JP7372885B2 - Electric valve and refrigeration cycle system - Google Patents

Electric valve and refrigeration cycle system Download PDF

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JP7372885B2
JP7372885B2 JP2020134532A JP2020134532A JP7372885B2 JP 7372885 B2 JP7372885 B2 JP 7372885B2 JP 2020134532 A JP2020134532 A JP 2020134532A JP 2020134532 A JP2020134532 A JP 2020134532A JP 7372885 B2 JP7372885 B2 JP 7372885B2
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main valve
valve body
valve
port
sub
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JP2022030466A (en
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大樹 中川
亮司 小池
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to CN202410249476.2A priority patent/CN117905928A/en
Priority to CN202110850714.1A priority patent/CN114060581A/en
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Priority to JP2023180154A priority patent/JP2024010029A/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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • 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
    • F16K1/02—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 with screw-spindle
    • 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
    • F16K1/44—Details of seats or valve members of double-seat valves
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)

Description

本発明は、冷凍サイクルシステムなどに使用する電動弁及び冷凍サイクルシステムに関する。 The present invention relates to an electric valve used in a refrigeration cycle system and the like, and a refrigeration cycle system.

従来、空気調和機の冷凍サイクルに設けられる電動弁として、小流量制御域と大流量域とで流量制御する電動弁がある。このような電動弁は、室内機に搭載される用途（例えば除湿弁）があり、例えば特開２０１７－２１１０３４号公報（特許文献１）に開示されている。 BACKGROUND ART Conventionally, as an electric valve provided in a refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control area and a large flow rate area. Such a motor-operated valve is used for being mounted on an indoor unit (for example, as a dehumidification valve), and is disclosed in, for example, Japanese Patent Application Publication No. 2017-211034 (Patent Document 1).

この特許文献１の電動弁は、主弁体（弁体３２）と副弁体（弁軸２０）とを備え、副弁体の連通路（２９ｗ）から副弁体内部を介して主弁体の副弁口（弁口３６）へと冷媒を通過させる小流量制御を行うものである。また、主弁体の全開時において、流体（冷媒）の大部分は主弁体と主弁座との隙間である主弁口（弁口１６）に流れるものの、流体の一部が副弁体の連通路（２９ｗ）から主弁体の副弁口に流れる（特許文献１の段落［００５０］）。 The electric valve of Patent Document 1 includes a main valve body (valve body 32) and a sub-valve body (valve shaft 20), and the main valve body is This is to control the small flow rate of the refrigerant to pass through to the sub-valve port (valve port 36). Furthermore, when the main valve body is fully open, most of the fluid (refrigerant) flows to the main valve port (valve port 16), which is the gap between the main valve body and the main valve seat, but some of the fluid flows to the sub valve body. flows from the communication path (29w) to the sub-valve port of the main valve body (paragraph [0050] of Patent Document 1).

また、この種の電動弁として、例えば図７に示すものが考えられている。この電動弁は、弁本体ａの主弁室ａＲ内に主弁ポートｂを開閉する主弁体ｃと、主弁体ｃに形成された副弁室ｃＲ内で副弁ポートｄの開度を制御する副弁体ｅとを備えた電動弁である。そして、主弁体ｃで主弁ポートｂを全閉として、副弁体ｅで副弁ポートｄの開度を制御して流体を絞る小流量制御域と、主弁体ｃで主弁ポートｂを全開として第１継手管ｆの入口ポートｇから流入する流体を主弁ポートｂに流す大流量域とを有する二段式の電動弁である。 Further, as this type of electric valve, one shown in FIG. 7, for example, has been considered. This electric valve has a main valve body c that opens and closes a main valve port b in a main valve chamber aR of a valve body a, and a main valve body c that controls the opening degree of a sub-valve port d in a sub-valve chamber cR formed in the main valve body c. This is an electric valve equipped with a sub-valve element e to be controlled. The main valve body c fully closes the main valve port b, and the sub-valve body e controls the opening degree of the sub-valve port d to throttle the fluid, and the main valve body c controls the main valve port b. This is a two-stage motor-operated valve having a large flow rate region in which the valve is fully opened and fluid flowing in from the inlet port g of the first joint pipe f flows to the main valve port b.

特開２０１７－２１１０３４号公報JP 2017-211034 Publication

特許文献１の電動弁では、主弁体の全開時（大流量域）において、流体の一部が副弁体の連通路（２９ｗ）から主弁体の副弁口に流れるため、弁室内の流速や圧力に乱れが生じて流体の流れが不安定になり、騒音や振動の原因となる可能性がある。また、図７に示す電動弁では、主弁体ｃの全開状態（大流量域）においては、流体は主弁室ａＲから主に主弁体ｃと主弁ポートｂとの間を通過するが、主弁体ｃに設けられた連通孔ｈから主弁体ｃの内部の副弁室ｃＲを通過し、副弁体ｅと副弁ポートｄとの間を通過する流れも生じる。このため、この副弁ポートｄを通過して絞られる流れにより、主弁ポートｂに流れる流体の速度や圧力の挙動が安定しなくなり、主弁体ｃの振動や冷媒通過音が発生する恐れがある。 In the motor-operated valve of Patent Document 1, when the main valve body is fully open (large flow range), a portion of the fluid flows from the communication passage (29w) of the sub-valve body to the sub-valve port of the main valve body. Disturbances occur in the flow velocity and pressure, making the fluid flow unstable and potentially causing noise and vibration. In addition, in the motor-operated valve shown in FIG. 7, when the main valve body c is fully open (large flow range), fluid mainly passes between the main valve body c and the main valve port b from the main valve chamber aR. , a flow passes through the auxiliary valve chamber cR inside the main valve element c from the communication hole h provided in the main valve element c, and passes between the auxiliary valve element e and the auxiliary valve port d. Therefore, due to the flow that passes through the sub-valve port d and is throttled, the velocity and pressure behavior of the fluid flowing into the main valve port b become unstable, which may cause vibrations in the main valve body c and refrigerant passing noise. be.

本発明は、主弁体で主弁ポートを全閉状態とし、この主弁体に形成された副弁ポートと副弁体との間の絞り部により冷媒の小流量制御域での流量制御を行うとともに、主弁体で主弁ポートを全開状態として流体を主弁ポートへ流す大流量域の制御を行う二段式の電動弁において、大流量域の制御時に、主弁体と主弁ポートに対する流体の流れを安定させて電動弁自体の騒音や振動の発生を抑制することを課題とする。 The present invention fully closes the main valve port with the main valve element, and controls the flow rate of refrigerant in a small flow rate control range using the throttle section between the auxiliary valve port and the auxiliary valve element formed in the main valve element. In a two-stage electric valve that controls a large flow range where the main valve port is fully open with the main valve body and the fluid flows to the main valve port, when controlling the large flow range, the main valve body and the main valve port The objective is to stabilize the flow of fluid to and suppress the noise and vibration of the electric valve itself.

本発明の電動弁は、弁本体の主弁室内に設けられて該主弁室に開口する主弁ポートを開閉する主弁体と、前記主弁体に形成された副弁室内で該主弁体に形成された副弁ポートの軸線方向に移動して該副弁ポートの開度を制御する副弁体と、を備え、前記主弁体で前記主弁ポートを閉として前記副弁体で前記副弁ポートの開度を制御して流体を絞る小流量制御域と、前記主弁体で前記主弁ポートを全開として、前記主弁体の側部にて前記主弁室に開口する入口ポートから流入する流体を前記主弁ポートに流す大流量域と、を有する二段式の電動弁において、前記主弁体に、前記主弁室から前記副弁室に連通する連通孔が設けられ、前記連通孔は、前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が前記入口ポートの開口と直接対向しない位置に設けられ、前記弁本体には、前記主弁体をガイドするガイド部材が設けられ、前記主弁体の前記軸線方向における前記主弁ポート側と反対側の端部には、前記主弁体と別体に設けられたリテーナが結合され、前記リテーナは、前記副弁体に係合可能に設けられ、前記ガイド部材と前記リテーナとの間には、前記リテーナを介して前記主弁体を前記主弁ポート側に付勢する主弁ばねが設けられていることを特徴とする。 The motor-operated valve of the present invention includes a main valve body that is provided in a main valve chamber of a valve body and opens and closes a main valve port that opens into the main valve chamber, and a main valve body that is disposed in a sub-valve chamber that is formed in the main valve body. a sub-valve body that moves in the axial direction of a sub-valve port formed in the body to control the opening degree of the sub-valve port, the main valve body closes the main valve port, and the sub-valve body closes the main valve port; a small flow rate control region that throttles the fluid by controlling the opening degree of the sub-valve port; and an inlet that opens into the main valve chamber at a side of the main valve body when the main valve port is fully opened by the main valve body. A two-stage motor-operated valve having a large flow rate region that allows fluid flowing in from a port to flow into the main valve port, wherein the main valve body is provided with a communication hole that communicates from the main valve chamber to the auxiliary valve chamber. , the communication hole is provided at a position where at least one of the communication holes located on the inlet port side does not directly oppose the opening of the inlet port when the main valve body is fully opened; , a guide member for guiding the main valve body is provided, and a retainer provided separately from the main valve body is provided at an end of the main valve body opposite to the main valve port side in the axial direction. the retainer is provided so as to be engageable with the auxiliary valve body, and a space between the guide member and the retainer urges the main valve body toward the main valve port side through the retainer. It is characterized by being provided with a main valve spring .

この際、前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が、前記主弁体をガイドするガイド部材の下部ガイド部内に位置することを特徴とする電動弁が好ましい。 In this case, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located within a lower guide portion of a guide member that guides the main valve body. Electrically operated valves are preferred.

また、前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が、前記入口ポートの前記開口の前方から外れた位置にあることを特徴とする電動弁が好ましい。 Furthermore, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located at a position away from the front of the opening of the inlet port. preferable.

また、前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔の中心軸線と、前記入口ポートの中心軸線とが、前記主弁ポートの軸線Ｌに対し垂直な平面に投影したときに交差することを特徴とする電動弁が好ましい。 Further, when the main valve body is fully opened, a center axis of at least one of the communication holes located on the inlet port side and a center axis of the inlet port are perpendicular to the axis L of the main valve port. It is preferable to use an electric valve that is characterized by intersecting when projected onto a flat plane.

本発明の冷凍サイクルシステムは、圧縮機と、室内熱交換器と、室外熱交換器と、前記室内熱交換器と前記室外熱交換器との間に設けられた電子膨張弁と、前記室内熱交換器に設けられる除湿弁とを含む冷凍サイクルシステムであって、前記電動弁が、前記除湿弁として用いられていることを特徴とする。 The refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and the indoor heat exchanger. A refrigeration cycle system including a dehumidification valve provided in an exchanger, characterized in that the electric valve is used as the dehumidification valve.

本発明の電動弁及び冷凍サイクルシステムによれば、主弁体の全開時において、入口ポートから主弁室に流入する流体が連通孔に対して直接噴射されることがないので、連通孔から副弁室への流体の流入を低減することができる。したがって、主弁体と主弁ポートに対する流体の流れを安定させることができ、電動弁自体の騒音や振動の発生を抑制することができる。 According to the electric valve and refrigeration cycle system of the present invention, when the main valve body is fully opened, the fluid flowing into the main valve chamber from the inlet port is not directly injected into the communication hole, so the fluid flows from the communication hole into the sub-valve chamber. Inflow of fluid into the valve chamber can be reduced. Therefore, the flow of fluid to the main valve body and the main valve port can be stabilized, and the generation of noise and vibration of the electric valve itself can be suppressed.

本発明の第１実施形態の電動弁の小流量制御域状態の縦断面図である。FIG. 2 is a longitudinal cross-sectional view of the electric valve according to the first embodiment of the present invention in a small flow rate control region state. 第１実施形態の電動弁の大流量域状態の縦断面図である。FIG. 2 is a longitudinal cross-sectional view of the electric valve of the first embodiment in a large flow range state. 本発明の第２実施形態の電動弁の大流量域状態の要部拡大縦断面図（Ａ）及び主弁ポートの軸線Ｌに対し垂直な平面に投影した要部拡大横断面図（Ｂ）である。An enlarged vertical cross-sectional view (A) of the main part of the electric valve according to the second embodiment of the present invention in a large flow range state and an enlarged cross-sectional view (B) of the main part projected on a plane perpendicular to the axis L of the main valve port. be. 本発明の第３実施形態の電動弁の大流量域状態の要部拡大縦断面図である。FIG. 7 is an enlarged longitudinal cross-sectional view of a main part of an electric valve according to a third embodiment of the present invention in a large flow range state. 本発明の第４実施形態の電動弁の大流量域状態の連通孔と入口ポートを主弁ポートの軸線Ｌに対し垂直な平面に投影した要部拡大横断面図である。FIG. 7 is an enlarged cross-sectional view of the main part of the electric valve according to the fourth embodiment of the present invention, in which the communication hole and the inlet port in a large flow range state are projected onto a plane perpendicular to the axis L of the main valve port. 本発明の実施形態の冷凍サイクルシステムを示す図である。1 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention. 二段式の電動弁の一例とその課題を説明する図である。FIG. 2 is a diagram illustrating an example of a two-stage electric valve and its problems.

次に、本発明の電動弁及び冷凍サイクルシステムの実施形態について図面を参照して説明する。図１は第１実施形態の電動弁の小流量制御域状態の縦断面図、図２は第１実施形態の電動弁の大流量域状態の縦断面図である。なお、以下の説明における「上下」の概念は図１及び図２の図面における上下に対応する。この電動弁１００は、弁ハウジング１と、ガイド部材２と、主弁体３と、副弁体４と、駆動部５と、を備えている。 Next, embodiments of the electric valve and refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal cross-sectional view of the motor-operated valve according to the first embodiment in a small flow control region state, and FIG. 2 is a longitudinal cross-sectional view of the motor-operated valve according to the first embodiment in a large flow control region state. Note that the concept of "up and down" in the following description corresponds to the up and down in the drawings of FIGS. 1 and 2. This electric valve 100 includes a valve housing 1 , a guide member 2 , a main valve body 3 , a sub-valve body 4 , and a drive section 5 .

弁ハウジング１は例えば、黄銅、ステンレス等で略円筒形状に形成されており、その内側に主弁室１Ｒを有している。弁ハウジング１の外周片側には主弁室１Ｒに導通される第１継手管１１が接続されるとともに、下端から下方に延びる筒状部に第２継手管１２が接続されている。また、弁ハウジング１の第２継手管１２の主弁室１Ｒ側には主弁座１３が形成され、この主弁座１３の内側は主弁ポート１３ａとなっている。主弁ポート１３ａは軸線Ｌを中心とする円柱形状の透孔（貫通した孔）であり、第２継手管１２は主弁ポート１３ａを介して主弁室１Ｒに導通される。そして、第１継手管１１の主弁室１Ｒ側の内側端部は入口ポート１１ａとなっている。 The valve housing 1 is made of, for example, brass or stainless steel and has a substantially cylindrical shape, and has a main valve chamber 1R inside thereof. A first joint pipe 11 that communicates with the main valve chamber 1R is connected to one side of the outer periphery of the valve housing 1, and a second joint pipe 12 is connected to a cylindrical portion extending downward from the lower end. Further, a main valve seat 13 is formed on the main valve chamber 1R side of the second joint pipe 12 of the valve housing 1, and the inside of this main valve seat 13 is a main valve port 13a. The main valve port 13a is a cylindrical through hole centered on the axis L, and the second joint pipe 12 is communicated with the main valve chamber 1R via the main valve port 13a. The inner end of the first joint pipe 11 on the side of the main valve chamber 1R serves as an inlet port 11a.

弁ハウジング１の上端の開口部には、ガイド部材２が取り付けられている。ガイド部材２は、弁ハウジング１の内周面内に圧入される圧入部２１と、圧入部２１から上方に位置する略円柱状の上部ガイド部２２と、上部ガイド部２２の上部に延設されたホルダ部２３と、圧入部２１の外周に設けられたリング状のフランジ部２４と、圧入部２１から下方に位置する略円柱状の下部ガイド部２５とを有している。圧入部２１、上部ガイド部２２、下部ガイド部２５、ホルダ部２３は樹脂製の一体品として構成されている。また、フランジ部２４は、例えば、黄銅、ステンレス等の金属板であり、このフランジ部２４は、インサート成形により樹脂製の圧入部２１と共に一体に設けられている。 A guide member 2 is attached to an opening at the upper end of the valve housing 1 . The guide member 2 includes a press-fitting part 21 that is press-fitted into the inner circumferential surface of the valve housing 1, a substantially cylindrical upper guide part 22 located above the press-fitting part 21, and an upper part of the upper guide part 22 extending therefrom. A ring-shaped flange part 24 provided on the outer periphery of the press-fitting part 21 , and a substantially cylindrical lower guide part 25 located below the press-fitting part 21 are provided. The press-fitting part 21, the upper guide part 22, the lower guide part 25, and the holder part 23 are constructed as an integral part made of resin. Further, the flange portion 24 is, for example, a metal plate made of brass, stainless steel, or the like, and is integrally provided with the resin press-fit portion 21 by insert molding.

ガイド部材２は、圧入部２１により弁ハウジング１に組み付けられ、フランジ部２４を介して弁ハウジング１の上端部に溶接により固定されている。また、ガイド部材２において、圧入部２１及び上部ガイド部２２、下部ガイド部２５の内側には軸線Ｌと同軸の円筒形状のガイド孔２Ａが形成されるとともに、ホルダ部２３の中心には、ガイド孔２Ａと同軸の雌ねじ部２３ａとそのねじ孔が形成されている。そして、ガイド孔２Ａ内には主弁体３が配設されている。 The guide member 2 is assembled to the valve housing 1 by a press-fitting part 21, and is fixed to the upper end part of the valve housing 1 via a flange part 24 by welding. Further, in the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the press-fitting part 21, the upper guide part 22, and the lower guide part 25, and a guide hole 2A coaxial with the axis L is formed in the center of the holder part 23. A female screw portion 23a coaxial with the hole 2A and its screw hole are formed. A main valve body 3 is disposed within the guide hole 2A.

主弁体３は、主弁座１３に対して着座及び離座する主弁部３１と、副弁体４を保持する保持部３２とで構成されている。主弁部３１の内側には円柱状の膨張孔３Ａが形成されるとともに、保持部３２の内側には円柱状の副弁室３Ｒが形成され、この副弁室３Ｒの内周面は副弁ガイド孔３Ｂとなっている。そして、主弁部３１と保持部３２との間には、軸線Ｌを中心として副弁室３Ｒから膨張孔３Ａ側に開口する円柱状の副弁ポート３ａが形成されている。 The main valve body 3 includes a main valve part 31 that seats and leaves the main valve seat 13, and a holding part 32 that holds the sub valve body 4. A cylindrical expansion hole 3A is formed inside the main valve part 31, and a cylindrical sub-valve chamber 3R is formed inside the holding part 32, and the inner peripheral surface of the sub-valve chamber 3R is This is a guide hole 3B. A cylindrical sub-valve port 3a is formed between the main valve part 31 and the holding part 32 and opens from the sub-valve chamber 3R to the expansion hole 3A side with the axis L as the center.

また、主弁体３の保持部３２の側面には、軸線Ｌと交差する方向で主弁室１Ｒから副弁室３Ｒに連通する連通路３ｂが形成されている。この実施形態では、連通路３ｂは、軸線Ｌ周りに回転対象な位置に放射状に複数本（例えば４本）形成されている。そして、４本の連通路３ｂは、軸線Ｌ方向で、第１継手管１１の開口である入口ポート１１ａに直接対向しない位置に形成されている。なお、ここでは連通路３ｂを４本としたものを例示したが、入口ポート１１ａに直接対向しない位置であれば何本でもよい。 Further, a communication passage 3b communicating from the main valve chamber 1R to the sub-valve chamber 3R in a direction intersecting the axis L is formed on the side surface of the holding portion 32 of the main valve body 3. In this embodiment, a plurality of communicating passages 3b (for example, four) are formed radially at positions that are rotationally symmetrical about the axis L. The four communicating passages 3b are formed in positions that do not directly face the inlet port 11a, which is the opening of the first joint pipe 11, in the direction of the axis L. Note that although four communicating paths 3b are illustrated here, any number of communicating paths 3b may be used as long as they are not directly opposed to the inlet port 11a.

主弁体３は、保持部３２の上端部にリテーナ３４を有するとともに、リテーナ３４とガイド部材２のガイド孔２Ａの上端部との間に主弁ばね３５を有しており、この主弁ばね３５により主弁体３は主弁座１３の方向（閉方向）に付勢されている。副弁体４は、ロータ軸５１の下端部にこのロータ軸５１と一体に形成されており、この副弁体４はガイド用ボス部４１とニードル弁４２とで構成されている。また、副弁体４のニードル弁４２は、その先端が副弁ポート３ａ対して軸線Ｌ方向に挿通されるものであり、ニードル弁４２と副弁ポート３ａとの隙間を小流量の冷媒が流れることにより小流量制御が行われる。なお、ガイド用ボス部４１の上端には、潤滑性樹脂からなる円環状のワッシャ４３が配設され、ガイド用ボス部４１は、副弁ガイド孔３Ｂ内に摺動可能に挿通されている。 The main valve body 3 has a retainer 34 at the upper end of the holding part 32, and a main valve spring 35 between the retainer 34 and the upper end of the guide hole 2A of the guide member 2. 35 urges the main valve body 3 in the direction of the main valve seat 13 (closed direction). The sub-valve body 4 is formed integrally with the rotor shaft 51 at the lower end of the rotor shaft 51, and the sub-valve body 4 includes a guide boss portion 41 and a needle valve 42. Further, the needle valve 42 of the sub-valve body 4 has its tip inserted into the sub-valve port 3a in the direction of the axis L, and a small flow rate of refrigerant flows through the gap between the needle valve 42 and the sub-valve port 3a. As a result, small flow rate control is performed. An annular washer 43 made of lubricating resin is disposed at the upper end of the guide boss 41, and the guide boss 41 is slidably inserted into the sub-valve guide hole 3B.

弁ハウジング１の上端にはケース１４が溶接等によって気密に固定され、このケース１４の内外に駆動部５が構成されている。駆動部５は、ステッピングモータ５Ａと、ステッピングモータ５Ａの回転により副弁体４を進退させるねじ送り機構５Ｂと、ステッピングモータ５Ａの回転を規制するストッパ機構５Ｃと、を備えている。 A case 14 is airtightly fixed to the upper end of the valve housing 1 by welding or the like, and a drive section 5 is configured inside and outside the case 14. The drive unit 5 includes a stepping motor 5A, a screw feeding mechanism 5B that advances and retreats the sub-valve body 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C that restricts the rotation of the stepping motor 5A.

ステッピングモータ５Ａは、ロータ軸５１と、ケース１４の内部に回転可能に配設されたマグネットロータ５２と、ケース１４の外周においてマグネットロータ５２に対して対向配置されたステータコイル５３と、その他、図示しないヨークや外装部材等により構成されている。ロータ軸５１はブッシュを介してマグネットロータ５２の中心に取り付けられ、このロータ軸５１のガイド部材２側の外周には雄ねじ部５１ａが形成されている。この雄ねじ部５１ａはガイド部材２の雌ねじ部２４ａに螺合されており、これにより、ガイド部材２はロータ軸５１を軸線Ｌ上に支持している。そして、ガイド部材２の雌ねじ部２４ａとロータ軸５１の雄ねじ部５１ａはねじ送り機構５Ｂを構成している。なお、ケース１４の内側天井部には回転ストッパ機構５Ｃを保持する円筒部１４ａが設けられ、この円筒部１４ａ内には、ロータ軸５１の上端をガイドするガイド部材５４が配設されている。 The stepping motor 5A includes a rotor shaft 51, a magnet rotor 52 rotatably disposed inside a case 14, a stator coil 53 disposed opposite to the magnet rotor 52 on the outer periphery of the case 14, and other components shown in the figure. It is made up of a yoke, exterior members, etc. The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male threaded portion 51a is formed on the outer periphery of the rotor shaft 51 on the guide member 2 side. The male threaded portion 51a is screwed into the female threaded portion 24a of the guide member 2, so that the guide member 2 supports the rotor shaft 51 on the axis L. The female threaded portion 24a of the guide member 2 and the male threaded portion 51a of the rotor shaft 51 constitute a screw feeding mechanism 5B. A cylindrical portion 14a that holds the rotation stopper mechanism 5C is provided on the inner ceiling of the case 14, and a guide member 54 that guides the upper end of the rotor shaft 51 is disposed within the cylindrical portion 14a.

以上の構成により、ステッピングモータ５Ａが駆動されるとマグネットロータ５２及びロータ軸５１が回転し、ロータ軸５１の雄ねじ部５１ａとガイド部材２の雌ねじ部２４ａとのねじ送り機構５Ｂにより、マグネットロータ５２と共にロータ軸５１が軸線Ｌ方向に移動する。そして、副弁体４が軸線Ｌ方向に進退移動してニードル弁４２が副弁ポート３ａに対して近接又は離間する。また、ニードル弁４２が上昇するとき、ワッシャ４３が主弁体３のリテーナ３４に係合し、主弁体３は副弁体４と共に移動して、主弁座１３から離座する。なお、マグネットロータ５２には突起部５２ａが形成されており、マグネットロータ５２の回転に伴って突起部５２ａが回転ストッパ機構５Ｃを作動させ、ロータ軸５１（及びマグネットロータ５２）の最下端位置及び最上端位置が規制される。 With the above configuration, when the stepping motor 5A is driven, the magnet rotor 52 and the rotor shaft 51 rotate, and the screw feeding mechanism 5B of the male threaded portion 51a of the rotor shaft 51 and the female threaded portion 24a of the guide member 2 causes the magnet rotor 52 to rotate. At the same time, the rotor shaft 51 moves in the direction of the axis L. Then, the sub-valve body 4 moves forward and backward in the direction of the axis L, and the needle valve 42 approaches or separates from the sub-valve port 3a. Further, when the needle valve 42 rises, the washer 43 engages with the retainer 34 of the main valve body 3, and the main valve body 3 moves together with the sub valve body 4 and leaves the main valve seat 13. Note that the magnet rotor 52 is formed with a protrusion 52a, and as the magnet rotor 52 rotates, the protrusion 52a operates the rotation stopper mechanism 5C, and the lowermost position of the rotor shaft 51 (and the magnet rotor 52) and The top position is restricted.

図１の小流量制御域状態では、主弁体３は主弁座１３に着座した状態で主弁ポート１３ａが弁閉となり、副弁体４のニードル弁４２により副弁ポート３ａの開度が制御され、小流量の制御が行われる。このとき、連通路３ｂはガイド部材２の下部ガイド部２５の下端よりも下方に位置し、主弁室１Ｒ内の冷媒は連通路３ｂを通って副弁室３Ｒに流れる。 In the small flow rate control region state of FIG. 1, the main valve port 13a is closed with the main valve body 3 seated on the main valve seat 13, and the opening degree of the sub valve port 3a is controlled by the needle valve 42 of the sub valve body 4. controlled, and small flow control is performed. At this time, the communication passage 3b is located below the lower end of the lower guide portion 25 of the guide member 2, and the refrigerant in the main valve chamber 1R flows into the sub valve chamber 3R through the communication passage 3b.

図２の大流量域状態では、冷媒は主弁室１Ｒから主に主弁体３の主弁部３１と主弁ポート１３ａとの間を通過するが、この主弁体３の全開状態では、連通路３ｂは入口ポート１１ａから下部ガイド部２５によって遮られている。これにより、入口ポート１１ａから主弁室１Ｒに流入する流体が連通孔３ｂに対して直接噴射されることがないので、連通孔３ｂから副弁室３Ｒへの流体の流入を低減することができる。したがって、主弁体３と主弁ポート１３ａに対する流体の流れを安定させることができ、主弁体３の振動が抑制され、この電動弁１００の騒音や振動の発生を抑制することができる。 In the large flow range state of FIG. 2, the refrigerant mainly passes between the main valve portion 31 of the main valve body 3 and the main valve port 13a from the main valve chamber 1R, but when the main valve body 3 is fully open, The communication path 3b is blocked by the lower guide portion 25 from the inlet port 11a. As a result, the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, so it is possible to reduce the flow of fluid from the communication hole 3b into the sub-valve chamber 3R. . Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

図３は、本発明の第２実施形態の電動弁の大流量域状態の図であり、図３（Ａ）は要部拡大縦断面図、図３（Ｂ）は、図３（Ａ）の連通孔と入口ポートを主弁ポートの軸線Ｌに対し垂直な平面に投影した要部拡大横断面図である。第１実施形態との相違点は、入口ポート１１ａと反対側のガイド部材２′の下部ガイド２５の長さが短くなっているのに対し、入口ポート１１ａ側の下部ガイド２５が所定の幅において長くなっていることと、図示しないが、主弁体３が上下方向に移動しても回転しないように回転ストッパが設けられている点である。回転ストッパは例えば、ガイド部材２′の内周に軸線方向縦長凸状のキー部が形成され、これが、主弁体３の外周に形成された縦長凹溝と嵌合することで主弁体３の回転を防止するものとしても良い。当初の弁組立時に、図３（Ａ）及び図３（Ｂ）に示すように大流量域状態において、入口ポート１１ａ側の連通孔３ｂが入口ポート１１ａ側の下部ガイド部によって遮られるように、主弁体３の回転ストッパの位置を設定しておけばよい。これにより、第２実施形態においても、第１実施形態と同様に大流量域状態で、入口ポート１１ａ側の連通孔３ｂは、下部ガイド２５により遮られる。よって、入口ポート１１ａから主弁室１Ｒに流入する流体が連通孔３ｂに対して直接噴射されることがないので、連通孔３ｂから副弁室３Ｒへの流体の流入を低減することができる。したがって、主弁体３と主弁ポート１３ａに対する流体の流れを安定させることができ、主弁体３の振動が抑制され、この電動弁１００の騒音や振動の発生を抑制することができる。 FIG. 3 is a diagram of the motor-operated valve according to the second embodiment of the present invention in a large flow range state, where FIG. 3(A) is an enlarged vertical cross-sectional view of the main part, and FIG. FIG. 2 is an enlarged cross-sectional view of the main part of the communication hole and the inlet port projected onto a plane perpendicular to the axis L of the main valve port. The difference from the first embodiment is that the length of the lower guide 25 of the guide member 2' on the side opposite to the inlet port 11a is shorter, whereas the lower guide 25 on the side of the inlet port 11a has a predetermined width. The main valve body 3 is longer in length and, although not shown, is provided with a rotation stopper to prevent the main valve body 3 from rotating even if it moves in the vertical direction. For example, the rotation stopper is formed by forming an axially elongated convex key part on the inner periphery of the guide member 2', which engages with a longitudinal groove formed on the outer periphery of the main valve element 3. It may also be used to prevent rotation. When initially assembling the valve, as shown in FIGS. 3(A) and 3(B), in a large flow range state, the communication hole 3b on the inlet port 11a side is blocked by the lower guide part on the inlet port 11a side. The position of the rotation stopper of the main valve body 3 may be set in advance. Accordingly, in the second embodiment as well, the communication hole 3b on the inlet port 11a side is blocked by the lower guide 25 in the large flow range state, as in the first embodiment. Therefore, since the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, the flow of fluid from the communication hole 3b into the sub-valve chamber 3R can be reduced. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

なお、図３においては、図３（Ｂ）に示すように入口ポート１１ａ側の連通孔３ｂの軸線は入口ポート１１ａの軸線と同じ方向（平行）としたが、これに限らず、入口ポート１１ａ側の連通孔３ｂが入口ポート１１ａ側の下部ガイド２５の所定幅内に入っていれば遮られるので、入口ポート１１ａ側の連通孔３ｂの軸線を入口ポートの軸線と所定の角度を成す方向としても良い（不図示）。 In addition, in FIG. 3, the axis of the communication hole 3b on the inlet port 11a side is set in the same direction (parallel) as the axis of the inlet port 11a, as shown in FIG. 3(B), but the axis is not limited to this. If the communication hole 3b on the side is within a predetermined width of the lower guide 25 on the inlet port 11a side, it will be blocked, so the axis of the communication hole 3b on the inlet port 11a side is set as a direction forming a predetermined angle with the axis of the inlet port. (not shown).

図４は本発明の第３実施形態の大流量域状態の要部拡大断面図であり、第１実施形態と
の相違点は、ガイド部材２″の圧入部２１″の下方にガイド部が無く、図４に示すように大流量域状態では、連通路３ｂが軸線Ｌ方向で第１継手管１１の開口である入口ポート１１ａに直接対向しない位置、すなわち、軸線Ｌ方向で入口ポート１１ａより上方に離れた位置に移動する点である。これにより、この第３実施形態においても大流量域状態では、冷媒は主弁室１Ｒから主に主弁体３の主弁部３１と主弁ポート１３ａとの間を通過するが、この主弁体３の全開状態では、入口ポート１１ａから主弁室１Ｒに流入する流体が連通孔３ｂに対して直接噴射されることがないので、連通孔３ｂから副弁室３Ｒへの流体の流入を低減することができる。したがって、主弁体３と主弁ポート１３ａに対する流体の流れを安定させることができ、主弁体３の振動が抑制され、この電動１００の騒音や振動の発生を抑制することができる。 FIG. 4 is an enlarged sectional view of the main part of the third embodiment of the present invention in a large flow range state, and the difference from the first embodiment is that there is no guide part below the press-fit part 21'' of the guide member 2'' , as shown in FIG. 4, in the large flow range state, the communication passage 3b is located at a position where it does not directly oppose the inlet port 11a, which is the opening of the first joint pipe 11, in the direction of the axis L, that is, above the inlet port 11a in the direction of the axis L. It is a point that moves to a far away position. As a result, in the third embodiment as well, in the large flow range state, the refrigerant mainly passes between the main valve portion 31 of the main valve body 3 and the main valve port 13a from the main valve chamber 1R; When the body 3 is fully open, the fluid flowing into the main valve chamber 1R from the inlet port 11a is not directly injected into the communication hole 3b, so the flow of fluid from the communication hole 3b into the sub-valve chamber 3R is reduced. can do. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric motor 100 can be suppressed.

尚、図４において連通孔３ｂの軸線と入口ポート１１ａの軸線を同じ方向としたが、異
なる方向としても良い。 Although the axis of the communication hole 3b and the axis of the inlet port 11a are set in the same direction in FIG. 4, they may be set in different directions.

図５は本発明の第４実施形態の大流量域状態の連通路３ｂと入口ポート１１ａを軸線Ｌに対し垂直な平面に投影した要部拡大横断面図であり、第３実施形態との相違点は、入口ポート１１ａ側の連通孔３ｂが軸線Ｌ方向で入口ポート１１ａの開口の内径の範囲に位置する点、連通孔３ｂの軸線の方向が入口ポート１１ａの軸線の方向と同じ方向（平行）ではなく、図５のように交差している点、さらに図示しないが、主弁体３が上下方向に移動しても回転しないように回転ストッパが設けられている点である。回転ストッパについては、第２実施形態と同様であり、主弁体３がＬ軸方向に移動しても連通孔３ｂの軸線と入口ポート１１ａの軸線が成す角度は変わらない。これにより、連通孔３ｂが軸線Ｌ方向で入口ポート１１ａの開口の内径の範囲に位置していても、図５に示すように、入口ポート１１ａから主弁室１Ｒに流入する流体が連通孔３ｂに対して直接噴射されることがないので、連通孔３ｂから副弁室３Ｒへの流体の流入を低減することができる。したがって、主弁体３と主弁ポート１３ａに対する流体の流れを安定させることができ、主弁体３の振動が抑制され、この電動弁１００の騒音や振動の発生を抑制することができる。 FIG. 5 is an enlarged cross-sectional view of main parts of the fourth embodiment of the present invention, in which the communication passage 3b and the inlet port 11a in a large flow area state are projected onto a plane perpendicular to the axis L, and shows differences from the third embodiment. The point is that the communication hole 3b on the inlet port 11a side is located within the range of the inner diameter of the opening of the inlet port 11a in the direction of the axis L, and the direction of the axis of the communication hole 3b is in the same direction (parallel) as the direction of the axis of the inlet port 11a. ), they intersect as shown in FIG. 5, and furthermore, although not shown, a rotation stopper is provided to prevent the main valve body 3 from rotating even if it moves in the vertical direction. The rotation stopper is the same as in the second embodiment, and even if the main valve body 3 moves in the L-axis direction, the angle formed by the axis of the communication hole 3b and the axis of the inlet port 11a does not change. As a result, even if the communication hole 3b is located within the inner diameter range of the opening of the inlet port 11a in the direction of the axis L, as shown in FIG. Since the fluid is not directly injected into the auxiliary valve chamber 3R, the inflow of fluid from the communication hole 3b into the sub-valve chamber 3R can be reduced. Therefore, the flow of fluid between the main valve body 3 and the main valve port 13a can be stabilized, the vibration of the main valve body 3 can be suppressed, and the generation of noise and vibration of the electric valve 100 can be suppressed.

第４実施形態において、図５の入口ポート１１ａ側の連通孔３ｂの中心軸線が入口ポート１１ａの中心軸線となす角度αは４５°以上９０°以下が好ましい。 In the fourth embodiment, the angle α between the central axis of the communication hole 3b on the side of the inlet port 11a in FIG. 5 and the central axis of the inlet port 11a is preferably 45° or more and 90° or less.

図６は本発明の実施形態の冷凍サイクルシステムを示す図であり、同図に基づいて実施形態の冷凍サイクルシステムについて説明する。冷凍サイクルシステムは、例えば、家庭用エアコン等の空気調和機に用いられる。前記実施形態の電動弁１００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おり、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及び電動弁１００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。 FIG. 6 is a diagram showing a refrigeration cycle system according to an embodiment of the present invention, and the refrigeration cycle system according to the embodiment will be explained based on the diagram. Refrigeration cycle systems are used, for example, in air conditioners such as household air conditioners. The motor-operated valve 100 of the embodiment is provided between the first indoor heat exchanger 91 (operates as a cooler during dehumidification) and the second indoor heat exchanger 92 (operates as a heater during dehumidification) of the air conditioner. The compressor 95, four-way valve 96, outdoor heat exchanger 94, and electronic expansion valve 93 constitute a heat pump refrigeration cycle. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the electric valve 100 are installed indoors, and the compressor 95, four-way valve 96, outdoor heat exchanger 94, and electronic expansion valve 93 are installed outdoors. They have heating and cooling equipment.

除湿弁としての実施形態の電動弁１００は、除湿時以外の冷房時または暖房時には主弁体が全開状態とされて、第１室内熱交換器９１と第２室内熱交換器９２は一つの室内熱交換器とされる。そして、この一体の室内熱交換器と室外熱交換器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、電子膨張弁としての電動弁９３は、蒸発器と凝縮器の間に設けられている。 In the electric valve 100 of the embodiment as a dehumidification valve, the main valve body is fully opened during cooling or heating other than during dehumidification, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are connected to one indoor heat exchanger. It is considered a heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 function alternatively as an "evaporator" and a "condenser." That is, the electric valve 93 as an electronic expansion valve is provided between the evaporator and the condenser.

なお、本発明は、前記実施形態に限定されるものではなく、本発明の目的が達成できる他の構成等を含み、以下に示すような変形等も本発明に含まれる。例えば、前記実施形態では、家庭用エアコン等の空気調和機に用いられる電動弁１００を例示したが、本発明の電動弁は、家庭用エアコンに限らず、業務用エアコンであってもよいし、空気調和機に限らず、各種の冷凍機等にも適用可能である。 Note that the present invention is not limited to the embodiments described above, and includes other configurations that can achieve the object of the present invention, and the present invention also includes the following modifications. For example, in the above embodiment, the electric valve 100 used in an air conditioner such as a domestic air conditioner is illustrated, but the electric valve of the present invention is not limited to a household air conditioner, but may be used in a commercial air conditioner. It is applicable not only to air conditioners but also to various types of refrigerators.

以上、本発明の実施の形態について図面を参照して詳述し、その他の実施形態についても詳述してきたが、具体的な構成はこれらの実施の形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計の変更等があっても本発明に含まれる。 The embodiments of the present invention have been described above in detail with reference to the drawings, and other embodiments have also been described in detail, but the specific configuration is not limited to these embodiments. Even if there are changes in the design within the scope of the invention, they are included in the present invention.

１ 弁ハウジング
１Ｒ 主弁室
１１ 第１継手管
１１ａ 入口ポート
１２ 第２継手管
１３ 主弁座
１３ａ 主弁ポート
Ｌ 軸線
２，２′，２″ ガイド部材
２Ａ ガイド孔
２２ 上部ガイド部
２５ 下部ガイド部
２３ ホルダ部
２３ａ 雌ねじ部
３ 主弁体
３１ 主弁部
３２ 保持部
３ａ 副弁ポート
３ｂ 連通孔
３Ａ 副弁室
４ 副弁体
４１ ガイド用ボス部
４２ ニードル弁
５ 駆動部
５Ａ ステッピングモータ
５Ｂ ねじ送り機構
５Ｃ ストッパ機構
５１ ロータ軸
５１ａ 雄ねじ部
５２ マグネットロータ
５３ ステータコイル
９１ 第１室内側熱交換器
９２ 第２室内側熱交換器
９３ 電子膨張弁
９４ 室外側熱交換器
９５ 圧縮機
９６ 四方弁
１００ 電動弁 1 Valve housing 1R Main valve chamber 11 First joint pipe 11a Inlet port 12 Second joint pipe 13 Main valve seat 13a Main valve port L Axis 2, 2', 2'' Guide member 2A Guide hole 22 Upper guide part 25 Lower guide part 23 Holder part 23a Female thread part 3 Main valve body 31 Main valve part 32 Holding part 3a Sub-valve port 3b Communication hole 3A Sub-valve chamber 4 Sub-valve body 41 Guide boss part 42 Needle valve 5 Drive part 5A Stepping motor 5B Screw feed mechanism 5C Stopper mechanism 51 Rotor shaft 51a Male thread 52 Magnet rotor 53 Stator coil 91 First indoor heat exchanger 92 Second indoor heat exchanger 93 Electronic expansion valve 94 Outdoor heat exchanger 95 Compressor 96 Four-way valve 100 Electric valve

Claims (5)

弁本体の主弁室内に設けられて該主弁室に開口する主弁ポートを開閉する主弁体と、前記主弁体に形成された副弁室内で該主弁体に形成された副弁ポートの軸線方向に移動して該副弁ポートの開度を制御する副弁体と、を備え、前記主弁体で前記主弁ポートを閉として前記副弁体で前記副弁ポートの開度を制御して流体を絞る小流量制御域と、前記主弁体で前記主弁ポートを全開として、前記主弁体の側部にて前記主弁室に開口する入口ポートから流入する流体を前記主弁ポートに流す大流量域と、を有する二段式の電動弁において、
前記主弁体に、前記主弁室から前記副弁室に連通する連通孔が設けられ、
前記連通孔は、前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が前記入口ポートの開口と直接対向しない位置に設けられ、
前記弁本体には、前記主弁体をガイドするガイド部材が設けられ、
前記主弁体の前記軸線方向における前記主弁ポート側と反対側の端部には、前記主弁体と別体に設けられたリテーナが結合され、
前記リテーナは、前記副弁体に係合可能に設けられ、
前記ガイド部材と前記リテーナとの間には、前記リテーナを介して前記主弁体を前記主弁ポート側に付勢する主弁ばねが設けられていることを特徴とする電動弁。 A main valve body that is provided in a main valve chamber of a valve body and opens and closes a main valve port that opens into the main valve chamber, and a sub-valve that is formed in the main valve body in a sub-valve chamber that is formed in the main valve body. a sub-valve element that moves in the axial direction of the port to control the opening degree of the sub-valve port, the main valve element closing the main valve port and the sub-valve element controlling the opening degree of the sub-valve port. a small flow rate control region that throttles the fluid by controlling the main valve body, and a small flow rate control region that controls the fluid flow by fully opening the main valve port with the main valve body, and controlling the fluid flowing in from the inlet port that opens into the main valve chamber at the side of the main valve body. In a two-stage electric valve that has a large flow area flowing to the main valve port,
The main valve body is provided with a communication hole that communicates from the main valve chamber to the auxiliary valve chamber,
The communication hole is provided at a position where at least one of the communication holes located on the inlet port side does not directly oppose the opening of the inlet port when the main valve body is fully opened;
The valve body is provided with a guide member that guides the main valve body,
A retainer provided separately from the main valve body is coupled to an end of the main valve body opposite to the main valve port side in the axial direction,
The retainer is provided so as to be engageable with the sub-valve body,
The motor-operated valve is characterized in that a main valve spring is provided between the guide member and the retainer to urge the main valve body toward the main valve port via the retainer. 前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が、前記主弁体をガイドするガイド部材の下部ガイド部内に位置することを特徴とする請求項１に記載の電動弁。 Claim 1, wherein when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located within a lower guide portion of a guide member that guides the main valve body. Electric valve described in. 前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔が、前記入口ポートの前記開口の前方から外れた位置にあることを特徴とする請求項１に記載の電動弁。 According to claim 1, when the main valve body is fully opened, at least one of the communication holes located on the inlet port side is located away from in front of the opening of the inlet port. electric valve. 前記主弁体の全開時において、前記連通孔のうち少なくとも前記入口ポート側に位置する連通孔の中心軸線と、前記入口ポートの中心軸線とが、前記主弁ポートの軸線Ｌに対し垂直な平面に投影したときに交差することを特徴とする請求項１に記載の電動弁。 When the main valve body is fully opened, a central axis of at least one of the communication holes located on the inlet port side and a central axis of the inlet port are in a plane perpendicular to the axis L of the main valve port. The motor-operated valve according to claim 1, wherein the motor-operated valve intersects when projected on. 圧縮機と、室内熱交換器と、室外熱交換器と、前記室内熱交換器と前記室外熱交換器との間に設けられた電子膨張弁と、前記室内熱交換器に設けられる除湿弁とを含む冷凍サイクルシステムであって、請求項１乃至４のいずれか一項に記載の電動弁が、前記除湿弁として用いられていることを特徴とする冷凍サイクルシステム。 A compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and a dehumidification valve provided in the indoor heat exchanger. A refrigeration cycle system comprising: the electric valve according to any one of claims 1 to 4 being used as the dehumidification valve.
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