, configurations having the same functions and actions as those of the above-described embodiment are denoted by the same reference numerals. It is needless to say that the flow rate adjusting valve 1B having such a configuration can also obtain the same operational effects as the flow rate adjusting valve 1 of the above-described embodiment.

また、上記実施形態において、圧縮コイルばね３９を取り付けずに流量調整弁を構成することも可能である。この場合、弁体３２は、主に流体圧によって弁座１５に着座若しくは弁座１５から離間する。 Further, in the above embodiment, the flow rate adjusting valve can be configured without attaching the compression coil spring 39. In this case, the valve element 32 is seated on the valve seat 15 or separated from the valve seat 15 mainly by fluid pressure.

なお、本発明は、上述の実施形態で説明したような、ステータとロータとを有するステッピングモータ等を用いて弁軸を昇降（移動）させてリフト量（弁開度）を任意に細かく調整する電動式の流量調整弁の他、例えばソレノイド等を用いた電磁式の流量調整（切換）弁にも採用し得ることは勿論である。 In the present invention, the lift amount (valve opening degree) is arbitrarily and finely adjusted by moving up and down (moving) the valve shaft by using the stepping motor or the like having the stator and the rotor as described in the above embodiment. It is needless to say that it can be applied to an electromagnetic type flow rate adjusting (switching) valve using, for example, a solenoid as well as the electric type flow rate adjusting valve.

１流量調整弁
１０弁本体
１１流入口
１１Ａ管継手
１２流出口
１２Ａ管継手
１４弁室
１５弁座（第１弁座）
１６弁口（第１弁口）
２０弁軸
２１逆止弁体
２１ａ圧縮コイルばね
２１ｂ収納室
２１ｕ連通口
２１ｖ逆止弁口
２２ねじ駆動部材
２７ねじ送り機構
２８推力伝達軸
２９連結軸
２９ａ鍔状係止部
２９ｂ第２弁体部（円錐台面部）
３０キャン
３２弁体
３３連動部材
３３ａ連動部材の円筒部
３３ｂ連動部材の天井部
３３ｃ挿通部
３３ｕ貫通口
３４連通空間
３５弁座（第２弁座）
３６弁口（第２弁口）
３７連通路
３８弁体部材
３８ｂ第１弁体部（円錐台面部）
３９圧縮コイルばね（付勢部材）
４０ステータ
５０ロータ
６０不思議遊星歯車減速機構
６３ステッピングモータ（昇降駆動部）
７１消音部材（弁室側消音部材）
７２消音部材（弁口側消音部材）
７３押さえ板（支持部材）
７３ａ押さえ板の通し穴 1 Flow Control Valve 10 Valve Body 11 Inlet 11A Pipe Joint 12 Outlet 12A Pipe Joint 14 Valve Chamber 15 Valve Seat (First Valve Seat)
16 valve mouth (first valve mouth)
20 valve shaft 21 non-return valve body 21a compression coil spring 21b storage chamber 21u communication port 21v non-return valve port 22 screw drive member 27 screw feed mechanism 28 thrust transmission shaft 29 connecting shaft 29a collar-shaped locking portion 29b second valve body portion (Conical surface)
30 can 32 valve body 33 interlocking member 33a interlocking member cylindrical portion 33b interlocking member ceiling 33c insertion portion 33u through hole 34 communication space 35 valve seat (second valve seat)
36 valve (2nd valve)
37 communication passage 38 valve body member 38b first valve body portion (conical surface portion)
39 Compression coil spring (biasing member)
40 stator 50 rotor 60 mysterious planetary gear speed reduction mechanism 63 stepping motor (elevation drive unit)
71 Noise reduction member (valve chamber side noise reduction member)
72 Noise reduction member (Valve side noise reduction member)
73 Presser plate (support member)
73a Through hole for the holding plate

Claims

A valve body provided with a valve chamber and a first valve opening, a valve shaft vertically movable in the valve chamber, a lifting drive unit for lifting the valve shaft, and an outer periphery of a lower end of the valve shaft. And a valve element that is slidably inserted into the valve shaft so as to surround the valve shaft and that is driven in association with the lifting operation of the valve shaft.
The valve body is provided with a first valve body section that changes a flow rate of a fluid flowing through the first valve opening according to a lift amount,
A small flow passage that connects the valve chamber and the first valve opening is formed through a communication space defined by the valve body around the lower end of the valve shaft, and the valve shaft has a lift amount. A second valve body portion that changes the flow rate of the fluid flowing through the second valve opening provided in the small flow passage according to
When the lift amount of the second valve body portion is less than or equal to a predetermined amount, the first valve body portion closes the first valve opening, and the first valve body portion closes the second valve body portion according to the lift amount of the second valve body portion. When the lift amount of the second valve body portion exceeds the predetermined amount, the valve body is lifted as the valve shaft is lifted, and the first valve is lifted. The body is configured to take a large flow rate control state in which the first valve opening is opened,
A sound deadening member that subdivides air bubbles in the fluid flowing through the small flow passage is disposed on the valve chamber side and the first valve opening side of the small flow passage from the second valve opening ,
The valve body is connected to a cylindrical interlocking member slidably inserted above the second valve body section of the valve shaft and a lower end opening of the interlocking member, and the first valve body section is It is configured with the provided valve body member,
The small flow passage is provided in the interlocking member for communicating the valve chamber with the communication space, the communication space, and the valve body member for communicating the communication space with the first valve port. And a second valve port is formed in the communication passage,
The sound deadening member is disposed in the through hole of the interlocking member and the communication passage of the valve body member,
A flow rate adjusting valve, wherein a cylindrical silencing member is provided on the inner circumference of the interlocking member .

A valve body provided with a valve chamber and a first valve opening, a valve shaft vertically movable in the valve chamber, a lifting drive unit for lifting the valve shaft, and an outer periphery of a lower end of the valve shaft. And a valve element that is slidably inserted into the valve shaft so as to surround the valve shaft and that is driven in association with the lifting operation of the valve shaft.
The valve body is provided with a first valve body section that changes a flow rate of a fluid flowing through the first valve opening according to a lift amount,
A small flow passage that connects the valve chamber and the first valve opening is formed through a communication space defined by the valve body around the lower end of the valve shaft, and the valve shaft has a lift amount. A second valve body portion that changes the flow rate of the fluid flowing through the second valve opening provided in the small flow passage according to
When the lift amount of the second valve body portion is less than or equal to a predetermined amount, the first valve body portion closes the first valve opening, and the first valve body portion closes the second valve body portion according to the lift amount of the second valve body portion. When the lift amount of the second valve body portion exceeds the predetermined amount, the valve body is lifted as the valve shaft is lifted, and the first valve is lifted. The body is configured to take a large flow rate control state in which the first valve opening is opened,
A sound deadening member that subdivides air bubbles in the fluid flowing through the small flow passage is disposed on the valve chamber side and the first valve opening side of the small flow passage from the second valve opening ,
The valve body is connected to a cylindrical interlocking member slidably inserted above the second valve body section of the valve shaft and a lower end opening of the interlocking member, and the first valve body section is It is configured with the provided valve body member,
The small flow passage is provided in the interlocking member for communicating the valve chamber with the communication space, the communication space, and the valve body member for communicating the communication space with the first valve port. And a second valve port is formed in the communication passage,
The sound deadening member is disposed in the through hole of the interlocking member and the communication passage of the valve body member,
A flow rate adjusting valve , wherein the silencing member is fixed to the communication passage of the valve body member and is fixed to the communication passage of the valve body member by a support member having a through hole .

A valve body provided with a valve chamber and a first valve opening, a valve shaft vertically movable in the valve chamber, a lifting drive unit for lifting the valve shaft, and an outer periphery of a lower end of the valve shaft. And a valve element that is slidably inserted into the valve shaft so as to surround the valve shaft and that is driven in association with the lifting operation of the valve shaft.
The valve body is provided with a first valve body section that changes a flow rate of a fluid flowing through the first valve opening according to a lift amount,
A small flow passage that connects the valve chamber and the first valve opening is formed through a communication space defined by the valve body around the lower end of the valve shaft, and the valve shaft has a lift amount. A second valve body portion that changes the flow rate of the fluid flowing through the second valve opening provided in the small flow passage according to
When the lift amount of the second valve body portion is less than or equal to a predetermined amount, the first valve body portion closes the first valve opening, and the first valve body portion closes the second valve body portion according to the lift amount of the second valve body portion. When the lift amount of the second valve body portion exceeds the predetermined amount, the valve body is lifted as the valve shaft is lifted, and the first valve is lifted. The body is configured to take a large flow rate control state in which the first valve opening is opened,
A sound deadening member that subdivides air bubbles in the fluid flowing through the small flow passage is disposed on the valve chamber side and the first valve opening side of the small flow passage from the second valve opening ,
With the first valve body section closing the first valve opening and the second valve body section closing the second valve opening, the fluid flowing from the first valve opening toward the valve chamber A flow control valve, which is provided with a check valve body that allows a flow but blocks a flow of fluid from the valve chamber toward the first valve opening .

When the valve body is biased by the biasing member in the valve closing direction of the first valve opening, and the lift amount of the second valve body portion exceeds the predetermined amount, a collar provided on the valve shaft is provided. The flow regulating valve according to any one of claims 1 to 3, characterized in that it is adapted to be pulled up against the urging force of the urging member by means of a linear locking portion.

The valve body is connected to a cylindrical interlocking member slidably inserted above the second valve body section of the valve shaft and a lower end opening of the interlocking member, and the first valve body section is The flow rate adjusting valve according to claim 3 , wherein the flow rate adjusting valve includes a valve body member provided.

The small flow passage is provided in the interlocking member for communicating the valve chamber with the communication space, the communication space, and the valve body member for communicating the communication space with the first valve port. And a second valve port is formed in the communication passage,
The flow control valve according to claim 5 , wherein the sound deadening member is disposed in the through hole of the interlocking member and the communication passage of the valve body member.

7. The flow rate adjusting valve according to claim 6 , wherein a cylindrical silencing member is provided on the inner circumference of the interlocking member.

The cylindrical silencing member is disposed on the inner periphery of the interlocking member such that the upper end is fitted into the recess provided in the interlocking member and the lower end is sandwiched between the valve body member and the interlocking member. The flow rate adjusting valve according to claim 1 , wherein the flow rate adjusting valve is provided.

Is fixed to the communicating passage of the valve member, the support member having a through hole, claims 1 or 6 wherein the silencing member is characterized in that it is supported and fixed to said communication passage of the valve member 8 The flow control valve according to any one of 1.

A storage chamber in which the check valve body is stored in the valve shaft, the storage chamber communicates with the storage chamber and the first valve port, and the storage chamber is connected to the first valve port side and the valve chamber side in accordance with a pressure difference between the first valve port side and the valve chamber side. The flow control valve according to claim 3 , wherein a check valve opening and closing by a check valve body, and a communication port that is always in communication with the storage chamber and the valve chamber are provided.