JP2022022689A - Flow control valve and refrigeration cycle system - Google Patents

Flow control valve and refrigeration cycle system Download PDF

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JP2022022689A
JP2022022689A JP2020114274A JP2020114274A JP2022022689A JP 2022022689 A JP2022022689 A JP 2022022689A JP 2020114274 A JP2020114274 A JP 2020114274A JP 2020114274 A JP2020114274 A JP 2020114274A JP 2022022689 A JP2022022689 A JP 2022022689A
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valve
control valve
port
resistance portion
rectifying member
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JP7349963B2 (en
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亮司 小池
Ryoji Koike
英樹 南澤
Hideki Minamizawa
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to CN202110632600.XA priority patent/CN113883325A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/08—Means in valves for absorbing fluid energy for decreasing pressure or noise level and having a throttling member separate from the closure member, e.g. screens, slots, labyrinths

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Details Of Valves (AREA)

Abstract

To provide a flow control valve that can sufficiently suppress fluid passage noise.SOLUTION: A flow control valve 10A includes: a main valve body 2 (valve body) including a communication hole 25 (inflow port) and an outflow part 211 (outflow port); and an auxiliary valve port (valve port) 24 installed inside the main valve body 2 to throttle a flow passage for a fluid. A straightening member 6 for straightening a flow of the fluid by causing the fluid to pass therethrough is provided between the auxiliary valve port 24 and the outflow part 211. The straightening member 6 includes: a high-resistance part 61 exerting high resistance on the center side thereof; and a low-resistance part 62 exerting low resistance on the outer side thereof as compared to the high-resistance part 61.SELECTED DRAWING: Figure 2

Description

本発明は、流量制御弁及び冷凍サイクルシステムに関する。 The present invention relates to a flow control valve and a refrigeration cycle system.

従来、空気調和機等の冷凍サイクルシステムに設けられる流量制御弁として、例えば、特許文献１には、流入口及び流出口を有した弁本体と、弁本体の内部に設けられて流体の流路を絞る弁口（弁座）と、を備え、弁口と流出口との間に設けられた消音部材（網目構造の部材又は発泡材料からなる部材）に流体（冷媒）を通過させることで、流体通過音（冷媒通過音）の抑制を意図した膨張弁が開示されている。 Conventionally, as a flow rate control valve provided in a refrigeration cycle system such as an air conditioner, for example, Patent Document 1 describes a valve body having an inlet and an outlet, and a fluid flow path provided inside the valve body. By passing a fluid (refrigerant) through a sound deadening member (a member having a mesh structure or a member made of a foam material) provided between the valve port and the outlet, which is provided with a valve port (valve seat) for squeezing. An expansion valve intended to suppress a fluid passing sound (refrigerant passing sound) is disclosed.

国際公開第２０１５／０６３８５４号公報International Publication No. 2015/063854

しかしながら、特許文献１に開示されたような従来の流量制御弁では、弁口を通過して流速が高まった流体が消音部材の中央付近に集中し、流速が低下しないままに消音部材を通過するため、流体通過音を必ずしも十分に抑制することができない虞がある。 However, in the conventional flow rate control valve as disclosed in Patent Document 1, the fluid having increased the flow velocity through the valve opening is concentrated near the center of the muffling member and passes through the muffling member without decreasing the flow velocity. Therefore, there is a possibility that the fluid passing sound cannot always be sufficiently suppressed.

本発明の目的は、流体通過音の十分な抑制を図ることができる流量制御弁及び冷凍サイクルシステムを提供することである。 An object of the present invention is to provide a flow control valve and a refrigeration cycle system capable of sufficiently suppressing fluid passing noise.

本発明の流量制御弁は、流入口及び流出口を有した弁本体と、前記弁本体の内部に設けられて流体の流路を絞る弁口と、を備えた流量制御弁であって、前記弁口と前記流出口との間には、流体を通過させることで整流する整流部材が設けられ、前記整流部材は、その中心側に流路抵抗の高い高抵抗部と、前記高抵抗部よりも外側に流路抵抗の低い低抵抗部と、を備えることを特徴とする。なお、本発明では、前記高抵抗部は、範囲を狭くした場合等にも、前記整流部材の中心を跨ぐ範囲に設定することが好ましい。 The flow rate control valve of the present invention is a flow rate control valve including a valve body having an inlet and an outlet, and a valve port provided inside the valve body to narrow the flow path of the fluid. A rectifying member that rectifies by passing a fluid is provided between the valve port and the outlet, and the rectifying member has a high resistance portion having a high flow path resistance and a high resistance portion on the center side thereof. It is also characterized by having a low resistance portion having a low flow path resistance on the outside. In the present invention, it is preferable to set the high resistance portion in a range straddling the center of the rectifying member even when the range is narrowed.

このような本発明によれば、弁口を通過した流体は、先ず整流部材の中心近傍に向かうものの、流路抵抗の高い高抵抗部は通過しにくいことから、外側の低抵抗部に向かっても流れることになり、流体の流れを中央付近から外側にも分散させてから、整流部材の略全体を流体が通過し、整流部材の略全体によって流体内の気泡を細分化させることで、消音効果を得ることができ、流体通過音の十分な抑制を図ることができる。 According to the present invention as described above, the fluid that has passed through the valve opening first heads toward the center of the rectifying member, but it is difficult for the high resistance part having high flow path resistance to pass through, so that the fluid passes toward the low resistance part on the outside. After the flow of the fluid is dispersed from the vicinity of the center to the outside, the fluid passes through almost the entire rectifying member, and the bubbles in the fluid are subdivided by the substantially entire rectifying member to mute the sound. The effect can be obtained, and the fluid passing sound can be sufficiently suppressed.

この際、前記整流部材の前記高抵抗部は、前記弁口の内径よりも大きい範囲に設けられていることが好ましい。 At this time, it is preferable that the high resistance portion of the rectifying member is provided in a range larger than the inner diameter of the valve port.

また、前記整流部材は、前記高抵抗部の方が前記低抵抗部よりも高い濾過密度を有していることが好ましい。 Further, it is preferable that the high resistance portion of the rectifying member has a higher filtration density than the low resistance portion.

また、前記整流部材は、前記高抵抗部の方が前記低抵抗部よりも大きな厚みに形成されていることが好ましい。 Further, it is preferable that the high resistance portion of the rectifying member is formed to have a larger thickness than the low resistance portion.

また、前記整流部材の前記高抵抗部は、前記弁口に対向する面が中心側から外側に向かって厚みが小さくなる傾斜面を有して形成されていることが好ましい。 Further, it is preferable that the high resistance portion of the rectifying member is formed so that the surface facing the valve port has an inclined surface whose thickness decreases from the center side to the outside.

また、前記整流部材の前記弁口に対向する側には、前記高抵抗部に位置する小孔と前記低抵抗部に位置する大孔とを有した板材が設けられていることが好ましい。 Further, it is preferable that a plate material having a small hole located in the high resistance portion and a large hole located in the low resistance portion is provided on the side of the rectifying member facing the valve port.

また、前記弁口を構成する弁座部には、前記弁口から前記流出口に向かって内径が大きくなる第２弁口と、前記第２弁口から前記流出口に向かってさらに内径が大きくなる第３弁口と、が設けられ、前記第３弁口に前記整流部材が設けられていることが好ましい。 Further, the valve seat portion constituting the valve port has a second valve port whose inner diameter increases from the valve port toward the outlet, and a valve seat portion having a larger inner diameter from the second valve port toward the outlet. It is preferable that the third valve port is provided and the rectifying member is provided at the third valve port.

また、軸線方向に進退移動することで前記弁口の開口面積を調整する弁体と、前記弁体を進退駆動する駆動部と、をさらに備えることが好ましい。 Further, it is preferable to further include a valve body that adjusts the opening area of the valve opening by moving forward and backward in the axial direction, and a drive unit that drives the valve body forward and backward.

本発明の冷凍サイクルシステムは、前記流量制御弁を備えることを特徴とする。 The refrigeration cycle system of the present invention is characterized by including the flow rate control valve.

このような本発明によれば、上記した流量制御弁のように、流体通過音の十分な抑制を図ることができるので、静音化された冷凍サイクルシステムとすることができる。 According to the present invention as described above, it is possible to sufficiently suppress the fluid passing noise as in the flow control valve described above, so that a noise-reduced refrigeration cycle system can be obtained.

本発明の流量制御弁及び冷凍サイクルシステムによれば、流体通過音の十分な抑制を図ることができる。 According to the flow rate control valve and the refrigeration cycle system of the present invention, it is possible to sufficiently suppress the fluid passing noise.

本発明の第１実施形態に係る流量制御弁を示す縦断面図である。It is a vertical sectional view which shows the flow rate control valve which concerns on 1st Embodiment of this invention. 前記流量制御弁の要部を拡大して示す縦断面図である。It is a vertical sectional view which shows the main part of the flow rate control valve in an enlarged manner. 本発明の第２実施形態に係る流量制御弁の要部を拡大して示す縦断面図である。It is a vertical sectional view which shows the main part of the flow rate control valve which concerns on 2nd Embodiment of this invention in an enlarged manner. 本発明の第３実施形態に係る流量制御弁の要部を拡大して示す縦断面図である。It is a vertical sectional view which shows the main part of the flow rate control valve which concerns on 3rd Embodiment of this invention in an enlarged manner. 本発明の第４実施形態に係る流量制御弁の要部を拡大して示す縦断面図である。It is a vertical sectional view which shows the main part of the flow rate control valve which concerns on 4th Embodiment of this invention in an enlarged manner. 本発明の冷凍サイクルシステムの一例を示す図である。It is a figure which shows an example of the refrigeration cycle system of this invention. 本発明の他の実施形態に係る流量制御弁を示す縦断面図である。It is a vertical sectional view which shows the flow rate control valve which concerns on other embodiment of this invention. 前記流量制御弁の要部を拡大して示す縦断面図である。It is a vertical sectional view which shows the main part of the flow rate control valve in an enlarged manner.

本発明の第１実施形態に係る流量制御弁を図１及び図２に基づいて説明する。本実施形態の流量制御弁１０Ａは、弁ハウジング１と、弁ハウジング１内に形成された主弁ポート１４と、主弁ポート１４を開閉可能な主弁体２（弁本体）と、主弁体２内の副弁ポート２４（弁口）と、副弁ポート２４を開閉可能な副弁体３（弁体）と、ステッピングモータ４（駆動部）と、を備えた二段式電動弁である。なお、以下の説明における「上下」の概念は図１の図面における上下に対応する。 The flow rate control valve according to the first embodiment of the present invention will be described with reference to FIGS. 1 and 2. The flow control valve 10A of the present embodiment includes a valve housing 1, a main valve port 14 formed in the valve housing 1, a main valve body 2 (valve body) capable of opening and closing the main valve port 14, and a main valve body. It is a two-stage electric valve including a sub-valve port 24 (valve port) in 2, a sub-valve body 3 (valve body) capable of opening and closing the sub-valve port 24, and a stepping motor 4 (drive unit). .. The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawing of FIG.

弁ハウジング１は、筒状の弁ハウジング部材１Ａと、弁ハウジング部材１Ａの上端開口部に固定される支持部材１Ｂと、を有している。弁ハウジング部材１Ａは、その内部に円筒状の主弁室１Ｃが形成され、弁ハウジング部材１Ａには、側面側から主弁室１Ｃに連通して冷媒等の流体が流入される一次継手管１１が取り付けられ、底面側から主弁室１Ｃに連通して流体が流出される二次継手管１２が取り付けられている。支持部材１Ｂは、樹脂成形品であって、金属製の固定部１５によって弁ハウジング部材１Ａに溶接固定されている。 The valve housing 1 has a cylindrical valve housing member 1A and a support member 1B fixed to the upper end opening of the valve housing member 1A. A cylindrical main valve chamber 1C is formed inside the valve housing member 1A, and a primary joint pipe 11 in which a fluid such as a refrigerant flows into the valve housing member 1A from the side surface side to the main valve chamber 1C. Is attached, and a secondary joint pipe 12 is attached, which communicates with the main valve chamber 1C from the bottom surface side and allows fluid to flow out. The support member 1B is a resin molded product, and is welded and fixed to the valve housing member 1A by a metal fixing portion 15.

主弁ポート１４は、弁ハウジング部材１Ａにおいて、主弁室１Ｃと二次継手管１２とが連通する位置に設けられた主弁座１３から二次継手管１２側に断面円形状に形成されている。 The main valve port 14 is formed in the valve housing member 1A from the main valve seat 13 provided at a position where the main valve chamber 1C and the secondary joint pipe 12 communicate with each other in a circular cross section on the secondary joint pipe 12 side. There is.

主弁体２は、主弁ポート１４を開閉する部位であって、主弁座１３に対して着座または離座する主弁部２１（弁座部）を有する弁体主部２Ａと、ストッパ部２Ｂと、副弁座２Ｃと、を有している。弁体主部２Ａは、軸線Ｌ方向を軸方向とする円筒部２２と、この円筒部２２の内部に形成されて流体が流通する副弁室２３と、軸線Ｌ方向に沿って副弁座２Ｃを貫通する副弁ポート２４と、を有している。円筒部２２は、その周面部に複数の連通孔２５（流入口）が形成され、その内周面には、軸線Ｌ方向に沿った挿通孔２６が形成されている。副弁室２３は、連通孔２５により主弁室１Ｃに連通されている。ストッパ部２Ｂは、円環状に形成されて弁体主部２Ａの上端部に固定され、その内部にロータ軸４６が挿通されており、このロータ軸４６の下端に設けられた副弁体３の上昇位置を規制する。副弁座２Ｃは、副弁室２３の二次継手管１２側に設けられている。なお、ストッパ部２Ｂは、その上端部から下方側にかけて段差形状が形成されており、この段差形状と支持部材１Ｂの天井面との間には、主弁ばね２７が配設されている。この主弁ばね２７により主弁体２は主弁座１３方向（閉方向）に付勢されている。 The main valve body 2 is a portion that opens and closes the main valve port 14, and has a valve body main portion 2A having a main valve portion 21 (valve seat portion) that sits on or leaves the main valve seat 13, and a stopper portion. It has 2B and an auxiliary valve seat 2C. The valve body main portion 2A has a cylindrical portion 22 whose axial direction is the axis L direction, a sub valve chamber 23 formed inside the cylindrical portion 22 through which a fluid flows, and a sub valve seat 2C along the axis L direction. It has an auxiliary valve port 24 and a penetrating the auxiliary valve port 24. A plurality of communication holes 25 (inflow ports) are formed in the peripheral surface of the cylindrical portion 22, and an insertion hole 26 along the axis L direction is formed in the inner peripheral surface thereof. The auxiliary valve chamber 23 is communicated with the main valve chamber 1C by a communication hole 25. The stopper portion 2B is formed in an annular shape and is fixed to the upper end portion of the valve body main portion 2A, and the rotor shaft 46 is inserted therein, and the auxiliary valve body 3 provided at the lower end of the rotor shaft 46 is inserted. Regulate the ascending position. The auxiliary valve seat 2C is provided on the secondary joint pipe 12 side of the auxiliary valve chamber 23. The stopper portion 2B has a stepped shape formed from the upper end portion to the lower side thereof, and a main valve spring 27 is arranged between the stepped shape and the ceiling surface of the support member 1B. The main valve body 2 is urged in the main valve seat 13 direction (closed direction) by the main valve spring 27.

副弁ポート２４は、主弁体２内において、副弁座２Ｃから二次継手管１２側に断面円形状に形成されている。そして、円筒部２２の内側において、副弁ポート２４の下流側には、この副弁ポート２４よりも径方向に拡径された円筒状の拡径部５（第２弁口）と、拡径部５の下流側には、この拡径部５よりも径方向に拡径された円筒状の第１段差部２１ａ（第３弁口）と、この第１段差部２１ａよりも径方向に拡径された円筒状の第２段差部２１ｂと、が設けられている。そして、第１段差部２１ａ内に、多孔質材や金属メッシュ等で形成された流体を通過させる円柱状の整流部材６が嵌め込まれ、更に環状の保持部２１ｃが第２段差部２１ｂ内に嵌め込まれ、整流部材６の下端部外周が保持され、保持部２１ｃの内周面に、流体の流出部２１１（流出口）が形成されている。 The sub-valve port 24 is formed in the main valve body 2 in a circular cross section from the sub-valve seat 2C to the secondary joint pipe 12 side. Inside the cylindrical portion 22, on the downstream side of the sub-valve port 24, a cylindrical diameter-expanded portion 5 (second valve port) whose diameter is expanded in the radial direction from the sub-valve port 24 is expanded. On the downstream side of the portion 5, a cylindrical first step portion 21a (third valve port) whose diameter is expanded in the radial direction from the enlarged diameter portion 5 and a radial first step portion 21a are expanded in the radial direction from the first step portion 21a. A cylindrical second step portion 21b having a diameter is provided. Then, a columnar rectifying member 6 for passing a fluid formed of a porous material, a metal mesh, or the like is fitted into the first step portion 21a, and an annular holding portion 21c is further fitted into the second step portion 21b. The outer periphery of the lower end portion of the rectifying member 6 is held, and the fluid outflow portion 211 (outlet) is formed on the inner peripheral surface of the holding portion 21c.

副弁体３は、主弁体２に形成された副弁ポート２４の開度を変更する部位である。この副弁体３は、円筒状の副弁基部３Ａと、副弁基部３Ａから下方に突出する副弁部３Ｂと、副弁基部３Ａの上側に設けられたスラストワッシャ３Ｃと、副弁基部３Ａの内部に設けられた副弁ばね（不図示）と、で構成されている。副弁基部３Ａは、主弁体２の挿通孔２６に挿通され、軸線Ｌ方向に沿った上下方向に進退自在かつ軸線Ｌ回りに回転自在に支持されている。副弁部３Ｂは、ロッド部３１と、ロッド部３１下端部のニードル部３２と、を有している。ニードル部３２は、副弁ポート２４との隙間によって流体を通過させる絞り部３３を構成している。さらに、ニードル部３２は、図２に示すように、副弁ポート２４に挿入されるとともに、副弁ポート２４の出口側に向かって徐々に径が小さくなる流量制御部３２ａを有する。スラストワッシャ３Ｃは、副弁基部３Ａの上面及びストッパ部２Ｂの下面に当接可能になっており、その当接面同士の摩擦力が極めて小さくなるようになっている。また、副弁基部３Ａの上部には挿通孔が設けられてロータ軸４６が挿通され、ロータ軸４６の下端部に形成されたフランジ部（不図示）と副弁基部３Ａの底部に接合された副弁部３Ｂの上端部との間に副弁ばねが配設されている。この副弁ばねにより副弁体３はロータ軸４６（マグネットロータ４４）に対して副弁座２Ｃ方向（閉方向）に付勢されている。なお、副弁基部３Ａは、ロータ軸４６および副弁部３Ｂと一体に形成されてもよく、その場合には、副弁基部３Ａが中実状に形成され、副弁ばねが省略されてもよい。 The sub-valve body 3 is a portion for changing the opening degree of the sub-valve port 24 formed in the main valve body 2. The sub-valve body 3 includes a cylindrical sub-valve base 3A, a sub-valve portion 3B protruding downward from the sub-valve base 3A, a thrust washer 3C provided on the upper side of the sub-valve base 3A, and a sub-valve base 3A. It is composed of an auxiliary valve spring (not shown) provided inside the. The sub-valve base 3A is inserted into the insertion hole 26 of the main valve body 2 and is supported so as to be vertically reciprocating along the axis L direction and rotatably around the axis L. The auxiliary valve portion 3B has a rod portion 31 and a needle portion 32 at the lower end of the rod portion 31. The needle portion 32 constitutes a throttle portion 33 through which a fluid passes through a gap with the auxiliary valve port 24. Further, as shown in FIG. 2, the needle unit 32 has a flow rate control unit 32a that is inserted into the sub-valve port 24 and whose diameter gradually decreases toward the outlet side of the sub-valve port 24. The thrust washer 3C can come into contact with the upper surface of the auxiliary valve base portion 3A and the lower surface of the stopper portion 2B, and the frictional force between the contact surfaces is extremely small. Further, an insertion hole was provided in the upper portion of the sub-valve base portion 3A, and the rotor shaft 46 was inserted into the rotor shaft 46, and the flange portion (not shown) formed at the lower end portion of the rotor shaft 46 was joined to the bottom portion of the sub-valve base portion 3A. A sub-valve spring is arranged between the sub-valve portion 3B and the upper end portion. The auxiliary valve body 3 is urged by the auxiliary valve spring in the auxiliary valve seat 2C direction (closed direction) with respect to the rotor shaft 46 (magnet rotor 44). The sub-valve base 3A may be integrally formed with the rotor shaft 46 and the sub-valve 3B. In that case, the sub-valve base 3A may be formed in a solid state and the sub-valve spring may be omitted. ..

ステッピングモータ４は、副弁体３の軸線Ｌ方向に進退させるとともに、この副弁体３を介して主弁体２も軸線Ｌ方向に進退させる部位である。このステッピングモータ４は、マグネットロータ４４の回転により副弁体３を進退させるねじ送り機構４２と、マグネットロータ４４の回転を規制するストッパ機構４３と、を備える。ステッピングモータ４は、外周部が多極に着磁されたマグネットロータ４４と、キャン１８の外周に配設されたステータコイル４５と、マグネットロータ４４に固定されたロータ軸４６と、を備えている。ロータ軸４６は、固定部材４６ａを介してマグネットロータ４４に固定されるとともに、軸線Ｌ方向に沿って延び、その上端部はストッパ機構４３のガイド４７に挿入されている。ロータ軸４６の中間部には雄ねじ部４６ｂが一体に形成され、この雄ねじ部４６ｂが支持部材１Ｂの雌ねじ部１７に螺合し、これによってねじ送り機構４２が構成されている。マグネットロータ４４が回転すると、ロータ軸４６の雄ねじ部４６ｂが雌ねじ部１７に案内されることで、マグネットロータ４４およびロータ軸４６が軸線Ｌ方向に進退移動し、これに伴って副弁体３も軸線Ｌに沿って上昇または下降する。 The stepping motor 4 is a portion that advances and retreats in the axis L direction of the sub-valve body 3 and also advances and retreats the main valve body 2 in the axis L direction via the sub-valve body 3. The stepping motor 4 includes a screw feed mechanism 42 that advances and retreats the auxiliary valve body 3 by the rotation of the magnet rotor 44, and a stopper mechanism 43 that regulates the rotation of the magnet rotor 44. The stepping motor 4 includes a magnet rotor 44 whose outer peripheral portion is magnetized to multiple poles, a stator coil 45 arranged on the outer peripheral portion of the can 18, and a rotor shaft 46 fixed to the magnet rotor 44. .. The rotor shaft 46 is fixed to the magnet rotor 44 via the fixing member 46a and extends along the axis L direction, and the upper end thereof is inserted into the guide 47 of the stopper mechanism 43. A male screw portion 46b is integrally formed in the middle portion of the rotor shaft 46, and the male screw portion 46b is screwed into the female screw portion 17 of the support member 1B, whereby the screw feed mechanism 42 is configured. When the magnet rotor 44 rotates, the male threaded portion 46b of the rotor shaft 46 is guided to the female threaded portion 17, so that the magnet rotor 44 and the rotor shaft 46 move forward and backward in the axis L direction, and the auxiliary valve body 3 also moves accordingly. Ascends or descends along the axis L.

ストッパ機構４３は、キャン１８内の天井部から垂下された円筒状のガイド４７と、ガイド４７の外周に固定された螺旋状のガイド線体４８と、ガイド線体４８にガイドされて回転かつ上下動可能な可動スライダ４９と、を備えている。可動スライダ４９には、径方向外側に突出した爪部４９ａが設けられ、マグネットロータ４４には、上方に延びて爪部４９ａと当接する延長部４４ａが設けられている。マグネットロータ４４が回転すると、延長部４４ａが爪部４９ａを押すことで、可動スライダ４９がガイド線体４８に倣って回転かつ上下する。ガイド線体４８には、マグネットロータ４４の最上端位置を規定する上端ストッパ４８ａと、マグネットロータ４４の最下端位置を規定する下端ストッパ４８ｂと、が形成されている。これらの上端ストッパ４８ａおよび下端ストッパ４８ｂに可動スライダ４９が当接することで、可動スライダ４９の回転が停止され、これによりマグネットロータ４４の回転が規制され、副弁体３の上昇または下降も停止される。 The stopper mechanism 43 is guided by a cylindrical guide 47 hanging from the ceiling in the can 18, a spiral guide wire 48 fixed to the outer periphery of the guide 47, and a guide wire 48 to rotate and move up and down. It is equipped with a movable slider 49 that can be moved. The movable slider 49 is provided with a claw portion 49a protruding outward in the radial direction, and the magnet rotor 44 is provided with an extension portion 44a extending upward and in contact with the claw portion 49a. When the magnet rotor 44 rotates, the extension portion 44a pushes the claw portion 49a, so that the movable slider 49 rotates and moves up and down according to the guide wire body 48. The guide wire body 48 is formed with an upper end stopper 48a that defines the uppermost end position of the magnet rotor 44 and a lower end stopper 48b that defines the lowermost end position of the magnet rotor 44. When the movable slider 49 comes into contact with the upper end stopper 48a and the lower end stopper 48b, the rotation of the movable slider 49 is stopped, thereby restricting the rotation of the magnet rotor 44 and stopping the ascent or descent of the auxiliary valve body 3. To.

本実施形態では、図２に示すように、整流部材６は、その中心側に流路抵抗の高い高抵抗部６１と、高抵抗部６１よりも外側に流路抵抗の低い低抵抗部６２と、を備えている。そして、整流部材６の高抵抗部６１は、整流部材６の中心を跨ぐ範囲に設けられている。また、高抵抗部６１は、副弁ポート２４の内径よりも大きい範囲に設けられ、更に、整流部材６は、高抵抗部６１の方が低抵抗部６２よりも高い濾過密度を有している。具体的には、高抵抗部６１の濾過密度は、低抵抗部６２の濾過密度よりも１．２倍以上高く設定されている。 In the present embodiment, as shown in FIG. 2, the rectifying member 6 has a high resistance portion 61 having a high flow path resistance on the center side thereof and a low resistance portion 62 having a low flow path resistance outside the high resistance portion 61. , Is equipped. The high resistance portion 61 of the rectifying member 6 is provided in a range straddling the center of the rectifying member 6. Further, the high resistance portion 61 is provided in a range larger than the inner diameter of the auxiliary valve port 24, and the rectifying member 6 has a higher filtration density in the high resistance portion 61 than in the low resistance portion 62. .. Specifically, the filtration density of the high resistance portion 61 is set to be 1.2 times or more higher than the filtration density of the low resistance portion 62.

以上のように構成された流量制御弁１０Ａは、次のように動作する。まず、流量制御弁１０Ａが、主弁体２の主弁部２１が主弁座１３に着座し、主弁ポート１４が閉じられた弁閉状態にあるとする。さらに、流量制御弁１０Ａが、副弁体３が副弁ポート２４に最も近づいた位置にあるとき、副弁体３は、副弁座２Ｃに着座せず、副弁体３のニードル部３２の外周面と副弁ポート２４の内周面との間隙によって流路が形成されている。従って、一次継手管１１から主弁室１Ｃに流入した流体は、弁体主部２Ａの連通孔２５を通過し、副弁室２３に流入する。副弁室２３に流入した流体は、副弁体３のニードル部３２の外周面と副弁ポート２４との間隙を通って主弁部２１の下方に流れ、主弁ポート１４から二次継手管１２に向かって流出する。すなわち、弁開度がゼロ（副弁部３Ｂが最下端の位置）であっても微少な流量が生じることとなる。 The flow rate control valve 10A configured as described above operates as follows. First, it is assumed that the flow control valve 10A is in a valve closed state in which the main valve portion 21 of the main valve body 2 is seated on the main valve seat 13 and the main valve port 14 is closed. Further, when the flow control valve 10A is in the position where the sub-valve body 3 is closest to the sub-valve port 24, the sub-valve body 3 does not sit on the sub-valve seat 2C, and the needle portion 32 of the sub-valve body 3 does not sit. A flow path is formed by a gap between the outer peripheral surface and the inner peripheral surface of the auxiliary valve port 24. Therefore, the fluid flowing from the primary joint pipe 11 into the main valve chamber 1C passes through the communication hole 25 of the valve body main portion 2A and flows into the sub-valve chamber 23. The fluid flowing into the sub-valve chamber 23 flows below the main valve portion 21 through the gap between the outer peripheral surface of the needle portion 32 of the sub-valve body 3 and the sub-valve port 24, and flows from the main valve port 14 to the secondary joint pipe. It flows out toward 12. That is, even if the valve opening degree is zero (the position where the auxiliary valve portion 3B is at the lowermost end), a minute flow rate is generated.

次に、ステッピングモータ４を駆動してマグネットロータ４４を回転させて副弁体３を上昇させることで、副弁体３の副弁部３Ｂのニードル部３２が副弁ポート２４の内部を上昇し、副弁部３Ｂのニードル部３２と副弁ポート２４との間隙による流路が拡大され、流量が徐々に増加する。この際、主弁体２の主弁部２１は主弁座１３に着座したままであるため、流量の増加は微少である。このように主弁体２を閉じたまま副弁体３の開度を変更する制御域が小流量制御域である。次に、副弁体３をさらに上昇させると、スラストワッシャ３Ｃがストッパ部２Ｂに当接し、副弁体３によって主弁体２が引き上げられ、主弁部２１が主弁座１３から離座する。このように主弁体２を離座させて主弁ポート１４の開度を変更する制御域が大流量制御域であって、この大流量制御域における流量の変化は大きなものとなり、主弁体２が主弁ポート１４から最も離れた全開状態において、流量は最大となる。 Next, by driving the stepping motor 4 to rotate the magnet rotor 44 to raise the sub-valve body 3, the needle portion 32 of the sub-valve portion 3B of the sub-valve body 3 rises inside the sub-valve port 24. The flow path due to the gap between the needle portion 32 of the sub-valve portion 3B and the sub-valve port 24 is expanded, and the flow rate is gradually increased. At this time, since the main valve portion 21 of the main valve body 2 remains seated on the main valve seat 13, the increase in the flow rate is slight. The control range for changing the opening degree of the sub-valve body 3 while the main valve body 2 is closed in this way is the small flow rate control range. Next, when the sub-valve body 3 is further raised, the thrust washer 3C abuts on the stopper portion 2B, the main valve body 2 is pulled up by the sub-valve body 3, and the main valve portion 21 is separated from the main valve seat 13. .. In this way, the control range in which the main valve body 2 is separated and the opening degree of the main valve port 14 is changed is the large flow rate control range, and the change in the flow rate in this large flow rate control range becomes large, and the main valve body In the fully open state where 2 is the furthest from the main valve port 14, the flow rate is maximum.

以上の本実施形態によれば、図２に示すように、副弁ポート２４を通過した流体は、先ず整流部材６の中心近傍に向かうものの、流路抵抗の高い高抵抗部６１は通過しにくいことから、外側の低抵抗部６２に向かっても流れることになり、流体の流れを中央付近から外側にも分散させてから、整流部材６の略全体を流体が通過し、整流部材６の略全体によって流体内の気泡を細分化させることで、特に小流量制御域における消音効果を得ることができ、流体通過音の十分な抑制を図ることができる。 According to the above embodiment, as shown in FIG. 2, the fluid that has passed through the auxiliary valve port 24 first heads toward the vicinity of the center of the rectifying member 6, but it is difficult for the high resistance portion 61 having high flow path resistance to pass through. Therefore, the fluid also flows toward the low resistance portion 62 on the outside, and after the flow of the fluid is dispersed from the vicinity of the center to the outside, the fluid passes through substantially the entire rectifying member 6 and is abbreviated as the rectifying member 6. By subdividing the bubbles in the fluid as a whole, it is possible to obtain a muffling effect especially in the small flow rate control range, and it is possible to sufficiently suppress the sound passing through the fluid.

本実施形態では、整流部材６の高抵抗部６１は、副弁ポート２４の内径よりも大きい範囲に設けられている。このような構成であるため、流速の速い流体が、より多く高抵抗部６１に向かうので、より多くの流体が外側の低抵抗部６２に向かっても流れることになり、整流部材６による消音効果をより得ることができ、流体通過音のより十分な抑制を図ることができる。 In the present embodiment, the high resistance portion 61 of the rectifying member 6 is provided in a range larger than the inner diameter of the auxiliary valve port 24. Since this configuration allows more fluid with a high flow velocity to flow toward the high resistance portion 61, more fluid also flows toward the outer low resistance portion 62, and the sound deadening effect of the rectifying member 6 Can be obtained more, and the fluid passing sound can be more sufficiently suppressed.

本実施形態では、整流部材６は、高抵抗部６１の方が低抵抗部６２よりも高い濾過密度を有している。このような構成であるため、異なる濾過密度の部材を繋ぎ合わせるなどして整流部材６を簡易に構成することができる。 In the present embodiment, the rectifying member 6 has a higher filtration density in the high resistance portion 61 than in the low resistance portion 62. With such a configuration, the rectifying member 6 can be easily configured by connecting members having different filtration densities.

次に、図３に基づき、本発明の第２実施形態に係る流量制御弁について説明する。本実施形態の流量制御弁１０Ｂは、第１実施形態の流量制御弁１０Ａと同様に、弁ハウジング１と、弁ハウジング１内に形成された主弁ポート１４と、主弁ポート１４を開閉可能な主弁体２（弁本体）と、主弁体２内の副弁ポート２４（弁口）と、副弁ポート２４を開閉可能な副弁体３（弁体）と、ステッピングモータ４（駆動部）と、を備えた二段式電動弁である。本実施形態の流量制御弁１０Ｂでは、主弁体２の一部構成が第１実施形態の流量制御弁１０Ａと相違している。以下、相違点について詳しく説明する。 Next, the flow rate control valve according to the second embodiment of the present invention will be described with reference to FIG. The flow rate control valve 10B of the present embodiment can open and close the valve housing 1, the main valve port 14 formed in the valve housing 1, and the main valve port 14 in the same manner as the flow rate control valve 10A of the first embodiment. The main valve body 2 (valve body), the sub-valve port 24 (valve port) in the main valve body 2, the sub-valve body 3 (valve body) that can open and close the sub-valve port 24, and the stepping motor 4 (drive unit). ), And a two-stage electric valve. In the flow rate control valve 10B of the present embodiment, a partial configuration of the main valve body 2 is different from the flow rate control valve 10A of the first embodiment. The differences will be described in detail below.

本実施形態の流量制御弁１０Ｂでは、主弁体２に設けられた整流部材６は、高抵抗部６１と低抵抗部６２の濾過密度は同じで、高抵抗部６１の方が低抵抗部６２よりも大きな厚みに形成されていることが、第１実施形態の流量制御弁１０Ａと相違している。なお、具体的には、本実施形態の流量制御弁１０Ｂでは、整流部材６において、高抵抗部６１の厚みは、低抵抗部６２の厚みの１．２倍以上に設定されている。 In the flow control valve 10B of the present embodiment, in the rectifying member 6 provided on the main valve body 2, the filtration densities of the high resistance portion 61 and the low resistance portion 62 are the same, and the high resistance portion 61 has the lower resistance portion 62. It is different from the flow control valve 10A of the first embodiment in that it is formed to have a larger thickness. Specifically, in the flow control valve 10B of the present embodiment, the thickness of the high resistance portion 61 is set to 1.2 times or more the thickness of the low resistance portion 62 in the rectifying member 6.

以上の本実施形態の流量制御弁１０Ｂでは、整流部材６における高抵抗部６１と低抵抗部６２との厚みの違いで流路抵抗の違いを出している。従って、本実施形態の流量制御弁１０Ｂによれば、第１実施形態の流量制御弁１０Ａと略同様の作用効果を奏することができる。 In the flow rate control valve 10B of the present embodiment described above, the difference in flow path resistance is caused by the difference in thickness between the high resistance portion 61 and the low resistance portion 62 in the rectifying member 6. Therefore, according to the flow rate control valve 10B of the present embodiment, it is possible to obtain substantially the same operation and effect as the flow rate control valve 10A of the first embodiment.

次に、図４に基づき、本発明の第３実施形態に係る流量制御弁について説明する。本実施形態の流量制御弁１０Ｃは、第１実施形態の流量制御弁１０Ａと同様に、弁ハウジング１と、弁ハウジング１内に形成された主弁ポート１４と、主弁ポート１４を開閉可能な主弁体２（弁本体）と、主弁体２内の副弁ポート２４（弁口）と、副弁ポート２４を開閉可能な副弁体３（弁体）と、ステッピングモータ４（駆動部）と、を備えた二段式電動弁である。本実施形態の流量制御弁１０Ｃでは、主弁体２の一部構成が第１実施形態の流量制御弁１０Ａと相違している。以下、相違点について詳しく説明する。 Next, the flow rate control valve according to the third embodiment of the present invention will be described with reference to FIG. The flow rate control valve 10C of the present embodiment can open and close the valve housing 1, the main valve port 14 formed in the valve housing 1, and the main valve port 14 in the same manner as the flow rate control valve 10A of the first embodiment. The main valve body 2 (valve body), the sub-valve port 24 (valve port) in the main valve body 2, the sub-valve body 3 (valve body) that can open and close the sub-valve port 24, and the stepping motor 4 (drive unit). ), And a two-stage electric valve. In the flow rate control valve 10C of the present embodiment, a partial configuration of the main valve body 2 is different from the flow rate control valve 10A of the first embodiment. The differences will be described in detail below.

本実施形態の流量制御弁１０Ｃでは、主弁体２に設けられた整流部材６は、高抵抗部６１と低抵抗部６２の濾過密度は同じで、高抵抗部６１は、副弁ポート２４に対向する面が中心側から外側に向かって厚みが小さくなる傾斜面を有する円錐部６１ａが形成されていることが、第１実施形態の流量制御弁１０Ａと相違している。なお、具体的には、本実施形態の流量制御弁１０Ｃでは、整流部材６において、円錐部６１ａを含めた高抵抗部６１の平均厚みは、低抵抗部６２の厚みの１．２倍以上に設定されている。 In the flow control valve 10C of the present embodiment, the rectifying member 6 provided in the main valve body 2 has the same filtration density of the high resistance portion 61 and the low resistance portion 62, and the high resistance portion 61 is connected to the sub valve port 24. The flow control valve 10A of the first embodiment is different from the flow control valve 10A of the first embodiment in that a conical portion 61a having an inclined surface whose facing surfaces decrease in thickness from the center side to the outside is formed. Specifically, in the flow control valve 10C of the present embodiment, in the rectifying member 6, the average thickness of the high resistance portion 61 including the conical portion 61a is 1.2 times or more the thickness of the low resistance portion 62. It is set.

以上の本実施形態の流量制御弁１０Ｃでは、整流部材６における高抵抗部６１と低抵抗部６２との形状の違いで流路抵抗の違いを出している。従って、本実施形態の流量制御弁１０Ｃによれば、第１実施形態の流量制御弁１０Ａと略同様の作用効果を奏することができる。 In the flow rate control valve 10C of the present embodiment described above, the difference in flow path resistance is caused by the difference in shape between the high resistance portion 61 and the low resistance portion 62 in the rectifying member 6. Therefore, according to the flow rate control valve 10C of the present embodiment, it is possible to obtain substantially the same operation and effect as the flow rate control valve 10A of the first embodiment.

次に、図５に基づき、本発明の第４実施形態に係る流量制御弁について説明する。本実施形態の流量制御弁１０Ｄは、第１実施形態の流量制御弁１０Ａと同様に、弁ハウジング１と、弁ハウジング１内に形成された主弁ポート１４と、主弁ポート１４を開閉可能な主弁体２（弁本体）と、主弁体２内の副弁ポート２４（弁口）と、副弁ポート２４を開閉可能な副弁体３（弁体）と、ステッピングモータ４（駆動部）と、を備えた二段式電動弁である。本実施形態の流量制御弁１０Ｄでは、主弁体２の一部構成が第１実施形態の流量制御弁１０Ａと相違している。以下、相違点について詳しく説明する。 Next, the flow rate control valve according to the fourth embodiment of the present invention will be described with reference to FIG. The flow rate control valve 10D of the present embodiment can open and close the valve housing 1, the main valve port 14 formed in the valve housing 1, and the main valve port 14 in the same manner as the flow rate control valve 10A of the first embodiment. The main valve body 2 (valve body), the sub-valve port 24 (valve port) in the main valve body 2, the sub-valve body 3 (valve body) that can open and close the sub-valve port 24, and the stepping motor 4 (drive unit). ), And a two-stage electric valve. In the flow rate control valve 10D of the present embodiment, a partial configuration of the main valve body 2 is different from the flow rate control valve 10A of the first embodiment. The differences will be described in detail below.

本実施形態の流量制御弁１０Ｄでは、主弁体２に設けられた整流部材６は、高抵抗部６１と低抵抗部６２の濾過密度は同じで、整流部材６の副弁ポート２４に対向する側に、高抵抗部６１に位置する小孔７ａ，・・・と低抵抗部６２に位置する大孔７ｂ，・・・とを有した板材７が設けられていることが、第１実施形態の流量制御弁１０Ａと相違している。なお、具体的には、本実施形態の流量制御弁１０Ｄの板材７における小孔７ａ，・・・と、大孔７ｂ，・・・とは、平面視で、軸線Ｌを中心とした円周上に等間隔でそれぞれ設けられている。そして、本実施形態の流量制御弁１０Ｄでは、整流部材６において、板材７の小孔７ａ，・・・の総開口面積に対して大孔７ｂ，・・・の総開口面積が１．２倍以上に設定されている。また、本実施形態における高抵抗部６１の範囲（半径）は、軸芯Ｌと大孔７ｂの内径の軸芯Ｌ側とを結ぶ範囲である。また、小孔７ａ，・・・と、大孔７ｂ，・・・とは、これらの個数、大きさ、形状、及び配置等を本発明の性能を発揮する範囲においては、その他様々にしてもよい。すなわち、例えば、小孔７ａは、整流部材６の中心に１個だけ設けられていてもよいし、大孔７ｂは、小孔７ａを囲むように環状に連続した形状で１個又は複数個が設けられていてもよい。 In the flow control valve 10D of the present embodiment, the rectifying member 6 provided in the main valve body 2 has the same filtration density of the high resistance portion 61 and the low resistance portion 62, and faces the sub-valve port 24 of the rectifying member 6. The first embodiment is provided with a plate material 7 having a small hole 7a, ... Located in the high resistance portion 61 and a large hole 7b, ... Located in the low resistance portion 62, on the side. It is different from the flow rate control valve 10A of. Specifically, the small holes 7a, ... And the large holes 7b, ... In the plate material 7 of the flow control valve 10D of the present embodiment are the circumferences about the axis L in a plan view. They are provided on the top at equal intervals. In the flow control valve 10D of the present embodiment, in the rectifying member 6, the total opening area of the large holes 7b, ... Is 1.2 times the total opening area of the small holes 7a, ... Of the plate material 7. It is set as above. Further, the range (radius) of the high resistance portion 61 in the present embodiment is a range connecting the shaft core L and the shaft core L side of the inner diameter of the large hole 7b. Further, the small holes 7a, ... And the large holes 7b, ... Are various in number, size, shape, arrangement, etc., as long as the performance of the present invention is exhibited. good. That is, for example, only one small hole 7a may be provided in the center of the rectifying member 6, and one or a plurality of large holes 7b may be formed in an annular continuous shape so as to surround the small hole 7a. It may be provided.

以上の本実施形態の流量制御弁１０Ｄでは、整流部材６に小孔７ａ，・・・と、大孔７ｂ，・・・とを有する板材７を付加部材として設けることで流路抵抗の違いを出している。従って、本実施形態の流量制御弁１０Ｄによれば、第１実施形態の流量制御弁１０Ａと略同様の作用効果を奏することができる。 In the flow control valve 10D of the present embodiment described above, the difference in flow path resistance is made by providing the rectifying member 6 with a plate material 7 having small holes 7a, ... And large holes 7b, ... As an additional member. It is out. Therefore, according to the flow rate control valve 10D of the present embodiment, it is possible to obtain substantially the same operation and effect as the flow rate control valve 10A of the first embodiment.

次に、本発明の冷凍サイクルシステムを図６に基づいて説明する。図６は、本発明の冷凍サイクルシステムの一例を示す図である。 Next, the refrigeration cycle system of the present invention will be described with reference to FIG. FIG. 6 is a diagram showing an example of the refrigeration cycle system of the present invention.

この図６に示されている冷凍サイクルシステム９０は、例えば、家庭用エアコン等の空気調和機に用いられる。上述の実施形態の流量制御弁１０（１０Ａ，１０Ｂ，１０Ｃ，１０Ｄ）は、空気調和機の第１室内側熱交換器９１（除湿時冷却器として作動）と第２室内側熱交換器９２（除湿時加熱器として作動）との間に設けられている。流量制御弁１０は、圧縮機９５、四方弁９６、室外側熱交換器９４および電子膨張弁９３とともに、ヒ－トポンプ式冷凍サイクルを構成している。第１室内側熱交換器９１と第２室内側熱交換器９２及び二段式電動弁１０は室内に設置され、圧縮機９５、四方弁９６、室外側熱交換器９４および電子膨張弁９３は室外に設置されていて冷暖房装置を構成している。 The refrigeration cycle system 90 shown in FIG. 6 is used, for example, in an air conditioner such as a home air conditioner. The flow control valves 10 (10A, 10B, 10C, 10D) of the above-described embodiment are the first indoor side heat exchanger 91 (acting as a dehumidifying cooler) and the second indoor side heat exchanger 92 (acting as a dehumidifying cooler) of the air conditioner. It is installed between (acting as a heater during dehumidification). The flow rate control valve 10 constitutes a heat pump type refrigeration cycle together with the compressor 95, the four-way valve 96, the outdoor heat exchanger 94, and the electronic expansion valve 93. The first indoor side heat exchanger 91, the second indoor side heat exchanger 92, and the two-stage electric valve 10 are installed indoors, and the compressor 95, the four-way valve 96, the outdoor heat exchanger 94, and the electronic expansion valve 93 are installed. It is installed outdoors and constitutes an air conditioner.

除湿弁としての流量制御弁１０は、除湿時以外の冷房時または暖房時には主弁体２によって主弁ポート１４が全開状態とされて、第１室内側熱交換器９１と第２室内側熱交換器９２は一つの室内側熱交換器とされる。そして、この一体の室内側熱交換器と室外側熱交換器９４は、「蒸発器」及び「凝縮器」として択一的に機能する。すなわち、電子膨張弁９３は、蒸発器と凝縮器の間に設けられている。 In the flow control valve 10 as a dehumidifying valve, the main valve port 14 is fully opened by the main valve body 2 during cooling or heating other than during dehumidification, and the heat exchanger 91 on the first chamber side and the heat exchange on the second chamber side are exchanged. The vessel 92 is one indoor heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 alternately function as an "evaporator" and a "condenser". That is, the electronic expansion valve 93 is provided between the evaporator and the condenser.

この冷凍サイクルシステム９０によれば、流体の経路上に上述した実施形態の流量制御弁１０が設けられているため、特に小流量制御域における流体通過音の抑制を図ることができるので、静音化された冷凍サイクルシステムとすることができる。 According to this refrigeration cycle system 90, since the flow rate control valve 10 of the above-described embodiment is provided on the fluid path, it is possible to suppress the fluid passing noise especially in the small flow rate control range, so that the noise is reduced. Can be a refrigeration cycle system.

次に、本発明の他の実施形態に係る流量制御弁を図７及び図８に基づいて説明する。本実施形態の流量制御弁１０Ｅは、弁ハウジング１１１と、弁ハウジング１１１内に形成された弁ポート１４０と、弁ポート１４０を開閉可能な電磁弁用弁体２０（弁本体）と、電磁ソレノイド装置４０（駆動部）と、を備えた電磁弁である。なお、図７及び図８は、いずれも電磁弁用弁体２０を全閉状態としたときの図である。 Next, the flow rate control valve according to another embodiment of the present invention will be described with reference to FIGS. 7 and 8. The flow control valve 10E of the present embodiment includes a valve housing 111, a valve port 140 formed in the valve housing 111, a solenoid valve valve body 20 (valve body) capable of opening and closing the valve port 140, and an electromagnetic solenoid device. It is a solenoid valve provided with 40 (driving unit). 7 and 8 are views when the solenoid valve valve body 20 is fully closed.

本実施形態の流量制御弁１０Ｅは、電磁弁用弁体２０の下端部に形成された円筒状の凹部内に、円板状の多孔体のフィルタ要素２５を嵌め込み、その下流に中心に絞り孔２６（弁口）を有する円柱状のオリフィス部材２７を嵌め込み、更にその下流に第１実施形態の流量制御弁１０Ａで用いた整流部材６を嵌め込んだ構成である。 In the flow control valve 10E of the present embodiment, a disc-shaped porous filter element 25 is fitted in a cylindrical recess formed at the lower end of the solenoid valve valve body 20, and a narrowing hole is centered downstream thereof. A cylindrical orifice member 27 having a 26 (valve port) is fitted, and a rectifying member 6 used in the flow rate control valve 10A of the first embodiment is fitted further downstream thereof.

本実施形態の流量制御弁１０Ｅは、電磁弁用弁体２０を、電磁ソレノイド装置４０により軸線Ｌ方向に上下動させ、弁ハウジング１１１内に形成された弁ポート１４０との開度を全開状態と全閉状態（絞り状態）とに制御可能な構成である。流量制御弁１０Ｅは、電磁弁用弁体２０を全開状態とすると、大流量制御域の弁となり、一次継手管１１から流入してきた流体が弁室１１Ｃ及び弁ポート１４０を介して、二次継手管１２に流入するようになっている。一方、図８に示すように、電磁弁用弁体２０を全閉状態とすると、一次継手管１１から流入してきた流体が、円筒フィルタ要素３２を介して流入孔３３（流入口）からフィルタ要素２５を通って絞り孔２６に流入し、整流部材６を通過してから、凹部の下端部２０ａ（流出口）から二次継手管１２に流入するようになっている。なお、整流部材６には、第２実施形態乃至第４実施形態の流量制御弁１０Ｂ～１０Ｄで用いたいずれの整流部材６を用いてもよい。 In the flow control valve 10E of the present embodiment, the solenoid valve body 20 is moved up and down in the axis L direction by the solenoid valve body 40, and the opening degree with the valve port 140 formed in the valve housing 111 is fully opened. It is a configuration that can be controlled to the fully closed state (aperture state). When the solenoid valve body 20 is fully opened, the flow rate control valve 10E becomes a valve in the large flow rate control range, and the fluid flowing in from the primary joint pipe 11 passes through the valve chamber 11C and the valve port 140 to the secondary joint. It is designed to flow into the pipe 12. On the other hand, as shown in FIG. 8, when the solenoid valve valve body 20 is fully closed, the fluid flowing in from the primary joint pipe 11 passes through the cylindrical filter element 32 from the inflow hole 33 (inflow port) to the filter element. It flows into the throttle hole 26 through 25, passes through the rectifying member 6, and then flows into the secondary joint pipe 12 from the lower end portion 20a (outlet) of the recess. As the rectifying member 6, any rectifying member 6 used in the flow control valves 10B to 10D of the second to fourth embodiments may be used.

本実施形態の流量制御弁１０Ｅでは、例えば、整流部材６の代わりに濾過密度が均一なフィルタ要素を設けた場合に比して、整流部材６の略全体を流体が通過し、整流部材６の略全体によって流体内の気泡を細分化させることで、特に小流量制御域における消音効果を得ることができ、流体通過音の十分な抑制を図ることができる。 In the flow control valve 10E of the present embodiment, for example, as compared with the case where a filter element having a uniform filtration density is provided instead of the rectifying member 6, the fluid passes through substantially the entire rectifying member 6 and the rectifying member 6 By subdividing the bubbles in the fluid by substantially the whole, it is possible to obtain a muffling effect especially in the small flow rate control range, and it is possible to sufficiently suppress the sound passing through the fluid.

以上、図面を参照して、本発明を実施するための形態を第１実施形態乃至第４実施形態、及び他の実施形態に基づいて詳述してきたが、具体的な構成は、これらの実施形態に限らず、本発明の要旨を逸脱しない程度の設計的変更は、本発明に含まれる。 As described above, the embodiments for carrying out the present invention have been described in detail based on the first to fourth embodiments and other embodiments with reference to the drawings. Not limited to the form, design changes to the extent that the gist of the present invention is not deviated are included in the present invention.

例えば、上記第１実施形態乃至第４実施形態では、高抵抗部６１の範囲を、副弁ポート２４の内径よりも大きくしたが、これに限定されず、副弁ポート２４の内径よりも小さくしてもよい。また、上記第２実施形態及び第３実施形態の整流部材６の高抵抗部６１を、上記第１実施形態のように、高抵抗部６１の方が低抵抗部６２よりも高い濾過密度を有しているようにしてもよい。また、上記第１実施形態乃至第４実施形態では、主弁部２１の下端部内に整流部材６を設けたが、これに限定されず、例えば、整流部材６を、弁ハウジング１の主弁ポート１４内や二次継手管１２内等に設けてもよい。この場合、大流量制御域における消音効果を得ることもできる。 For example, in the first to fourth embodiments, the range of the high resistance portion 61 is made larger than the inner diameter of the auxiliary valve port 24, but is not limited to this, and is made smaller than the inner diameter of the auxiliary valve port 24. You may. Further, the high resistance portion 61 of the rectifying member 6 of the second embodiment and the third embodiment has a higher filtration density in the high resistance portion 61 than in the low resistance portion 62 as in the first embodiment. You may do so. Further, in the first to fourth embodiments, the rectifying member 6 is provided in the lower end portion of the main valve portion 21, but the present invention is not limited to this, and for example, the rectifying member 6 can be used as the main valve port of the valve housing 1. It may be provided in 14 or in the secondary joint pipe 12. In this case, it is possible to obtain a muffling effect in the large flow rate control range.

さらに、上記本発明の一例では、流量制御弁１０を通常のエアコンに使用したが、これに限定されず、ビル用のマルチエアコンや冷凍機などに使用してもよい。 Further, in the above example of the present invention, the flow rate control valve 10 is used for a normal air conditioner, but the present invention is not limited to this, and the flow control valve 10 may be used for a multi air conditioner for a building, a refrigerator, or the like.

１０，１０Ａ～１０Ｅ 流量制御弁
２５ 連通孔（流入口）
３３ 流入孔（流入口）
２１１ 流出部（流出口）
２ 主弁体（弁本体）
２０ 電磁弁用弁体（弁本体）
２４ 副弁ポート（弁口）
２６ 絞り孔（弁口）
６ 整流部材
６１ 高抵抗部
６１ａ 円錐部
６２ 低抵抗部
７ 板材
７ａ 小孔
７ｂ 大孔
２１ 主弁部（弁座部）
５ 拡径部（第２弁口）
２１ａ 第１段差部（第３弁口）
Ｌ 軸線
３ 副弁体（弁体）
９０ 冷凍サイクルシステム 10,10A-10E Flow control valve 25 Communication hole (inlet)
33 Inflow hole (inflow port)
211 Outflow part (outlet)
2 Main valve body (valve body)
20 Solenoid valve valve body (valve body)
24 Secondary valve port (valve port)
26 Aperture hole (valve port)
6 Rectifying member 61 High resistance part 61a Conical part 62 Low resistance part 7 Plate material 7a Small hole 7b Large hole 21 Main valve part (valve seat part)
5 Enlarged diameter part (second valve port)
21a 1st step (3rd valve port)
L-axis line 3 Sub-valve body (valve body)
90 Refrigeration cycle system

Claims (9)

流入口及び流出口を有した弁本体と、前記弁本体の内部に設けられて流体の流路を絞る弁口と、を備えた流量制御弁であって、
前記弁口と前記流出口との間には、流体を通過させることで整流する整流部材が設けられ、
前記整流部材は、その中心側に流路抵抗の高い高抵抗部と、前記高抵抗部よりも外側に流路抵抗の低い低抵抗部と、を備えることを特徴とする流量制御弁。 A flow control valve including a valve body having an inflow port and an outflow port, and a valve port provided inside the valve body for narrowing a fluid flow path.
A rectifying member that rectifies by passing a fluid is provided between the valve port and the outlet.
The flow control valve is characterized in that the rectifying member includes a high resistance portion having a high flow path resistance on the center side thereof and a low resistance portion having a low flow path resistance outside the high resistance portion. 前記整流部材の前記高抵抗部は、前記弁口の内径よりも大きい範囲に設けられていることを特徴とする請求項１に記載の流量制御弁。 The flow rate control valve according to claim 1, wherein the high resistance portion of the rectifying member is provided in a range larger than the inner diameter of the valve opening. 前記整流部材は、前記高抵抗部の方が前記低抵抗部よりも高い濾過密度を有していることを特徴とする請求項１又は２に記載の流量制御弁。 The flow rate control valve according to claim 1 or 2, wherein the rectifying member has a higher filtration density in the high resistance portion than in the low resistance portion. 前記整流部材は、前記高抵抗部の方が前記低抵抗部よりも大きな厚みに形成されていることを特徴とする請求項１又は２に記載の流量制御弁。 The flow rate control valve according to claim 1 or 2, wherein the rectifying member is formed with a thickness of the high resistance portion larger than that of the low resistance portion. 前記整流部材の前記高抵抗部は、前記弁口に対向する面が中心側から外側に向かって厚みが小さくなる傾斜面を有して形成されていることを特徴とする請求項１又は２に記載の流量制御弁。 According to claim 1 or 2, the high resistance portion of the rectifying member is formed so that the surface facing the valve port has an inclined surface whose thickness decreases from the center side to the outside. The flow control valve described. 前記整流部材の前記弁口に対向する側には、前記高抵抗部に位置する小孔と前記低抵抗部に位置する大孔とを有した板材が設けられていることを特徴とする請求項１又は２に記載の流量制御弁。 The claim is characterized in that a plate material having a small hole located in the high resistance portion and a large hole located in the low resistance portion is provided on the side of the rectifying member facing the valve port. The flow rate control valve according to 1 or 2. 前記弁口を構成する弁座部には、前記弁口から前記流出口に向かって内径が大きくなる第２弁口と、前記第２弁口から前記流出口に向かってさらに内径が大きくなる第３弁口と、が設けられ、前記第３弁口に前記整流部材が設けられていることを特徴とする請求項１乃至６のいずれか１項に記載の流量制御弁。 The valve seat portion constituting the valve port has a second valve port whose inner diameter increases from the valve port toward the outlet, and a second valve port whose inner diameter further increases from the second valve port toward the outlet. The flow control valve according to any one of claims 1 to 6, wherein a three-valve port is provided, and the rectifying member is provided at the third valve port. 軸線方向に進退移動することで前記弁口の開口面積を調整する弁体と、前記弁体を進退駆動する駆動部と、をさらに備えることを特徴とする請求項１乃至７のいずれか１項に記載の流量制御弁。 One of claims 1 to 7, further comprising a valve body that adjusts the opening area of the valve opening by moving forward and backward in the axial direction, and a drive unit that drives the valve body forward and backward. Flow control valve according to. 請求項１乃至８のいずれか１項に記載の流量制御弁を備えることを特徴とする冷凍サイクルシステム。 A refrigeration cycle system comprising the flow rate control valve according to any one of claims 1 to 8.
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