JP7145134B2 - Electric valve and refrigeration cycle system - Google Patents

Electric valve and refrigeration cycle system Download PDF

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JP7145134B2
JP7145134B2 JP2019177469A JP2019177469A JP7145134B2 JP 7145134 B2 JP7145134 B2 JP 7145134B2 JP 2019177469 A JP2019177469 A JP 2019177469A JP 2019177469 A JP2019177469 A JP 2019177469A JP 7145134 B2 JP7145134 B2 JP 7145134B2
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valve
sub
port
main valve
valve port
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JP2021055711A (en
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亮司 小池
雄希 北見
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to JP2019177469A priority Critical patent/JP7145134B2/en
Priority to CN202010936759.6A priority patent/CN112576763B/en
Priority to CN202211557495.9A priority patent/CN115750908A/en
Publication of JP2021055711A publication Critical patent/JP2021055711A/en
Priority to JP2022147743A priority patent/JP7383774B2/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
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (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。 TECHNICAL FIELD The present invention relates to an electrically operated valve and a refrigeration cycle system used in a refrigeration cycle system and the like.

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制御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２０１９－１３２３４７号公報（特許文献１）に開示されている。 Conventionally, as an electric valve provided in the refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control region and a large flow rate control region. Such an electrically operated valve has applications (for example, a dehumidification valve) mounted on an indoor unit, and is disclosed in Japanese Patent Laying-Open No. 2019-132347 (Patent Document 1), for example.

特開２０１９－１３２３４７号公報JP 2019-132347 A

近年、業務用及び家庭用の空気調和機においては、極めて高い静音性が求められている。小流量制御域は例えば除湿運転を行うものであり、特にこの小流量制御域において、副弁ポートとニードル弁との間の絞り部を通過する冷媒通過音を低減することが要求される。 In recent years, commercial and domestic air conditioners are required to be extremely quiet. In the small flow rate control region, for example, dehumidification operation is performed, and especially in this small flow control region, it is required to reduce the sound of the refrigerant passing through the throttle portion between the auxiliary valve port and the needle valve.

本発明は、ニードル部が弁ポートの周囲の弁座に着座しないよう構成された電動弁において、第１絞り部の冷媒通過音を低減することを課題とする。 SUMMARY OF THE INVENTION An object of the present invention is to reduce the sound of refrigerant passing through a first throttle in a motor-operated valve in which a needle portion is not seated on a valve seat around a valve port.

本発明の電動弁は、弁室の流体を弁ポートを介して下流側に流出させるとともに、駆動部のロータの回転により回転するニードル部を弁ポートの軸線方向に進退させて該弁ポートを流れる流体の流量を制御する電動弁であって、前記ニードル部が前記弁ポートの周囲の弁座に着座しないよう構成された電動弁において、前記ニードル部と前記弁ポートとの隙間からなる第１絞り部と、前記弁室と前記下流側との間に設けられた第２絞り部と、を備え、前記第２絞り部は、前記弁ポートに形成された複数の溝であり、当該複数の溝それぞれの軸線方向の長さは前記弁ポートの軸線方向の長さより短く形成されていることを特徴とする。 The motor-operated valve of the present invention causes the fluid in the valve chamber to flow downstream through the valve port, and moves the needle portion, which is rotated by the rotation of the rotor of the driving portion, back and forth in the axial direction of the valve port to flow through the valve port. A motor-operated valve for controlling the flow rate of a fluid, the motor-operated valve configured so that the needle portion does not sit on a valve seat around the valve port, wherein a first throttle formed by a gap between the needle portion and the valve port and a second throttle portion provided between the valve chamber and the downstream side , wherein the second throttle portion is a plurality of grooves formed in the valve port, and the plurality of grooves The length in the axial direction of each valve port is shorter than the length in the axial direction of the valve port .

この際、主弁座の主弁ポートを開閉する主弁体と、前記主弁体に設けられた前記弁座としての副弁座と、前記弁ポートとしての副弁ポートと、前記副弁ポートの開度を変更する前記ニードル部としての副弁体と、を備え、前記主弁体が前記主弁ポートを閉とした状態で、前記副弁体が前記副弁ポートの開度を変更する小流量制御域と、前記主弁体が前記主弁ポートを全開状態として、前記主弁ポートから大流量の流体を流す大流量制御域と、の二段の流量制御域を有することを特徴とする電動弁が好ましい。 At this time, a main valve body for opening and closing a main valve port of the main valve seat, a sub-valve seat as the valve seat provided on the main valve body, a sub-valve port as the valve port, and the sub-valve port and a sub-valve body as the needle portion that changes the opening degree of the sub-valve port, wherein the sub-valve body changes the opening degree of the sub-valve port in a state where the main valve body closes the main valve port. characterized by having a two-step flow control region, a small flow control region and a large flow control region in which the main valve body fully opens the main valve port and causes a large flow of fluid to flow from the main valve port. A motor operated valve is preferred.

また、前記第２絞り部が、前記副弁座に形成されていることを特徴とする電動弁が好ましい。また、他の電動弁として、前記第２絞り部が、前記副弁座または前記副弁体に形成されていることとしてもよい。 Further, it is preferable that the motor-operated valve is characterized in that the second throttle portion is formed on the auxiliary valve seat. Further, as another electrically operated valve, the second throttle portion may be formed on the sub-valve seat or the sub-valve body.

また、前記第２絞り部が、前記主弁座に形成されていることを特徴とする電動弁が好ましい。また、他の電動弁として、前記第２絞り部が、前記主弁座または前記主弁体に形成されていることとしてもよい。 Further, it is preferable that the motor-operated valve is characterized in that the second throttle portion is formed on the main valve seat. Further, as another electrically operated valve, the second throttle portion may be formed on the main valve seat or the main valve body.

また、前記第２絞り部が、前記副弁座の前記副弁ポートの副弁室側の開口縁に形成されていることを特徴とする電動弁が好ましい。 Further, it is preferable that the motor-operated valve is characterized in that the second throttle portion is formed at the opening edge of the sub-valve port of the sub-valve seat on the side of the sub-valve chamber.

また、前記第２絞り部が、前記主弁座の前記主弁ポートの主弁室側の開口縁に形成されていることを特徴とする電動弁が好ましい。 Further, it is preferable that the motor-operated valve is characterized in that the second throttle portion is formed at the opening edge of the main valve port of the main valve seat on the main valve chamber side.

また、他の電動弁として、前記第２絞り部が、前記副弁体の前記副弁ポートに対向する部位にて前記軸線周りに複数形成されていることとしてもよい。 Further, as another electrically operated valve, a plurality of the second throttle portions may be formed around the axis at a portion of the sub-valve element facing the sub-valve port.

また、他の電動弁として、前記第２絞り部が、前記主弁体の前記主弁ポートに対向する部位にて前記軸線周りに複数形成されていることとしてもよい。 Further , as another electric valve, a plurality of the second throttle portions may be formed around the axis at a portion of the main valve body facing the main valve port.

また、前記第２絞り部が、前記副弁座の副弁側と、前記主弁座の主弁側の少なくとも一方に形成されていることを特徴とする電動弁が好ましい。 Further, it is preferable that the motor-operated valve is characterized in that the second throttle portion is formed on at least one of the sub-valve side of the sub-valve seat and the main valve side of the main valve seat .

また、他の電動弁として、前記第２絞り部が、孔により構成されていることとしてもよい。 Moreover, as another electric valve, the second throttle portion may be configured by a hole .

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。 A 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 A refrigeration cycle system including a dehumidification valve provided in an exchanger, wherein the motor operated 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、ニードル部が弁ポートの周囲の弁座に着座しないよう構成された電動弁において、例えば二段の流量制御域を有する電動弁の特に小流量制御域での第１絞り部の冷媒通過音を低減することができる。 According to the motor-operated valve and refrigerating cycle system of the present invention, in the motor-operated valve configured so that the needle portion does not sit on the valve seat around the valve port, for example, the motor-operated valve having two-stage flow control regions, especially the small flow rate control It is possible to reduce the sound of the refrigerant passing through the first throttle portion in the region.

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. 4 is a vertical cross-sectional view of the motor operated 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主弁体の全開状態で運転停止時、または冷房運転時の縦断面図である。FIG. 4 is a vertical cross-sectional view of the motor-operated valve of the first embodiment when the main valve body is fully open and the operation is stopped or when the cooling operation is performed; 第１実施形態の電動弁の副弁座及び副弁ポートの拡大縦断面図及び拡大平面断面図である。4A and 4B are an enlarged vertical cross-sectional view and an enlarged plan cross-sectional view of the sub-valve seat and sub-valve port of the motor-operated valve of the first embodiment; 第１実施形態の電動弁の小流量制御域状態でのニードル部と副弁ポートの拡大図である。FIG. 4 is an enlarged view of a needle portion and a sub-valve port of the motor-operated valve of the first embodiment in a small flow rate control region state; 第１実施形態の変形例１を示す図である。It is a figure which shows the modification 1 of 1st Embodiment. 第１実施形態の変形例２を示す図である。It is a figure which shows the modification 2 of 1st Embodiment. 本発明の第２実施形態を示す図である。FIG. 5 is a diagram showing a second embodiment of the present invention; 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。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows the refrigerating-cycle system of embodiment of this invention.

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主弁体の全開状態で運転停止時、または冷房運転時の縦断面図、図３は第１実施形態の電動弁の副弁座及び副弁ポートの拡大縦断面図（図３（Ａ））及び拡大平面断面図（図３（Ｂ））、図４は第１実施形態の電動弁の小流量制御域状態でのニードル部と副弁ポートの拡大図である。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。また、図１及び図２では副弁座及副弁ポートの詳細構造は省略してある。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、ニードル弁４と、駆動部５と、を備えている。 Next, an embodiment of an electrically operated valve and a refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the motor-operated valve of the first embodiment in a small flow rate control region state, and FIG. 2 is a longitudinal section of the motor-operated valve of the first embodiment when the main valve body is fully open and the operation is stopped or cooling operation is performed. 3 is an enlarged longitudinal sectional view (FIG. 3(A)) and an enlarged plan sectional view (FIG. 3(B)) of the sub-valve seat and sub-valve port of the motor-operated valve of the first embodiment; FIG. FIG. 4 is an enlarged view of the needle portion and the sub-valve port of the motor-operated valve of the embodiment in the small flow rate control region state; It should be noted that the concept of "up and down" in the following description corresponds to up and down in the drawings of FIGS. 1 and 2. FIG. 1 and 2, detailed structures of the sub-valve seat and the sub-valve port are omitted. This electrically operated valve 100 includes a valve housing 1 , a guide member 2 , a main valve body 3 , a needle valve 4 and a driving portion 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側には円筒状の主弁座１３が形成され、この主弁座１３の内側は主弁ポート１３ａとなっており、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。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）である。なお、第１継手管１１及び第２継手管１２は、弁ハウジング１に対してろう付け等により固着されている。 The valve housing 1 is made of, for example, brass, stainless steel, or the like and has a substantially cylindrical shape, and has a main valve chamber 1R inside. 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 that extends downward from the lower end. A cylindrical 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 inner side of the main valve seat 13 serves as a main valve port 13a. The pipe 12 is connected to the main valve chamber 1R through the main valve port 13a. The main valve port 13a is a cylindrical through-hole (through-hole) centered on the axis L. As shown in FIG. The first joint pipe 11 and the second joint pipe 12 are fixed to the valve housing 1 by brazing or the like.

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より小径で圧入部２１の上下に位置する略円柱状のガイド部２２，２３と、上側のガイド部２２の上部に延設されたホルダ部２４と、圧入部２１の外周に設けられたリング状のフランジ部２５とを有している。圧入部２１、ガイド部２２，２３、ホルダ部２４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２５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２５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 the opening at the upper end of the valve housing 1 . The guide member 2 includes a press-fitting portion 21 press-fitted into the inner peripheral surface of the valve housing 1, substantially cylindrical guide portions 22 and 23 having a smaller diameter than the press-fitting portion 21 and positioned above and below the press-fitting portion 21, and upper guides. It has a holder portion 24 extending from the upper portion of the portion 22 and a ring-shaped flange portion 25 provided on the outer periphery of the press-fitting portion 21 . The press-fitting portion 21, the guide portions 22 and 23, and the holder portion 24 are configured as an integrated product made of resin. Further, the flange portion 25 is, for example, a metal plate such as brass or stainless steel, and the flange portion 25 is provided integrally with the press-fitting portion 21 made of resin 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２５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及び上下のガイド部２２，２３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２４の中心には、ガイド孔２Ａと同軸の雌ねじ部２４ａとそのねじ孔が形成されている。そして、下側のガイド部２３の内側でガイド孔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 the press-fitting portion 21 and fixed to the upper end portion of the valve housing 1 via the flange portion 25 by welding. In the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the press-fit portion 21 and the upper and lower guide portions 22 and 23. A female threaded portion 24a coaxial with and a threaded hole thereof are formed. The main valve body 3 is arranged inside the guide hole 2A inside the guide portion 23 on the lower side.

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、円柱状のニードルガイド孔３２ａを有する保持部３２と、ニードルガイド孔３２ａの底部を構成する副弁座３３と、保持部３２の端部に設けられたリテーナ３４と、を有している。なお、ニードルガイド孔３２ａの下側一部は副弁室３Ｒとなっている。保持部３２のニードルガイド孔３２ａ内には、後述のロータ軸５１に取り付けられたワッシャ４３とロータ軸５１と一体に形成されたガイド用ボス部４４とが挿通されるとともに、リング状のリテーナ３４は保持部３２の上端に嵌合固着または溶接等により固着されている。 The main valve body 3 includes a main valve portion 31 that is seated and separated from the main valve seat 13, a holding portion 32 that has a cylindrical needle guide hole 32a, and a sub valve seat that constitutes the bottom of the needle guide hole 32a. 33 and a retainer 34 provided at the end of the holding portion 32 . A part of the lower side of the needle guide hole 32a serves as an auxiliary valve chamber 3R. A washer 43 attached to a rotor shaft 51, which will be described later, and a guide boss portion 44 formed integrally with the rotor shaft 51 are inserted into the needle guide hole 32a of the holding portion 32. is fixed to the upper end of the holding portion 32 by fitting or welding.

また、リテーナ３４とガイド孔２Ａの上端部との間には、主弁ばね３ａが配設されており、この主弁ばね３ａ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。副弁座３３の中心には軸線Ｌを中心とする円筒形状の副弁ポート３３ａが形成されている。また、保持部３２の側面の少なくとも一箇所には、副弁室３Ｒと主弁室１Ｒとを導通する導通孔３２ｂが形成されており、副弁体としてのニードル弁４が副弁ポート３３ａを開状態としたとき、主弁室１Ｒ、副弁室３Ｒ、副弁ポート３３ａ及び主弁ポート１３ａが導通する。 A main valve spring 3a is arranged between the retainer 34 and the upper end of the guide hole 2A. energized. A cylindrical sub-valve port 33a centered on the axis L is formed at the center of the sub-valve seat 33 . At least one side surface of the holding portion 32 is formed with a communication hole 32b that connects the sub-valve chamber 3R and the main valve chamber 1R. When opened, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a and the main valve port 13a are electrically connected.

ニードル弁４は、後述のロータ軸５１の下端部にこのロータ軸５１と一体に形成されてロータ軸５１側に連なる先端に向かって徐々に径が小さくなる円錐台状の「副弁体」としてのニードル部４２とを一体に形成して備えている。また、ニードル弁４は、ロータ軸５１に取り付けられた潤滑性樹脂からなる円環状のワッシャ４３と、ロータ軸５１と一体に形成されたガイド用ボス部４４と、を有している。そして、ワッシャ４３とガイド用ボス部４４は、ニードルガイド孔３２ａ内に摺動可能に挿通されている。 The needle valve 4 is formed integrally with the rotor shaft 51 at the lower end of the rotor shaft 51, which will be described later. and a needle portion 42 are integrally formed. The needle valve 4 also has an annular washer 43 made of lubricating resin attached to the rotor shaft 51 and a guide boss portion 44 integrally formed with the rotor shaft 51 . The washer 43 and the guide boss portion 44 are slidably inserted into the needle guide hole 32a.

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の回転によりニードル弁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 hermetically fixed to the upper end of the valve housing 1 by welding or the like. The drive unit 5 includes a stepping motor 5A, a screw feed mechanism 5B that advances and retracts the needle valve 4 by rotation of the stepping motor 5A, and a stopper mechanism 5C that restricts rotation of the stepping motor 5A.

そして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。 The stepping motor 5A includes a rotor shaft 51, a magnet rotor 52 rotatably disposed inside the case 14, a stator coil 53 opposed to the magnet rotor 52 on the outer periphery of the case 14, and others. It is composed of a yoke, an exterior member, and the like (not shown). 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 circumference 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. As shown in FIG. The female threaded portion 24a of the guide member 2 and the male threaded portion 51a of the rotor shaft 51 constitute a screw feed mechanism 5B.

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、ニードル弁４が軸線Ｌ方向に進退移動してニードル弁４が副弁ポート３３ａに対して近接又は離間する。また、ニードル弁４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はニードル弁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 are rotated. At the same time, the rotor shaft 51 moves in the axis L direction. Then, the needle valve 4 advances and retreats in the direction of the axis L, and the needle valve 4 approaches or separates from the sub-valve port 33a. Also, when the needle valve 4 rises, the washer 43 engages the retainer 34 of the main valve body 3 , and the main valve body 3 moves together with the needle valve 4 to separate from the main valve seat 13 . A projection 52a is formed on the magnet rotor 52, and as the magnet rotor 52 rotates, the projection 52a operates the rotation stopper mechanism 5C, and the rotor shaft 51 (and the magnet rotor 52) is positioned at the lowest end and The uppermost position is regulated.

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、ニードル弁４により副弁ポート３３ａの開度が制御され、小流量の制御が行われる。また、例えば冷凍サイクルシステムの圧縮機が停止して流体（冷媒）が停止した状態で、ニードル弁４と主弁体３が上昇されると、図２のように主弁ポート１３ａが全開状態となる。これにより、冷房運転時、第１継手管１１から第２継手管１２へ大流量の流体（冷媒）が流されたり、暖房運転時、第２継手管１２から第１継手管１１へ大流量の流体（冷媒）が流される。 1, the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the opening of the sub-valve port 33a is controlled by the needle valve 4. is controlled. Further, for example, when the compressor of the refrigeration cycle system is stopped and the fluid (refrigerant) is stopped, and the needle valve 4 and the main valve body 3 are raised, the main valve port 13a is fully opened as shown in FIG. Become. As a result, a large amount of fluid (refrigerant) flows from the first joint pipe 11 to the second joint pipe 12 during cooling operation, and a large amount of fluid (refrigerant) flows from the second joint pipe 12 to the first joint pipe 11 during heating operation. A fluid (refrigerant) is caused to flow.

図３に示すように、副弁ポート３３ａの副弁室３Ｒ側の開口縁には、複数（この例では６個）の「第２絞り部」としての溝６が形成されている。この溝６は、軸線Ｌ周りで等間隔（６０°毎）となる軸線Ｌに対して回転対称な位置に形成されている。また、溝６の軸線Ｌ方向の長さは、副弁ポート３３ａの軸線Ｌ方向の長さより短く形成されており、また、溝６の流れ方向上流側の副弁室３Ｒから軸線Ｌ方向の第２継手管側に向かう程、溝６の水平断面積が徐々に減少する様に形成されている。また、図４に示すように、ニードル部４２は、軸線Ｌを中心線とする円柱からなるストレート部４２ａと、先端側にかけて縮径されたテーパ部４２ｂとから構成されている。また、ストレート部４２ａの外径は、副弁ポート３３ａの内径より小さくなっており、ストレート部４２ａと副弁ポート３３ａとの間には第１絞り部（隙間）が形成される。そして、この第１絞り部を一定流量の冷媒が流れることにより小流量制御が行われる。また、この小流量制御のとき、ストレート部４２ａと副弁ポート３３ａの絞り部に流れ込む冷媒の圧力は、副弁ポート３３ａの副弁室３Ｒ側に形成された溝６（第２絞り部）により軸線Ｌ周りに分散され、副弁座３３とニードル部４２とで構成される第１絞り部の前後の差圧が減少し、この第１絞り部での冷媒通過音を低減することができる。 As shown in FIG. 3, a plurality (six in this example) of grooves 6 as "second throttle portions" are formed in the opening edge of the sub-valve port 33a on the side of the sub-valve chamber 3R. The grooves 6 are formed at positions rotationally symmetrical with respect to the axis L at equal intervals (every 60°) around the axis L. As shown in FIG. The length of the groove 6 in the direction of the axis L is shorter than the length of the sub-valve port 33a in the direction of the axis L. Further, the length of the groove 6 in the direction of the axis L is formed to be shorter than the length of the sub-valve port 33a in the direction of the axis L. The horizontal cross-sectional area of the groove 6 is formed so as to gradually decrease toward the second joint pipe side. Further, as shown in FIG. 4, the needle portion 42 is composed of a straight portion 42a formed of a column centered on the axis L, and a tapered portion 42b having a reduced diameter toward the distal end side. Further, the outer diameter of the straight portion 42a is smaller than the inner diameter of the sub-valve port 33a, and a first throttle portion (gap) is formed between the straight portion 42a and the sub-valve port 33a. A small flow rate control is performed by causing a constant flow rate of the refrigerant to flow through the first throttle portion. During this small flow rate control, the pressure of the refrigerant flowing into the straight portion 42a and the throttle portion of the sub-valve port 33a is controlled by the groove 6 (second throttle portion) formed on the sub-valve chamber 3R side of the sub-valve port 33a. The differential pressure before and after the first throttle portion, which is dispersed around the axis L and is composed of the sub valve seat 33 and the needle portion 42, is reduced, and the noise of the refrigerant passing through the first throttle portion can be reduced.

このように、第１実施形態の電動弁１００は、小流量制御域で作用する副弁座３３とニードル弁４（副弁体のニードル部４２）との冷媒が流れる第１絞り部に連続する溝６（第２絞り部）が、副弁座３３に形成されている。したがって、副弁ポート３３ａとニードル部４２との間の第１絞り部を通過する冷媒通過音を低減できる。 Thus, in the motor operated valve 100 of the first embodiment, the sub-valve seat 33 and the needle valve 4 (needle portion 42 of the sub-valve body), which act in the small flow rate control region, are connected to the first throttle portion through which the refrigerant flows. A groove 6 (second throttle portion) is formed in the sub valve seat 33 . Therefore, the sound of the refrigerant passing through the first throttle portion between the sub-valve port 33a and the needle portion 42 can be reduced.

図５乃至図７は第１実施形態の電動弁の変形例及び第２実施形態を示す図であり、各変形例及び第２実施形態において電動弁の全体構成は図５乃至図７部位以外は図１及び図２と同様である。 5 to 7 are diagrams showing a modification of the motor operated valve of the first embodiment and a second embodiment. In each of the modifications and the second embodiment, the overall structure of the motor operated valve is Similar to FIGS. 1 and 2. FIG.

図５の変形例１は、ニードル部４２に「第２絞り部」としての溝７を形成したものである。溝７は、ニードル部４２の前記ガイド用ボス部４４側の付け根部４２ｃからストレート部４２ａの中ほどまで形成したものである。また、この溝７は複数（この例では６個）形成され、この溝７は、軸線Ｌ周りで等間隔（６０°毎）となる軸線Ｌに対して回転対称な位置に形成されている。さらに、溝７の水平断面の面積は軸線Ｌ方向で副弁ポート３３ａに近づくにしたがって小さくなっている。この変形例１では、溝７はストレート部４２ａの中ほどまでしか形成されていないので、ストレート部４２ａと副弁ポート３３ａとの絞り部の開口面積は実施形態と同様に一定であり、小流量制御のときの流量を一定に保つことができる。 In Modification 1 of FIG. 5, a groove 7 is formed in the needle portion 42 as a "second constricted portion". The groove 7 is formed from the root portion 42c of the needle portion 42 on the guide boss portion 44 side to the middle of the straight portion 42a. A plurality of grooves 7 (six in this example) are formed, and the grooves 7 are formed at positions rotationally symmetrical about the axis L at equal intervals (every 60°) around the axis L. As shown in FIG. Furthermore, the horizontal cross-sectional area of the groove 7 decreases in the direction of the axis L as it approaches the auxiliary valve port 33a. In this modified example 1, the groove 7 is formed only to the middle of the straight portion 42a, so the opening area of the narrowed portion between the straight portion 42a and the sub-valve port 33a is constant as in the embodiment, and the flow rate is small. The flow rate during control can be kept constant.

そして、この変形例１でも、小流量制御のとき、ストレート部４２ａと副弁ポート３３ａの絞り部に流れ込む冷媒の圧力は、ニードル部４２に形成された溝７より軸線Ｌ周りに分散され、副弁座３３とニードル部４２とで構成される絞り部の前後の差圧が減少し、この絞り部での冷媒通過音を低減することができる。 Also in Modification 1, when the small flow rate is controlled, the pressure of the refrigerant flowing into the straight portion 42a and the constricted portion of the auxiliary valve port 33a is dispersed around the axis L by the groove 7 formed in the needle portion 42, The differential pressure across the throttle portion formed by the valve seat 33 and the needle portion 42 is reduced, and the sound of the refrigerant passing through the throttle portion can be reduced.

図６の変形例２は、ニードル部４２に「第２絞り部」としての溝７′を形成したものである。溝７′は、ニードル部４２のストレート部４２ａの中ほどから、テーパ部４２ｂまで形成したものである。また、この溝７′は複数（この例では６個）形成され、この溝７′は、軸線Ｌ周りで等間隔（６０°毎）となる軸線Ｌに対して回転対称な位置に形成されている。この変形例２でも、小流量制御のとき、ストレート部４２ａと副弁ポート３３ａの絞り部に流れ込む冷媒の圧力は、ニードル部４２に形成された溝７′より軸線Ｌ周りに分散され、副弁座３３とニードル部４２とで構成される絞り部の前後の差圧が減少し、この絞り部での冷媒通過音を低減することができる。 Modification 2 of FIG. 6 is obtained by forming a groove 7' in the needle portion 42 as a "second constricted portion". The groove 7' is formed from the middle of the straight portion 42a of the needle portion 42 to the tapered portion 42b. A plurality of grooves 7' (six in this example) are formed, and the grooves 7' are formed at equal intervals (every 60°) around the axis L and are rotationally symmetrical with respect to the axis L. there is In this modified example 2 as well, when the small flow rate is controlled, the pressure of the refrigerant flowing into the straight portion 42a and the constricted portion of the sub-valve port 33a is dispersed around the axis L by the groove 7' formed in the needle portion 42, The differential pressure before and after the throttle portion formed by the seat 33 and the needle portion 42 is reduced, and the sound of the refrigerant passing through the throttle portion can be reduced.

図７の第２実施形態は、図１及び図２の第１実施形態における主弁座１３や主弁ポート１３ａに特徴を持たせたものである。図７（Ａ）の第２実施形態の変形例１は、主弁座１３において主弁ポート１３ａの開口縁に複数（この例では６個）の「第２絞り部」としての溝８を形成したものである。第１実施形態と同様に、溝８も軸線Ｌ周りで等間隔（６０°毎）となる軸線Ｌに対して回転対称な位置に形成されている。溝８は、副弁ポート３３ａとニードル部４２のストレート部４２ａとの絞り部により小流量制御が行われるときにも、この溝８により主弁室１Ｒから主弁ポート１３ａに冷媒を流す作用をする。したがって、副弁ポート３３ａとニードル部４２との絞り部の前後の差圧が減少し、この絞り部での冷媒通過音を低減することができる。図７（Ｂ）の第２実施形態の変形例２は主弁３の主弁部３１において複数（この例では６個）の「第２絞り部」としての溝８′を形成したものである。第１実施形態と同様に、溝８′も軸線Ｌ周りで等間隔（６０°毎）となる軸線Ｌに対して回転対称な位置に形成されている。溝８′は、副弁ポート３３ａとニードル部４２のストレート部４２ａとの絞り部により小流量制御が行われるときにも、この溝８′により主弁室１Ｒから主弁ポート１３ａに冷媒を流す作用をする。したがって、副弁ポート３３ａとニードル部４２との絞り部の前後の差圧が減少し、この絞り部での冷媒通過音を低減することができる。 The second embodiment shown in FIG. 7 is characterized by the main valve seat 13 and the main valve port 13a in the first embodiment shown in FIGS. Modification 1 of the second embodiment shown in FIG. 7(A) forms a plurality of (six in this example) grooves 8 as "second throttle sections" on the opening edge of the main valve port 13a in the main valve seat 13. It is what I did. As in the first embodiment, the grooves 8 are also formed at equal intervals (every 60°) around the axis L and are rotationally symmetrical with respect to the axis L. As shown in FIG. The groove 8 allows the refrigerant to flow from the main valve chamber 1R to the main valve port 13a even when small flow rate control is performed by the narrowed portion formed by the sub-valve port 33a and the straight portion 42a of the needle portion 42. do. Therefore, the differential pressure between the sub-valve port 33a and the needle portion 42 before and after the throttle portion is reduced, and the refrigerant passage noise at the throttle portion can be reduced. A modification 2 of the second embodiment shown in FIG. 7(B) has a plurality (six in this example) of grooves 8' as "second throttle sections" in the main valve portion 31 of the main valve 3. . As in the first embodiment, the grooves 8' are also formed at equal intervals (every 60°) around the axis L and are rotationally symmetrical with respect to the axis L. As shown in FIG. The groove 8' allows the refrigerant to flow from the main valve chamber 1R to the main valve port 13a even when small flow rate control is performed by the throttle portion between the sub-valve port 33a and the straight portion 42a of the needle portion 42. act. Therefore, the differential pressure between the sub-valve port 33a and the needle portion 42 before and after the throttle portion is reduced, and the refrigerant passage noise at the throttle portion can be reduced.

次に、図８に基づいて本発明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。 Next, the refrigerating cycle system of the present invention will be described based on FIG. Refrigerating cycle systems are used, for example, in air conditioners such as domestic air conditioners. The motor-operated valve 100 of the above embodiment is installed between the first indoor heat exchanger 91 (operating as a cooler during dehumidification) and the second indoor heat exchanger 92 (operating as a heater during dehumidification) of the air conditioner. A heat pump refrigerating cycle is formed together with a compressor 95, a four-way valve 96, an outdoor heat exchanger 94 and an electronic expansion valve 93. The first indoor heat exchanger 91, the second indoor heat exchanger 92, and the motor-operated valve 100 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 outdoors. They make up the heating and cooling system.

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 motor-operated valve 100 of the embodiment as a dehumidification valve, the main valve body is in a fully open state 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. 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。 It should be noted that the present invention is not limited to the above-described embodiments, but includes other configurations and the like that can achieve the object of the present invention, and the following modifications and the like are also included in the present invention. For example, in the above-described embodiment, the motor-operated valve 100 used in an air conditioner such as a domestic air conditioner was exemplified, but the motor-operated valve of the present invention is not limited to a domestic air conditioner, and may be a commercial air conditioner. It is applicable not only to air conditioners but also to various types of refrigerators.

また、実施形態における「第２絞り部」としての溝６，７，７′，８，８′は断面が三角形であるが、断面が四角形の溝や断面が円形の溝であってもよい。また、前記の各実施形態において、「第２絞り部」としての溝は等間隔と記述したが、等間隔に限られるものではなく、第１継手管１１から第２継手管１２への横から下への流体の流れによる影響等に対応する為、非等間隔の複数溝を形成してもよい。また、前記の各実施形態において、溝は６個の例で示したが、６箇所に限定するものではなく、１箇所でも、６箇所以外の複数（２箇所以上）でもよい。 Further, although the grooves 6, 7, 7', 8, 8' as the "second throttle portions" in the embodiment have a triangular cross section, they may have a square cross section or a circular cross section. In each of the above-described embodiments, the grooves as the "second constricted portion" were described as being at equal intervals, but the grooves are not limited to being at equal intervals. A plurality of grooves may be formed at non-equidistant intervals in order to cope with the influence of downward fluid flow. In each of the above embodiments, the number of grooves is six, but the number of grooves is not limited to six, and may be one or a plurality other than six (two or more).

なお、第１実施形態では副弁体に対する副弁座に溝を形成したものとし、第２実施形態では主弁座に溝を形成したものとし、主弁座と副弁座について別々に溝を形成する例を挙げたが、第１実施形態と第２実施形態を複合して、副弁座に溝を形成してさらに主弁座に溝を形成した構成の実施形態としてもよい。また、変形例として、副弁座に溝を形成し、さらに主弁体に溝を形成した構成の実施形態としてもよい。さらに、副弁体に溝を形成し、主弁体に溝を形成した構成の実施形態としてもよい。さらに、副弁体に溝を形成し、主弁座に溝を形成した構成の実施形態としてもよい。 また、第２実施形態では、主弁体又は、主弁座に溝を形成する構成として記載したが、溝に限定するものではなく、孔などによる「第２絞り部」でもよい。 In the first embodiment, the groove is formed in the sub-valve seat for the sub-valve element, and in the second embodiment, the groove is formed in the main valve seat. Although an example of forming a groove has been given, the first embodiment and the second embodiment may be combined to form an embodiment in which a groove is formed in the sub-valve seat and a groove is further formed in the main valve seat. As a modification, an embodiment may be adopted in which a groove is formed in the sub-valve seat and a groove is further formed in the main valve body. Furthermore, an embodiment may be adopted in which a groove is formed in the sub valve body and a groove is formed in the main valve body. Furthermore, an embodiment may be adopted in which a groove is formed in the sub valve body and a groove is formed in the main valve seat. Further, in the second embodiment, the groove is formed in the main valve body or the main valve seat.

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。 As described above, the embodiments of the present invention have been described in detail with reference to the drawings, and other embodiments have also been described in detail. Even if there is a change in design without departing from the gist of the invention, it is included in the present invention.

１ 弁ハウジング
１Ｒ 主弁室
１１ 第１継手管
１２ 第２継手管
１３ 主弁座
１３ａ 主弁ポート
１４ ケース
Ｌ 軸線
２ ガイド部材
３ 主弁体
３ａ 主弁ばね
３Ｒ 副弁室
３１ 主弁部
３２ 保持部
３２ａ ニードルガイド孔
３２ｂ 導通孔
３３ 副弁座
３３ａ 副弁ポート
４ ニードル弁
４２ ニードル部（副弁体）
４２ａ ストレート部
４３ ワッシャ
４４ ガイド用ボス部
５ 駆動部
６ 溝（切欠き部）
７ 溝（切欠き部）
７′ 溝（切欠き部）
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 12 second joint pipe 13 main valve seat 13a main valve port 14 case L axis 2 guide member 3 main valve body 3a main valve spring 3R sub-valve chamber 31 main valve portion 32 holding Portion 32a Needle guide hole 32b Conducive hole 33 Sub-valve seat 33a Sub-valve port 4 Needle valve 42 Needle portion (sub-valve element)
42a straight portion 43 washer 44 guide boss portion 5 drive portion 6 groove (notch portion)
7 groove (notch)
7' groove (notch)
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 (8)

弁室の流体を弁ポートを介して下流側に流出させるとともに、駆動部のロータの回転により回転するニードル部を弁ポートの軸線方向に進退させて該弁ポートを流れる流体の流量を制御する電動弁であって、前記ニードル部が前記弁ポートの周囲の弁座に着座しないよう構成された電動弁において、
前記ニードル部と前記弁ポートとの隙間からなる第１絞り部と、前記弁室と前記下流側との間に設けられた第２絞り部と、を備え、
前記第２絞り部は、前記弁ポートに形成された複数の溝であり、当該複数の溝それぞれの軸線方向の長さは前記弁ポートの軸線方向の長さより短く形成されていることを特徴とする電動弁。 The electric drive causes the fluid in the valve chamber to flow downstream through the valve port, and controls the flow rate of the fluid flowing through the valve port by advancing and retracting the needle portion, which is rotated by the rotation of the rotor of the drive unit, in the axial direction of the valve port. In an electrically operated valve, wherein the needle portion is configured so as not to be seated on the valve seat around the valve port,
a first throttle portion formed by a gap between the needle portion and the valve port; and a second throttle portion provided between the valve chamber and the downstream side ,
The second throttle portion is a plurality of grooves formed in the valve port, and the axial length of each of the plurality of grooves is shorter than the axial length of the valve port. motorized valve. 主弁座の主弁ポートを開閉する主弁体と、前記主弁体に設けられた前記弁座としての副弁座と、前記弁ポートとしての副弁ポートと、前記副弁ポートの開度を変更する前記ニードル部としての副弁体と、を備え、前記主弁体が前記主弁ポートを閉とした状態で、前記副弁体が前記副弁ポートの開度を変更する小流量制御域と、前記主弁体が前記主弁ポートを全開状態として、前記主弁ポートから大流量の流体を流す大流量制御域と、の二段の流量制御域を有することを特徴とする請求項１に記載の電動弁。 a main valve body that opens and closes a main valve port of the main valve seat, a sub-valve seat as the valve seat provided in the main valve body, a sub-valve port as the valve port, and an opening degree of the sub-valve port and a sub-valve element as the needle portion that changes the small flow rate control in which the sub-valve element changes the degree of opening of the sub-valve port in a state where the main valve element closes the main valve port. and a large flow rate control region in which the main valve body fully opens the main valve port and allows a large flow rate of fluid to flow from the main valve port. 1. The electric valve according to 1. 前記第２絞り部が、前記副弁座に形成されていることを特徴とする請求項２に記載の電動弁。 3. The motor-operated valve according to claim 2, wherein the second throttle portion is formed on the auxiliary valve seat . 前記第２絞り部が、前記主弁座に形成されていることを特徴とする請求項２に記載の電動弁。 3. The motor-operated valve according to claim 2, wherein the second throttle portion is formed on the main valve seat . 前記第２絞り部が、前記副弁座の前記副弁ポートの副弁室側の開口縁に形成されていることを特徴とする請求項３に記載の電動弁。 4. The motor-operated valve according to claim 3, wherein the second throttle portion is formed at an opening edge of the sub-valve port of the sub-valve seat on the side of the sub-valve chamber. 前記第２絞り部が、前記主弁座の前記主弁ポートの主弁室側の開口縁に形成されていることを特徴とする請求項４に記載の電動弁。 5. The motor-operated valve according to claim 4, wherein the second throttle portion is formed at the opening edge of the main valve port of the main valve seat on the main valve chamber side. 前記第２絞り部が、前記副弁座の副弁側と、前記主弁座の主弁側の少なくとも一方に形成されていることを特徴とする請求項２に記載の電動弁。 3. The motor-operated valve according to claim 2, wherein the second throttle portion is formed on at least one of the sub-valve side of the sub-valve seat and the main valve side of the main valve seat . 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７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 8. A refrigeration cycle system, wherein the motor-operated valve according to any one of claims 1 to 7 is used as the dehumidification valve.
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