JP7474892B2 - Motor-operated valve and refrigeration cycle system - Google Patents

Motor-operated valve and refrigeration cycle system Download PDF

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JP7474892B2
JP7474892B2 JP2023038527A JP2023038527A JP7474892B2 JP 7474892 B2 JP7474892 B2 JP 7474892B2 JP 2023038527 A JP2023038527 A JP 2023038527A JP 2023038527 A JP2023038527 A JP 2023038527A JP 7474892 B2 JP7474892 B2 JP 7474892B2
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valve
sub
main valve
valve body
main
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JP2023068024A (en
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雄希 北見
亮司 小池
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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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
    • 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
    • F16K1/36—Valve members
    • F16K1/38—Valve members of conical shape
    • 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
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F16K31/043—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves characterised by mechanical means between the motor and the valve, e.g. lost motion means reducing backlash, clutches, brakes or return means
    • 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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/04—Means in valves for absorbing fluid energy for decreasing pressure or noise level, the throttle being incorporated in the closure member
    • 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)
  • Lift Valve (AREA)
  • Electrically Driven Valve-Operating Means (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 electrically operated valve for use in a refrigeration cycle system 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, motorized valves that control flow rate in a small flow rate control range and a large flow rate control range are used in the refrigeration cycle of air conditioners. Such motorized valves are used in indoor units (e.g., dehumidification valves), and are disclosed, for example, in JP 2019-132347 A (Patent Document 1).

特開２０１９－１３２３４７号公報JP 2019-132347 A

この種の電動弁は、小流量制御域は例えば除湿運転を行うものであり、この小流量制御域では、主弁座の主弁ポートを主弁体で全閉状態とし、この主弁体に形成された副弁ポートとニードル弁（副弁体）との間の絞り部を冷媒が通過するように構成されている。しかし、一次側または二次側における冷媒流れの脈動などにより圧力変化や配管振動が生じ、主弁体が振動して小流量域の制御性が低下するという問題がある。 This type of motor-operated valve performs dehumidification operation in the low flow control range, for example. In this low flow control range, the main valve port of the main valve seat is fully closed by the main valve body, and the refrigerant passes through a throttle section between the sub-valve port formed on the main valve body and the needle valve (sub-valve body). However, there is a problem in that pressure changes and piping vibrations occur due to pulsation of the refrigerant flow on the primary or secondary side, causing the main valve body to vibrate and reducing controllability in the low flow range.

本発明は、主弁体を主弁座に着座状態とし、この主弁体と主弁座との間の絞り部や、主弁体に形成された副弁ポートとニードル弁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二段の流量制御域を有する電動弁において、小流量制御域での主弁体の振動を防止して、小流量域の制御性を向上させることを課題とする。 The present invention aims to prevent vibration of the main valve body in the small flow control range and improve controllability in the small flow control range in an electric valve having a two-stage flow control range in which the main valve body is seated on the main valve seat and the flow rate of the refrigerant is controlled in the small flow control range by a throttling section between the main valve body and the main valve seat, and by a throttling section between a sub-valve port formed on the main valve body and a needle valve.

本発明の電動弁は、弁ハウジングの主弁室内に設けられた主弁ポートの周縁に形成された主弁座と近接または離隔する主弁体を備えるとともに、前記主弁体の内部の副弁室内に設けられた副弁ポートの周縁に形成された副弁座と近接または離隔する副弁体とを備える二段式の電動弁であって、前記副弁体と、前記主弁体とは、互いに直接接触する当接部をそれぞれ備え、前記副弁体が、前記弁ハウジングの軸線を中心線とする円柱からなるストレート部を有し、前記ストレート部の外径は、前記副弁ポートの内径よりも小さく、前記主弁体が前記主弁座に着座するとともに前記ストレート部が前記副弁ポート内に位置することで前記副弁体と前記副弁ポートとの隙間からなる第１絞り部が形成された状態において、前記副弁体が前記当接部により前記主弁体と当接することで、前記副弁体が前記主弁体を前記主弁座に押し付けるよう構成されていることを特徴とする。 The motor-operated valve of the present invention is a two-stage motor-operated valve comprising a main valve body adjacent to or separated from a main valve seat formed on the periphery of a main valve port provided in a main valve chamber of a valve housing, and a sub-valve body adjacent to or separated from a sub-valve seat formed on the periphery of a sub-valve port provided in a sub-valve chamber inside the main valve body, the sub-valve body and the main valve body each have an abutment portion that directly contacts each other, the sub-valve body has a straight portion made of a cylinder with the axis of the valve housing as its center line, the outer diameter of the straight portion is smaller than the inner diameter of the sub-valve port, and the sub-valve body is configured such that when the main valve body is seated on the main valve seat and the straight portion is positioned within the sub-valve port to form a first throttling portion consisting of a gap between the sub-valve body and the sub-valve port, the sub-valve body abuts against the main valve body at the abutment portion, and the sub-valve body presses the main valve body against the main valve seat.

また、前記副弁体は、前記当接部と、ニードル部と、を備え、前記ニードル部は、前記ストレート部と、前記主弁ポート側に向かって縮径するとともに前記ストレート部の前記主弁ポート側に接続されるニードルと、を備えることを特徴とする電動弁が好ましい。 The motor-operated valve is preferably characterized in that the sub-valve body includes the abutment portion and a needle portion, and the needle portion includes the straight portion and a needle that narrows toward the main valve port side and is connected to the main valve port side of the straight portion.

この際、前記当接部より前記副弁ポート側に、前記主弁室と前記副弁室とを連通する導通孔が形成されることを特徴とする電動弁が好ましい。 In this case, it is preferable that the motor-operated valve is characterized in that a through hole that communicates between the main valve chamber and the auxiliary valve chamber is formed on the auxiliary valve port side of the abutment portion.

また、前記副弁体と前記主弁体との前記当接部は、少なくとも一方が段部であることを特徴とする電動弁が好ましい。 Furthermore, it is preferable that the motor-operated valve be characterized in that at least one of the contact portions between the sub-valve body and the main valve body is a step portion.

また、前記副弁体と前記主弁体との前記当接部は、一方が前記副弁ポートの軸線を中心軸とするテーパ部であり、他方が前記軸線を中心軸とする段部であることを特徴とする電動弁が好ましい。 In addition, the motor-operated valve is preferably characterized in that the abutment portion between the sub-valve body and the main valve body is a tapered portion having the axis of the sub-valve port as its central axis on one side, and a stepped portion having the axis as its central axis on the other side.

また、前記主弁座または前記主弁体に、または／および、前記副弁座または前記副弁体に第２の絞り部が形成されていることを特徴とする電動弁が好ましい。 Furthermore, it is preferable that the motor-operated valve is characterized in that a second throttle portion is formed in the main valve seat or the main valve body, and/or in the sub-valve seat or the sub-valve body.

また、前記第２の絞り部が、溝または孔により構成されていることを特徴とする電動弁が好ましい。 Furthermore, it is preferable that the second throttle portion is configured as a groove or 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。 The refrigeration cycle system of the present invention is a refrigeration cycle system including 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, characterized in that 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、副弁体と副弁ポートとの間の絞り部（隙間）による、または、主弁体と主弁座との間や副弁体と副弁座との間の絞り部による小流量制御の状態では、副弁体と主弁体との当接部（副弁体と主弁体の間にバネを介したものも含む）が当接し、副弁体が主弁体を主弁座に押し付けるので、主弁ポートでの流体の圧力変化や配管振動が生じても、主弁体が振動することなく、小流量域の制御性が向上する。 According to the motor-operated valve and refrigeration cycle system of the present invention, in a state of small flow rate control by the throttling portion (gap) between the sub-valve element and the sub-valve port, or by the throttling portion between the main valve element and the main valve seat, or between the sub-valve element and the sub-valve seat, the abutment portion between the sub-valve element and the main valve element (including the sub-valve element and the main valve element via a spring) abuts and the sub-valve element presses the main valve element against the main valve seat, so that even if a pressure change of the fluid at the main valve port or piping vibration occurs, the main valve element does not vibrate, and controllability in the small flow rate range is improved.

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 vertical cross-sectional view of the motor-operated valve of the first embodiment of the present invention in a small flow rate control range 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。1 is a vertical cross-sectional view of a main valve body of the motor-operated valve of the first embodiment in a fully open state when the valve is stopped or in a cooling operation. FIG. 第１実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 2 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the first embodiment in a small flow rate control range state. 第２実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 11 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the second embodiment in a small flow rate control range state. 第２実施形態における第２絞り部の実施例１及び実施例２を示す図である。13A and 13B are diagrams showing examples 1 and 2 of a second narrowing portion in the second embodiment. 第１及び第２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 an auxiliary valve port in a small flow rate control range state of the motor-operated valve of the first and second embodiments. 第１及び第２実施形態の変形例を示す図である。FIG. 13 is a diagram showing a modification of the first and second embodiments. 第３実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 11 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the third embodiment in a small flow rate control range state. 第４実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 13 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the fourth embodiment in a small flow rate control range state. 第５実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 13 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the fifth embodiment in a small flow rate control range state. 第６実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。FIG. 13 is an enlarged longitudinal sectional view of a main portion of the motor-operated valve of the sixth embodiment in a small flow rate control range state. 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.

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小流量制御域状態の要部拡大縦断面図である。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」としてのニードル弁４と、駆動部５と、を備えている。 Next, an embodiment of the motor-operated valve and 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 the small flow control range state, Fig. 2 is a vertical cross-sectional view of the motor-operated valve of the first embodiment in the fully open state of the main valve body when the operation is stopped or during cooling operation, and Fig. 3 is an enlarged vertical cross-sectional view of the main part of the motor-operated valve of the first embodiment in the small flow control range state. Note that the concepts of "upper and lower" in the following description correspond to the upper and lower in Figs. 1 and 2. This motor-operated valve 100 comprises a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "sub-valve body", and a drive unit 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 formed in a generally cylindrical shape from, for example, brass or stainless steel, and has a main valve chamber 1R inside. A first coupling pipe 11 that is connected to the main valve chamber 1R is connected to one side of the outer periphery of the valve housing 1, and a second coupling pipe 12 is connected to a cylindrical portion extending downward from the lower end. A cylindrical main valve seat 13 is formed on the main valve chamber 1R side of the second coupling pipe 12 of the valve housing 1, and the inside of this main valve seat 13 is a main valve port 13a, and the second coupling pipe 12 is connected to the main valve chamber 1R via the main valve port 13a. The main valve port 13a is a cylindrical through hole (through hole) centered on the axis L. The first coupling pipe 11 and the second coupling 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。なお、フランジ部２５には主弁室１Ｒと後述するケース１４内とを弁軸の軸線Ｌ方向に連通する孔（不図示）が設けられている。 A guide member 2 is attached to the opening at the upper end of the valve housing 1. The guide member 2 has a press-fit portion 21 that is press-fitted into the inner peripheral surface of the valve housing 1, approximately cylindrical guide portions 22, 23 that are smaller in diameter than the press-fit portion 21 and are located above and below the press-fit portion 21, a holder portion 24 that extends from the upper portion of the upper guide portion 22, and a ring-shaped flange portion 25 that is provided on the outer periphery of the press-fit portion 21. The press-fit portion 21, the guide portions 22, 23, and the holder portion 24 are configured as an integrated resin product. The flange portion 25 is a metal plate such as brass or stainless steel, and is formed integrally with the resin press-fit portion 21 by insert molding. The flange portion 25 has a hole (not shown) that communicates between the main valve chamber 1R and the inside of the case 14 described later in the direction of the axis L of the valve shaft.

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-fit portion 21, and is fixed to the upper end of the valve housing 1 by welding via the flange portion 25. In addition, 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, 23 of the guide member 2, and a female threaded portion 24a coaxial with the guide hole 2A and its threaded hole are formed in the center of the holder portion 24. The main valve body 3 is disposed inside the guide hole 2A inside the lower guide portion 23.

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。また、ニードルガイド孔３２ａの下側にはこのニードルガイド孔３２ａに連なる副弁室３Ｒとなっており、この副弁室３Ｒとニードルガイド孔３２ａとの境界に「当接部」としての段部３ａが形成されている。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ニードル弁４のガイド用ボス部４１とが挿通されている。なお、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 has a main valve portion 31 that seats and unseats on the main valve seat 13, a holding portion 32 having a cylindrical needle guide hole 32a, an auxiliary valve seat 33 that forms the bottom of the needle guide hole 32a, and a retainer 34 provided at the end of the holding portion 32. In addition, below the needle guide hole 32a, there is an auxiliary valve chamber 3R that is connected to the needle guide hole 32a, and a step portion 3a is formed as an "abutment portion" at the boundary between the auxiliary valve chamber 3R and the needle guide hole 32a. A washer 43 attached to the rotor shaft 51 described later and a guide boss portion 41 of the needle valve 4 formed integrally with the rotor shaft 51 are inserted into the needle guide hole 32a of the holding portion 32. The ring-shaped retainer 34 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３５が配設されており、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、段部３ａより下側で保持部３２の側面の一箇所には、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。さらに、主弁室１Ｒとケース１４の内部は、フランジ部２５に設けられた弁軸の軸線Ｌ方向に連通する孔（不図示）により連通され、ケース１４の内部とガイド部材２の内部は、ガイド部材２の上部に設けられた連通孔により連通され、主弁体３の上部と主弁体３の段部３ａ直上の空間は、ワッシャ４３の外周及びニードル弁４のガイド用ボス部４１の外周と主弁体３のニードルガイド孔３２ａの内周との隙間により連通されることで、主弁室１Ｒと副弁室３Ｒが連通する。 A main valve spring 35 is disposed between the retainer 34 and the upper end of the guide hole 2A, and the main valve element 3 is biased in the direction (closing direction) of the main valve seat 13 by the main valve spring 35. A cylindrical sub-valve port 33a centered on the axis L is formed in the center of the sub-valve seat 33. A through hole 32b that connects the sub-valve chamber 3R and the main valve chamber 1R is formed in one location on the side of the retaining portion 32 below the step 3a, and when the needle valve 4 as the sub-valve element opens the sub-valve port 33a, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a are connected. Furthermore, the main valve chamber 1R and the inside of the case 14 are connected by a hole (not shown) provided in the flange portion 25 that communicates in the direction of the axis L of the valve shaft, the inside of the case 14 and the inside of the guide member 2 are connected by a communication hole provided in the upper part of the guide member 2, and the upper part of the main valve body 3 and the space directly above the step portion 3a of the main valve body 3 are connected by the outer periphery of the washer 43 and the gap between the outer periphery of the guide boss portion 41 of the needle valve 4 and the inner periphery of the needle guide hole 32a of the main valve body 3, thereby connecting the main valve chamber 1R and the auxiliary valve chamber 3R.

「副弁体」としてのニードル弁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、このニードル弁４はガイド用ボス部４１とニードル部４２とで構成されている。ガイド用ボス部４１はニードル部４２側に向かって徐々に径が小さくなる円錐台状の「当接部」としてのテーパ部４１ａを有し、このテーバ部４１ａは主弁体３の段部３ａ（当接部）に当接可能となっている。また、ニードル部４２はテーパ部４１ａの端部に連結されている。また、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が配設されている。そして、ワッシャ４３とガイド用ボス部４１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 as the "auxiliary valve body" is formed integrally with the rotor shaft 51 at the lower end of the rotor shaft 51, and this needle valve 4 is composed of a guide boss portion 41 and a needle portion 42. The guide boss portion 41 has a tapered portion 41a as a "contact portion" in the shape of a truncated cone whose diameter gradually decreases toward the needle portion 42 side, and this tapered portion 41a can contact the step portion 3a (contact portion) of the main valve body 3. The needle portion 42 is connected to the end of the tapered portion 41a. A circular washer 43 made of a lubricating resin is disposed at the upper end of the guide boss portion 41. The washer 43 and the guide boss portion 41 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 fixed airtightly to the upper end of the valve housing 1 by welding or the like, and the drive unit 5 is configured inside and outside this case 14. The drive unit 5 includes a stepping motor 5A, a screw feed mechanism 5B that moves the needle valve 4 forward and backward by the 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。また、ケース１４の内側天井部で回転ストッパ機構５Ｃを保持する円筒部１４ａ内には、ロータ軸５１の上端に当接するバネ受け５４を介してコイルバネ５５が配設されており、このコイルバネ５５はロータ軸５１を下方に付勢することにより、ねじ送り機構５Ｂにおけるのバックラッシュを防止している。 The stepping motor 5A is composed of a rotor shaft 51, a magnet rotor 52 rotatably arranged inside the case 14, a stator coil 53 arranged opposite the magnet rotor 52 on the outer periphery of the case 14, and other yokes and exterior members (not shown). The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male thread 51a is formed on the outer periphery of the rotor shaft 51 on the guide member 2 side. This male thread 51a is screwed into the female thread 24a of the guide member 2, so that the guide member 2 supports the rotor shaft 51 on the axis L. The female thread 24a of the guide member 2 and the male thread 51a of the rotor shaft 51 constitute the screw feed mechanism 5B. In addition, a coil spring 55 is disposed within the cylindrical portion 14a that holds the rotation stopper mechanism 5C on the inner ceiling of the case 14, via a spring bearing 54 that abuts against the upper end of the rotor shaft 51. This coil spring 55 biases the rotor shaft 51 downward, thereby preventing backlash in the 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 rotate, and the rotor shaft 51 moves in the axial direction L together with the magnet rotor 52 due to the screw feed mechanism 5B between the male thread 51a of the rotor shaft 51 and the female thread 24a of the guide member 2. Then, the needle valve 4 moves forward and backward in the axial direction L, and the needle valve 4 approaches or moves away from the auxiliary valve port 33a. When the needle valve 4 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 needle valve 4 and leaves the main valve seat 13. In addition, a protrusion 52a is formed on the magnet rotor 52, and as the magnet rotor 52 rotates, the protrusion 52a activates the rotation stopper mechanism 5C, and the lowest and highest positions of the rotor shaft 51 (and the magnet rotor 52) are 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。 In the low flow control range state of FIG. 1, the main valve body 3 is seated on the main valve seat 13, the main valve port 13a is closed, and the needle valve 4 controls the opening of the sub-valve port 33a to control the low flow rate. Also, for example, when the compressor of the refrigeration cycle system is stopped and the fluid (refrigerant) is stopped, if the needle valve 4 and the main valve body 3 rise, the main valve port 13a is fully opened as shown in FIG. 2. As a result, during cooling operation, a large flow rate of fluid (refrigerant) flows from the first joint pipe 11 to the second joint pipe 12, and during heating operation, a large flow rate of fluid (refrigerant) flows from the second joint pipe 12 to the first joint pipe 11.

図３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ニードル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の絞り部（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
流量制御の状態では、ニードル弁４のガイド用ボス部４１のテーパ部４１ａが主弁体３の段差部３ａに当接する。そして、このときバックラッシュ防止用のコイルバネ５５の付勢力により、ニードル弁４は主弁体３を主弁座１３側に押圧する。したがって、主弁室１Ｒと主弁ポート１３ａとの間で流体の圧力変化が生じても、主弁体３が振動することなく、小流量域の制御性が向上する。 As shown in FIG. 3, the needle portion 42 is composed of a straight portion 42a made of a cylinder with the axis L as the center line, and a needle 42b whose diameter is reduced toward the tip side. 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 constant flow rate of refrigerant flows through this first throttle portion, thereby performing small flow rate control. In addition, in this small flow rate control state, the tapered portion 41a of the guide boss portion 41 of the needle valve 4 abuts against the step portion 3a of the main valve body 3. At this time, the needle valve 4 presses the main valve body 3 toward the main valve seat 13 due to the biasing force of the coil spring 55 for preventing backlash. Therefore, even if a pressure change of the fluid occurs between the main valve chamber 1R and the main valve port 13a, the main valve body 3 does not vibrate, and the controllability in the small flow rate range is improved.

図４は第２実施形態の電動弁の小流量制御域状態の要部拡大縦断面図、図５は第２実施形態における第２絞り部の実施例１及び実施例２を示す図、図６は第１及び第２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、図７は第１及び第２実施形態の電動弁の変形例を示す図であり、以下の各実施形態及び変形例において電動弁の全体構成は図１及び図２と同様である。 Figure 4 is an enlarged longitudinal cross-sectional view of the main parts of the motor-operated valve of the second embodiment in the small flow control range state, Figure 5 is a diagram showing examples 1 and 2 of the second throttling portion in the second embodiment, Figure 6 is an enlarged view of the needle portion and auxiliary valve port in the small flow control range state of the motor-operated valve of the first and second embodiments, and Figure 7 is a diagram showing a modified example of the motor-operated valve of the first and second embodiments. The overall configuration of the motor-operated valve in each of the following embodiments and modified examples is the same as in Figures 1 and 2.

図４の第２実施形態の電動弁でも、ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間で第１の絞り部を構成すること、小流量制御の状態でニードル弁４のテーパ部４１ａが主弁体３の段差部３ａを当接、押圧して、主弁体３が振動することなく、小流量域の制御性が向上することは、第１実施形態と同様である。これに加えて第２実施形態では、主弁体３と主弁座１３との間に第２絞り部Ｐを形成したものである。 The motor-operated valve of the second embodiment of FIG. 4 is similar to the first embodiment in that a first throttling section is formed between the straight section 42a of the needle section 42 and the sub-valve port 33a, and in the state of small flow control, the tapered section 41a of the needle valve 4 abuts and presses the stepped section 3a of the main valve body 3, so that the main valve body 3 does not vibrate and the controllability in the small flow range is improved. In addition, in the second embodiment, a second throttling section P is formed between the main valve body 3 and the main valve seat 13.

図５（Ａ）の実施例１は、主弁座１３において主弁ポート１３ａの開口縁に「第２の絞り部Ｐ」としての溝６を形成したものである。溝６は、副弁ポート３３ａとニードル部４２のストレート部４２ａとの第１絞り部により小流量制御が行われるときにも、この溝６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。 In the first embodiment shown in FIG. 5(A), a groove 6 is formed as a "second throttling portion P" on the opening edge of the main valve port 13a in the main valve seat 13. The groove 6 acts to allow the refrigerant to flow from the main valve chamber 1R to the main valve port 13a even when low flow control is performed by the first throttling portion between the sub-valve port 33a and the straight portion 42a of the needle portion 42. Therefore, the pressure difference before and after the throttling portion between the sub-valve port 33a and the needle portion 42 is reduced, and the refrigerant passing noise at this throttling portion can be reduced.

図５（Ｂ）の実施例２は、主弁３の主弁部３１において「第２の絞り部Ｐ」としての溝６′を形成したものである。そして、実施例１と同様に。溝６′は、副弁ポート３３ａとニードル部４２のストレート部４２ａとの第１絞り部により小流量制御が行われるときにも、この溝６′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。 In the second embodiment of FIG. 5(B), a groove 6' is formed as a "second throttling portion P" in the main valve portion 31 of the main valve 3. As in the first embodiment, the groove 6' allows the refrigerant to flow from the main valve chamber 1R to the main valve port 13a even when low flow control is performed by the first throttling portion between the sub-valve port 33a and the straight portion 42a of the needle portion 42. Therefore, the pressure difference before and after the throttling portion between the sub-valve port 33a and the needle portion 42 is reduced, and the refrigerant passing sound at this throttling portion can be reduced.

また、図６に示すように、ニードル部４２は、軸線Ｌを中心線とする薄型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ニードル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. 6, the needle portion 42 is composed of a straight portion 42a made of a thin cylinder with the axis L as the center line, and a needle 42b whose diameter is reduced toward the tip side. The outer diameter of the straight portion 42a is smaller than the inner diameter of the sub-valve port 33a, and a first throttling portion (gap) is formed between the straight portion 42a and the sub-valve port 33a. A constant flow rate of refrigerant flows through this first throttling portion, and low flow control is performed. During this low flow control, the pressure of the refrigerant flowing into the straight portion 42a and the throttling portion of the sub-valve port 33a is dispersed around the axis L by a groove 6 (second throttling portion) formed on the sub-valve chamber 3R side of the sub-valve port 33a, reducing the pressure difference before and after the first throttling portion composed of the sub-valve seat 33 and the needle portion 42, thereby reducing the refrigerant passing sound at this first throttling portion.

図７の変形例は、ニードル部４２に「第２絞り部」としての溝４ａを形成したものである。溝４ａ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４ａは複数（この例では６個）形成され、この溝４ａ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４ａ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。この変形例では、溝４ａ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 the modified example shown in FIG. 7, a groove 4a is formed in the needle portion 42 as a "second throttle portion". The groove 4a is formed from the root portion 42c on the guide boss portion 44 side of the needle portion 42 to the middle of the straight portion 42a. In addition, a plurality of grooves 4a (six in this example) are formed, and the grooves 4a are formed at positions rotationally symmetrical with respect to the axis L at equal intervals (every 60°) around the axis L. Furthermore, the area of the horizontal cross section of the groove 4a becomes smaller as it approaches the auxiliary valve port 33a in the direction of the axis L. In this modified example, the groove 4a is formed only to the middle of the straight portion 42a, so the opening area of the throttle portion between the straight portion 42a and the auxiliary valve port 33a is constant as in the embodiment, and the flow rate during low flow control can be kept constant.

そして、この変形例でも、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４ａ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。 Even in this modified example, during low flow control, the pressure of the refrigerant flowing into the straight section 42a and the throttling section of the auxiliary valve port 33a is dispersed around the axis L by the groove 4a formed in the needle section 42, reducing the pressure difference before and after the throttling section formed by the auxiliary valve seat 33 and the needle section 42, thereby reducing the refrigerant passing noise in this throttling section.

図８は第３実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。この第３実施形態と第１実施形態との違いは、「副弁体」としてのニードル弁４′の構造である。この第３実施形態のニードル弁４′は、ロータ軸５１と一体に形成された薄型のガイド用ボス部４１′と、第１実施形態と同様なニードル部４２と、円柱部４３と、ニードル部４２側に向かって徐々に径が小さくなる円錐台状の「当接部」としてのテーパ部４４とで構成されている。そして、ニードル部４２はテーパ部４４の端部に連結されており、テーバ部４４は主弁体３の段部３ａに当接可能となっている。また、ガイド用ボス部４１′と主弁体３の段差部３ａとの間には、潤滑性樹脂からなる円環状のバネ受け７ａを介してコイルバネ７が配設されている。 Figure 8 is an enlarged longitudinal sectional view of the main part of the motor-operated valve of the third embodiment in the small flow control region state. The difference between the third embodiment and the first embodiment is the structure of the needle valve 4' as the "sub-valve body". The needle valve 4' of the third embodiment is composed of a thin guide boss portion 41' formed integrally with the rotor shaft 51, a needle portion 42 similar to that of the first embodiment, a cylindrical portion 43, and a tapered portion 44 as a truncated cone-shaped "contact portion" whose diameter gradually decreases toward the needle portion 42 side. The needle portion 42 is connected to the end of the tapered portion 44, and the tapered portion 44 can contact the step portion 3a of the main valve body 3. In addition, a coil spring 7 is arranged between the guide boss portion 41' and the step portion 3a of the main valve body 3 via a ring-shaped spring receiver 7a made of lubricating resin.

以上の構成により、第１実施形態と同様に、ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間の第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、この小流量制御の状態では、ニードル弁４′のテーパ部４４が主弁体３の段部３ａに当接する。そして、このときコイルバネ７の付勢力により、ニードル弁４′は主弁体３を主弁座１３側に押圧する。したがって、主弁室１Ｒと主弁ポート１３ａとの間で流体の圧力変化が生じても、主弁体３が振動することなく、小流量域の制御性が向上する。 With the above configuration, as in the first embodiment, a constant flow rate of refrigerant flows through the first throttling section between the straight section 42a of the needle section 42 and the sub-valve port 33a, thereby performing small flow rate control. In this small flow rate control state, the tapered section 44 of the needle valve 4' abuts against the step section 3a of the main valve body 3. At this time, the needle valve 4' presses the main valve body 3 toward the main valve seat 13 due to the biasing force of the coil spring 7. Therefore, even if a pressure change occurs in the fluid between the main valve chamber 1R and the main valve port 13a, the main valve body 3 does not vibrate, and controllability in the small flow rate range is improved.

図９は第４実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。この第４実施形態は第３実施形態のテーパ部４４を無くしたものである。この第４実施形態のニードル弁４″は、ロータ軸５１と一体に形成された薄型のガイド用ボス部４１″（フランジ部）と、１実施形態と同様な「副弁体」としてのニードル部４２と、長尺円錐台状の連結ロッド４３″とで構成されており、ニードル部４２は連結ロッド４３″の端部に連結されている。また、第３実施形態と同様に、ガイド用ボス部４１″と主弁体３の段部３ａとの間には、潤滑性樹脂からなる円環状のバネ受け７ａを介してコイルバネ７が配設されている。そして、コイルバネ７の下端は段部３ａに当接する「当接部」を構成している。 Figure 9 is an enlarged longitudinal sectional view of the main part of the motor-operated valve of the fourth embodiment in the small flow control region state. In this fourth embodiment, the tapered portion 44 of the third embodiment is eliminated. The needle valve 4" of this fourth embodiment is composed of a thin guide boss portion 41" (flange portion) formed integrally with the rotor shaft 51, a needle portion 42 as a "sub-valve body" similar to the first embodiment, and a long truncated cone-shaped connecting rod 43", and the needle portion 42 is connected to the end of the connecting rod 43". As in the third embodiment, a coil spring 7 is disposed between the guide boss portion 41" and the step portion 3a of the main valve body 3 via a ring-shaped spring receiver 7a made of lubricating resin. The lower end of the coil spring 7 forms an "abutment portion" that abuts against the step portion 3a.

以上の構成により、第１実施形態と同様に、ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間の第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、この小流量制御の状態では、コイルバネ６の付勢力により、ニードル弁４″は主弁体３を主弁座１３側に押圧する。したがって、主弁室１Ｒと主弁ポート１３ａとの間で流体の圧力変化が生じても、主弁体３が振動することなく、小流量域の制御性が向上する。 As with the first embodiment, the above configuration allows a constant flow rate of refrigerant to flow through the first throttling section between the straight section 42a of the needle section 42 and the sub-valve port 33a, thereby controlling the small flow rate. In this small flow rate control state, the needle valve 4" presses the main valve body 3 toward the main valve seat 13 due to the biasing force of the coil spring 6. Therefore, even if a change in fluid pressure occurs between the main valve chamber 1R and the main valve port 13a, the main valve body 3 does not vibrate, improving controllability in the small flow rate range.

図１０は第５実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。この第５実施形態と第１実施形態との違いは、ニードル弁４のテーパ部４１ａに対向する主弁体３の段差部３ａに溝８を形成したものである。この第５実施形態でも、ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間の第１絞り部で小流量制御が行われること、この小流量制御のとき、ニードル弁４が主弁体３を主弁座１３側に押圧することで、主弁体３が振動することなく、小流量域の制御性が向上することは、第１実施形態と同様である。溝８は、主弁体３のニードルガイド孔３２ａ内とガイド部材２のガイド孔２Ａ内とを副弁室３Ｒに導通し、テーパ部４１ａが主弁体３の段部３ａに当接した状態でもニードル弁４に対する背圧を副弁室３Ｒと均圧するものである。 Figure 10 is an enlarged longitudinal sectional view of the main part of the motor-operated valve of the fifth embodiment in the small flow control region state. The difference between the fifth embodiment and the first embodiment is that a groove 8 is formed in the step portion 3a of the main valve body 3 facing the tapered portion 41a of the needle valve 4. In the fifth embodiment, the small flow control is performed in the first throttling portion between the straight portion 42a of the needle portion 42 and the sub-valve port 33a, and in this small flow control, the needle valve 4 presses the main valve body 3 toward the main valve seat 13, so that the main valve body 3 does not vibrate and the controllability in the small flow region is improved, as in the first embodiment. The groove 8 connects the needle guide hole 32a of the main valve body 3 and the guide hole 2A of the guide member 2 to the sub-valve chamber 3R, and equalizes the back pressure against the needle valve 4 with the sub-valve chamber 3R even when the tapered portion 41a is in contact with the step portion 3a of the main valve body 3.

図１１は第６実施形態の電動弁の小流量制御域状態の要部拡大縦断面図である。この第
６実施形態と第１実施形態との違いは、ニードル弁４のテーパ部４１ａに溝９を形成したものである。この第６実施形態でも、ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間の第１絞り部で小流量制御が行われること、この小流量制御のとき、ニードル弁４が主弁体３を主弁座１３側に押圧することで、主弁体３が振動することなく、小流量域の制御性が向上することは、第１実施形態と同様である。溝９はガイド用ボス部４１の外周側からニードル部４２のストレート部４２ａの付け根まで形成したものである。ニードル部４２のストレート部４２ａと副弁ポート３３ａとの間の第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ことは前記各実施形態と同様である。溝９は、主弁体３のニードルガイド孔３２ａ内とガイド部材２のガイド孔２Ａ内とを副弁室３Ｒに導通し、テーパ部４１ａが主弁体３の段部３ａに当接した状態でもニードル弁４に対する背圧を副弁室３Ｒと均圧するものである。 11 is an enlarged longitudinal sectional view of the main part of the motor-operated valve of the sixth embodiment in the small flow rate control region state. The difference between the sixth embodiment and the first embodiment is that a groove 9 is formed in the tapered portion 41a of the needle valve 4. In the sixth embodiment, the small flow rate control is performed in the first throttle portion between the straight portion 42a of the needle portion 42 and the sub-valve port 33a, and in the small flow rate control, the needle valve 4 presses the main valve body 3 toward the main valve seat 13, so that the main valve body 3 does not vibrate and the controllability in the small flow rate region is improved, as in the first embodiment. The groove 9 is formed from the outer periphery of the guide boss portion 41 to the root of the straight portion 42a of the needle portion 42. As in each of the above embodiments, the small flow rate control is performed by a constant flow rate of refrigerant flowing through the first throttle portion between the straight portion 42a of the needle portion 42 and the sub-valve port 33a. The groove 9 connects the needle guide hole 32a of the main valve body 3 and the guide hole 2A of the guide member 2 to the sub-valve chamber 3R, and equalizes the back pressure on the needle valve 4 with the sub-valve chamber 3R even when the tapered portion 41a abuts against the step portion 3a of the main valve body 3.

次に、図１２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 refrigeration cycle system of the present invention will be described with reference to FIG. 12. The refrigeration cycle system is used, for example, in an air conditioner such as a home air conditioner. The motor-operated valve 100 of the embodiment is provided 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, and constitutes a heat pump type refrigeration cycle together with the compressor 95, four-way valve 96, outdoor heat exchanger 94, and 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, four-way valve 96, outdoor heat exchanger 94, and electronic expansion valve 93 are installed outdoors to constitute a heating and cooling device.

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 embodiment of the motor-operated valve 100 as a dehumidification valve, during cooling or heating other than dehumidification, the main valve body is fully open, and the first indoor heat exchanger 91 and the second indoor heat exchanger 92 are made into a single indoor heat exchanger. The combined indoor heat exchanger and outdoor heat exchanger 94 function alternatively as an "evaporator" and a "condenser". In other words, the motor-operated 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。 The present invention is not limited to the above-described embodiment, but includes other configurations that can achieve the object of the present invention, and the following modifications are also included in the present invention. For example, the above-described embodiment illustrates an electric valve 100 used in an air conditioner such as a home air conditioner, but the electric valve of the present invention is not limited to home air conditioners, but may also be used in commercial air conditioners, and is not limited to air conditioners, but can also be applied to various types of refrigeration machines, etc.

また、前記実施形態では、ニードル弁側に当接部としてのテーバ部を形成し、主弁体側に当接部としての段部を形成した例について説明したが、ニードル弁側に円柱状の段部を形成し、主弁体側にこの円柱状の段部をに対向するようなすり鉢状のテーバ部を形成してもよい。また、前記実施形態では、主弁体、主弁座、段差部、又は、ニードル弁に形成した第２の絞り部は溝の構成として記載したが、第２の絞り部は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 above embodiment, an example was described in which a tapered portion was formed as an abutment portion on the needle valve side and a step portion was formed as an abutment portion on the main valve body side, but a cylindrical step portion may be formed on the needle valve side and a cone-shaped tapered portion may be formed on the main valve body side facing this cylindrical step portion. In the above embodiment, the second throttling portion formed on the main valve body, main valve seat, step portion, or needle valve was described as having a groove configuration, but the second throttling portion is not limited to a groove and may be a second throttling portion formed by a hole or the like.

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 above describes the embodiments of the present invention 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, and the present invention also includes design changes that do not deviate from the gist of 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
２ ガイド部材
２Ａ ガイド孔
２１ 圧入部
２２ ガイド部
２３ ガイド部
２４ ホルダ部
２４ａ 雌ねじ部
２５ フランジ部
３ 主弁体
３Ｒ 副弁室
３ａ 段部（当接部）
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
３４ リテーナ
３５ 主弁ばね
４ ニードル弁（副弁体）
４１ ガイド用ボス部
４１ａ テーパ部（当接部）
４２ ニードル部
４３ ワッシャ
５ 駆動部
５Ａ ステッピングモータ
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
５４ バネ受け
５５ コイルバネ
５Ｂ ねじ送り機構
５Ｃ ストッパ機構
Ｌ 軸線
６ 溝
６′ 溝
４′ ニードル弁（副弁体）
４１′ ガイド用ボス部
４２ ニードル部
４３ 円柱部
４４ テーパ部（当接部）
７ａ バネ受け
７ コイルバネ
４″ ニードル弁（副弁体）
４１″ ガイド用ボス部
４２ ニードル部
４３″ 連結ロッド
８ 溝
９ 溝
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 2 Guide member 2A Guide hole 21 Press-fit portion 22 Guide portion 23 Guide portion 24 Holder portion 24a Female thread portion 25 Flange portion 3 Main valve body 3R Sub-valve chamber 3a Step portion (contact portion)
31 Main valve portion 32 Retaining portion 32a Needle guide hole 32b Conduit hole 33 Sub-valve seat 33a Sub-valve port 34 Retainer 35 Main valve spring 4 Needle valve (sub-valve body)
41 Guide boss portion 41a Tapered portion (contact portion)
42 Needle portion 43 Washer 5 Drive portion 5A Stepping motor 51 Rotor shaft 51a Male thread portion 52 Magnet rotor 53 Stator coil 54 Spring receiver 55 Coil spring 5B Screw feed mechanism 5C Stopper mechanism L Axis 6 Groove 6' Groove 4' Needle valve (auxiliary valve body)
41' Guide boss portion 42 Needle portion 43 Cylindrical portion 44 Tapered portion (contact portion)
7a Spring receiver 7 Coil spring 4" Needle valve (auxiliary valve body)
41″ Guide boss portion 42 Needle portion 43″ Connecting rod 8 Groove 9 Groove 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 Motor-operated valve

Claims (8)

弁ハウジングの主弁室内に設けられた主弁ポートの周縁に形成された主弁座と近接または離隔する主弁体を備えるとともに、前記主弁体の内部の副弁室内に設けられた副弁ポートの周縁に形成された副弁座と近接または離隔する副弁体とを備える二段式の電動弁であって、
前記副弁体と、前記主弁体とは、互いに直接接触する当接部をそれぞれ備え、
前記副弁体が、前記弁ハウジングの軸線を中心線とする円柱からなるストレート部を有し、前記ストレート部の外径は、前記副弁ポートの内径よりも小さく、
前記主弁体が前記主弁座に着座するとともに前記ストレート部が前記副弁ポート内に位置することで前記副弁体と前記副弁ポートとの隙間からなる第１絞り部が形成された状態において、前記副弁体が前記当接部により前記主弁体と当接することで、前記副弁体が前記主弁体を前記主弁座に押し付けるよう構成されていることを特徴とする電動弁。 A two-stage motor-operated valve comprising a main valve body adjacent to or separated from a main valve seat formed on a periphery of a main valve port provided in a main valve chamber of a valve housing, and a sub-valve body adjacent to or separated from a sub-valve seat formed on a periphery of a sub-valve port provided in a sub-valve chamber inside the main valve body,
The sub-valve body and the main valve body each have a contact portion that directly contacts each other,
the sub-valve body has a straight portion formed of a cylinder having a center line coincident with an axis of the valve housing, and an outer diameter of the straight portion is smaller than an inner diameter of the sub-valve port,
an electric valve configured such that, when the main valve body is seated on the main valve seat and the straight portion is positioned within the sub-valve port, thereby forming a first throttling portion consisting of a gap between the sub-valve body and the sub-valve port, the sub-valve body abuts against the main valve body at the abutment portion, thereby pressing the main valve body against the main valve seat. 前記副弁体は、前記当接部と、ニードル部と、を備え、
前記ニードル部は、前記ストレート部と、前記主弁ポート側に向かって縮径するとともに前記ストレート部の前記主弁ポート側に接続されるニードルと、を備えることを特徴とする請求項１に記載の電動弁。 The sub-valve body includes the contact portion and a needle portion,
2. The motor-operated valve according to claim 1, wherein the needle portion comprises: the straight portion; and a needle that reduces in diameter toward the main valve port side and is connected to the main valve port side of the straight portion. 前記当接部より前記副弁ポート側に、前記主弁室と前記副弁室とを連通する導通孔が形成されることを特徴とする請求項１に記載の電動弁。 The motor-operated valve according to claim 1, characterized in that a through hole that communicates between the main valve chamber and the auxiliary valve chamber is formed on the auxiliary valve port side of the abutment portion. 前記副弁体と前記主弁体との前記当接部は、少なくとも一方が段部であることを特徴とする請求項１～３のいずれか一項に記載の電動弁。 The motor-operated valve according to any one of claims 1 to 3, characterized in that at least one of the contact portions between the sub-valve body and the main valve body is a step portion. 前記副弁体と前記主弁体との前記当接部は、一方が前記副弁ポートの軸線を中心軸とするテーパ部であり、他方が前記軸線を中心軸とする段部であることを特徴とする請求項１～４のいずれか一項に記載の電動弁。 The motor-operated valve according to any one of claims 1 to 4, characterized in that one of the contact portions between the sub-valve body and the main valve body is a tapered portion with the axis of the sub-valve port as its central axis, and the other is a stepped portion with the axis as its central axis. 前記主弁座または前記主弁体に、または／および、前記副弁座または前記副弁体に第２の絞り部が形成されていることを特徴とする請求項５に記載の電動弁。 The motor-operated valve according to claim 5, characterized in that a second throttle portion is formed in the main valve seat or the main valve body, and/or in the sub-valve seat or the sub-valve body. 前記第２の絞り部が、溝または孔により構成されていることを特徴とする請求項６に記載の電動弁。 The motor-operated valve according to claim 6, characterized in that the second throttling portion is formed by a groove or a hole. 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１～７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 refrigeration cycle system including 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, wherein the motor-operated valve according to any one of claims 1 to 7 is used as the dehumidification valve.
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