JP2021067314A - Motor-operated valve and refrigeration cycle system - Google Patents

Motor-operated valve and refrigeration cycle system Download PDF

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Publication number
JP2021067314A
JP2021067314A JP2019192915A JP2019192915A JP2021067314A JP 2021067314 A JP2021067314 A JP 2021067314A JP 2019192915 A JP2019192915 A JP 2019192915A JP 2019192915 A JP2019192915 A JP 2019192915A JP 2021067314 A JP2021067314 A JP 2021067314A
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Prior art keywords
valve
main valve
sub
valve body
main
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JP7246291B2 (en
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雄希 北見
Yuki Kitami
雄希 北見
亮司 小池
Ryoji Koike
亮司 小池
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to CN202011077973.7A priority patent/CN112696498A/en
Publication of JP2021067314A publication Critical patent/JP2021067314A/en
Priority to JP2023038527A priority patent/JP7474892B2/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
    • 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)
  • Electrically Driven Valve-Operating Means (AREA)
  • Lift Valve (AREA)

Abstract

To improve controllability in a small flow rate area by preventing vibration of a main valve element in a small flow rate control area, in a motor-operated valve having two-stage flow rate control areas in which a main valve port of a main valve seat is kept in a fully closed state by a main valve element, and flow rate control in the small flow rate control area, of a refrigerant is performed by a throttle portion between an auxiliary valve port formed on the main valve element and a needle valve.SOLUTION: A main valve port 13a is kept in a fully closed state by a main valve element 3, and a fluid flows in a throttle portion (clearance) between a needle portion 42 of a needle valve 4 and an auxiliary valve port 33a to define a small flow rate control area. In the small flow rate control area, a tapered portion 41a (contact portion) of the needle valve 4 (auxiliary valve element) is brought into contact with a step portion 3a (contact portion) of the main valve element 3. By the contact of the taper portion 41a and the step portion 3a, the main valve element 3 is pressed toward a main valve seat 13 side by the needle valve 4.SELECTED DRAWING: Figure 3

Description

本発明は、冷凍サイクルシステムなどに使用する電動弁及び冷凍サイクルシステムに関する。 The present invention relates to an electric valve and a refrigeration cycle system used in a refrigeration cycle system or 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 a refrigeration cycle of an air conditioner, there is an electric valve that controls the flow rate in a small flow rate control range and a large flow rate control range. Such an electric valve has an application to be mounted on an indoor unit (for example, a dehumidifying valve), and is disclosed in, for example, Japanese Patent Application Laid-Open No. 2019-132347 (Patent Document 1).

特開２０１９−１３２３４７号公報Japanese Unexamined Patent Publication No. 2019-132347

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。 In this type of electric valve, for example, a dehumidifying operation is performed in the small flow rate control area. In this small flow rate control area, the main valve port of the main valve seat is fully closed by the main valve body, and the main valve body is used. The refrigerant is configured to pass through the throttle portion between the formed sub-valve port and the needle valve (sub-valve body). However, there is a problem that pressure changes and pipe vibrations occur due to pulsation of the refrigerant flow on the primary side or the secondary side, the main valve body vibrates, and the controllability in the small flow rate range deteriorates.

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。 In the present invention, the main valve body is seated on the main valve seat, and the throttle portion between the main valve body and the main valve seat and the throttle between the auxiliary valve port and the needle valve formed on the main valve body are narrowed. In an electric valve that has a two-stage flow rate control range that controls the flow rate of the refrigerant in the small flow rate control range, it prevents vibration of the main valve body in the small flow rate control range and improves controllability in the small flow rate range. The task is to make it.

本発明の電動弁は、弁本体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、前記主弁体が前記主弁座に着座した状態において、前記副弁体が前記副弁座と当接することなく、前記副弁体が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 electric valve of the present invention includes a main valve body that is close to or separated from a main valve seat formed on the periphery of a main valve port provided in the main valve chamber of the valve body, and a sub valve inside the main valve body. It is a two-stage electric valve including a sub-valve seat formed on the periphery of a sub-valve port provided in a room and a sub-valve body that is close to or separated from the sub-valve seat, and the main valve body is seated on the main valve seat. In the state, the sub-valve body does not come into contact with the sub-valve seat, but the sub-valve body comes into contact with the main valve body so that the sub-valve body presses the main valve body against the main valve seat. It is characterized by being configured.

また、前記副弁室側の前記当接部より下側に、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。 Further, an electric valve characterized in that a conduction hole communicating the main valve chamber and the sub-valve chamber is formed below the contact portion on the sub-valve chamber side is preferable.

この際、前記副弁体と前記主弁体との当接部は、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。 At this time, one of the contact portions between the sub-valve body and the main valve body is a tapered portion whose central axis is the axis of the sub-valve port, and the other is a stepped portion whose central axis is the axis. An electric valve characterized by this is preferable.

また、前記副弁体と前記主弁体との当接部は、前記副弁体に設けられたフランジ部と前記主弁体に設けられた段部との間に設置されたバネを介して当接されることを特徴とする電動弁が好ましい。 Further, the contact portion between the sub-valve body and the main valve body is formed via a spring installed between the flange portion provided on the sub-valve body and the step portion provided on the main valve body. An electric valve characterized by being abutted is preferable.

また、前記弁室からガイド部材のフランジ部に設けた前記軸線方向の孔を通って、ガイド部材のガイド部に設けた連通孔からガイド部内を通り、前記副弁体外周と前記主弁体内周との隙間を通って前記副弁室の下部に達する連通路が形成されることを特徴とする電動弁が好ましい。 Further, the valve chamber passes through the axial hole provided in the flange portion of the guide member, the communication hole provided in the guide portion of the guide member passes through the guide portion, and the outer periphery of the sub-valve body and the inner circumference of the main valve. An electric valve characterized in that a communication passage is formed to reach the lower part of the auxiliary valve chamber through the gap between the valve and the vehicle is preferable.

また、前記副弁体のニードル部と前記副弁ポートとの隙間からなる第１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。 Further, an electric valve characterized in that a first throttle portion formed by a gap between the needle portion of the sub-valve body and the sub-valve port is formed is preferable.

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。 Further, an electric valve characterized in that a second throttle portion is formed on the main valve seat or the main valve body and / or on the sub valve seat or the sub valve body is preferable.

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。 Further, an electric valve characterized in that the second throttle portion is formed of a groove or a hole is preferable.

本発明の冷凍サイクルシステムは、圧縮機と、室内熱交換器と、室外熱交換器と、前記室内熱交換器と前記室外熱交換器との間に設けられた電子膨張弁と、前記室内熱交換器に設けられる除湿弁とを含む冷凍サイクルシステムであって、前記電動弁が、前記除湿弁として用いられていることを特徴とする。 The refrigeration cycle system of the present invention includes a compressor, an indoor heat exchanger, an outdoor heat exchanger, an electronic expansion valve provided between the indoor heat exchanger and the outdoor heat exchanger, and the indoor heat. A refrigeration cycle system including a dehumidifying valve provided in an exchanger, characterized in that the electric valve is used as the dehumidifying 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 electric valve and refrigeration cycle system of the present invention, there is a throttle portion (gap) between the sub-valve body and the sub-valve port, or between the main valve body and the main valve seat, or between the sub-valve body and the sub-valve. In the state of small flow control by the throttle part between the seat, the contact part between the sub-valve body and the main valve body (including the one via a spring between the sub-valve body and the main valve body) comes into contact with each other. Since the auxiliary valve body presses the main valve body against the main valve seat, even if the pressure of the fluid at the main valve port changes or the pipe vibration occurs, the main valve body does not vibrate and the controllability in the small flow 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。It is a vertical cross-sectional view of the small flow rate control region state of the electric valve of 1st Embodiment of this invention. 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。It is a vertical cross-sectional view at the time of the operation stop or the cooling operation in the fully open state of the main valve body of the electric valve of 1st Embodiment. 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。It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of 1st Embodiment. 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。It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of the 2nd Embodiment. 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。It is a figure which shows Example 1 and Example 2 of the 2nd diaphragm part in 2nd 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。It is an enlarged view of the needle part and the auxiliary valve port in the small flow rate control range state of the electric valve of the 1st and 2nd embodiments. 第１及び第２実施形態の変形例を示す図である。It is a figure which shows the modification of 1st and 2nd Embodiment. 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。It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of the 3rd embodiment. 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。It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of 4th Embodiment. 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. 5 is an enlarged vertical cross-sectional view of a main part of the electric 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。It is an enlarged vertical sectional view of the main part of the small flow rate control region state of the electric valve of the sixth embodiment. 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。It is a figure which shows the refrigeration 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 electric valve and the 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 electric valve of the first embodiment in a small flow rate control range state, and FIG. 2 is a vertical cross-sectional view of the electric valve of the first embodiment when the main valve body is fully open and the operation is stopped or during cooling operation. FIG. 3 is an enlarged vertical cross-sectional view of a main part of the electric valve of the first embodiment in the small flow rate control range state. The concept of "upper and lower" in the following description corresponds to the upper and lower parts in the drawings of FIGS. 1 and 2. The electric valve 100 includes a valve housing 1, a guide member 2, a main valve body 3, a needle valve 4 as a "secondary 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 of, for example, brass, stainless steel, or the like in a substantially cylindrical shape, and has a main valve chamber 1R inside the valve housing 1. A first joint pipe 11 conducting to the main valve chamber 1R is connected to one side of the outer circumference of the valve housing 1, and a second joint pipe 12 is connected to a tubular portion extending downward from the lower end. Further, 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 inside of the main valve seat 13 is the main valve port 13a, and the second joint The pipe 12 is conducted 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 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。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 includes a press-fitting portion 21 that is press-fitted into the inner peripheral surface of the valve housing 1, substantially cylindrical guide portions 22 and 23 that are smaller in diameter than the press-fitting portion 21 and are located above and below the press-fitting portion 21, and an upper guide. It has a holder portion 24 extending above 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, 23, and the holder portion 24 are configured as an integral 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 integrally provided together with the resin press-fitting portion 21 by insert molding. The flange portion 25 is provided with a hole (not shown) for communicating the main valve chamber 1R and the inside of the case 14, which will be described later, in the axis L direction 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-fitting portion 21, and is fixed to the upper end portion of the valve housing 1 via the flange portion 25 by welding. Further, in the guide member 2, a cylindrical guide hole 2A coaxial with the axis L is formed inside the press-fitting portion 21 and the upper and lower guide portions 22 and 23, and the guide hole 2A is formed in the center of the holder portion 24. A female screw portion 24a coaxial with the screw portion 24a and a screw hole thereof are formed. The main valve body 3 is arranged 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 includes a main valve portion 31 that seats and departs from the main valve seat 13, a holding portion 32 having a columnar needle guide hole 32a, and a sub valve seat that constitutes the bottom of the needle guide hole 32a. It has 33 and a retainer 34 provided at the end of the holding portion 32. Further, below the needle guide hole 32a, there is an auxiliary valve chamber 3R connected to the needle guide hole 32a, and a step portion as an "contact portion" at the boundary between the auxiliary valve chamber 3R and the needle guide hole 32a. 3a is formed. A washer 43 attached to the rotor shaft 51, which will be described later, and a guide boss portion 41 of the needle valve 4 integrally formed 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。 Further, a main valve spring 35 is disposed between the retainer 34 and the upper end portion of the guide hole 2A, and the main valve body 3 is moved in the direction (closed direction) of the main valve seat 13 by the main valve spring 35. Being urged. A cylindrical sub-valve port 33a centered on the axis L is formed at the center of the sub-valve seat 33. Further, a conduction hole 32b that conducts the auxiliary valve chamber 3R and the main valve chamber 1R is formed at one position on the side surface of the holding portion 32 below the step portion 3a, and the needle valve 4 as the auxiliary valve body 4 When the sub-valve port 33a is opened, the main valve chamber 1R, the sub-valve chamber 3R, the sub-valve port 33a, and the main valve port 13a become conductive. Further, the main valve chamber 1R and the inside of the case 14 are communicated with each other by a hole (not shown) communicating with the valve shaft in the axis L direction provided in the flange portion 25, and the inside of the case 14 and the inside of the guide member 2 are communicated with each other. The space is communicated by the communication holes provided in the upper part of the guide member 2, and the space directly above the upper part of the main valve body 3 and the step portion 3a of the main valve body 3 is the outer circumference of the washer 43 and the guide boss portion 41 of the needle valve 4. The main valve chamber 1R and the sub-valve chamber 3R are communicated with each other by being communicated by the gap between the outer periphery and the inner circumference of the needle guide hole 32a of the main valve body 3.

「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 "secondary valve body" is integrally formed with the rotor shaft 51 at the lower end of the rotor shaft 51, and the needle valve 4 is composed of a guide boss portion 41 and a needle portion 42. There is. The guide boss portion 41 has a tapered portion 41a as a truncated cone-shaped "contact portion" whose diameter gradually decreases toward the needle portion 42 side, and this taber portion 41a is a step portion 3a of the main valve body 3. It is possible to contact the (contact part). Further, the needle portion 42 is connected to the end portion of the tapered portion 41a. An annular 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 airtightly fixed to the upper end of the valve housing 1 by welding or the like, and a drive unit 5 is formed inside and outside the case 14. The drive unit 5 includes a stepping motor 5A, a screw feed mechanism 5B that advances and retreats the needle valve 4 by the rotation of the stepping motor 5A, and a stopper mechanism 5C that regulates 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 includes a rotor shaft 51, a magnet rotor 52 rotatably arranged inside the case 14, a stator coil 53 arranged to face the magnet rotor 52 on the outer circumference of the case 14, and others shown in the figure. It is composed of a yoke, exterior members, etc. The rotor shaft 51 is attached to the center of the magnet rotor 52 via a bush, and a male screw 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, whereby the guide member 2 supports the rotor shaft 51 on the axis L. The female screw portion 24a of the guide member 2 and the male screw portion 51a of the rotor shaft 51 form the screw feed mechanism 5B. Further, a coil spring 55 is arranged in a cylindrical portion 14a that holds the rotation stopper mechanism 5C on the inner ceiling portion of the case 14 via a spring receiver 54 that abuts on the upper end of the rotor shaft 51. By urging the rotor shaft 51 downward, backlash in the screw feed mechanism 5B is prevented.

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 magnet rotor 52 is provided by the screw feed mechanism 5B between the male screw portion 51a of the rotor shaft 51 and the female screw portion 24a of the guide member 2. At the same time, the rotor shaft 51 moves in the L direction of the axis. Then, the needle valve 4 moves back and forth in the axis L direction, and the needle valve 4 approaches or separates from the auxiliary valve port 33a. Further, 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 separates from the main valve seat 13. A protrusion 52a is formed on the magnet rotor 52, and the protrusion 52a operates the rotation stopper mechanism 5C as the magnet rotor 52 rotates, and the lowermost position of the rotor shaft 51 (and the magnet rotor 52) and the lowermost position and the magnet rotor 52. The topmost 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。 In the small flow rate 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 degree of the sub valve port 33a, resulting in a small flow rate. Is controlled. Further, for example, when the needle valve 4 and the main valve body 3 are raised while the compressor of the refrigeration cycle system is stopped and the fluid (refrigerant) is stopped, the main valve port 13a is fully opened as shown in FIG. Become. As a result, a large flow rate of fluid (refrigerant) flows from the first joint pipe 11 to the second joint pipe 12 during the cooling operation, and a large flow rate flows from the second joint pipe 12 to the first joint pipe 11 during the heating operation. A fluid (refrigerant) is flowed.

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 formed of a cylinder having an axis L as a center line and a needle 42b whose diameter is reduced toward the tip 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. Then, a small flow rate control is performed by flowing a constant flow rate of the refrigerant through the first throttle portion. Further, in this small flow rate control state, the tapered portion 41a of the guide boss portion 41 of the needle valve 4 comes into contact with the stepped 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 by the urging force of the coil spring 55 for preventing backlash. Therefore, even if the pressure of the fluid changes 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 region 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。 FIG. 4 is an enlarged vertical cross-sectional view of a main part of the small flow rate control range state of the electric valve of the second embodiment, and FIG. 5 is a view showing Examples 1 and 2 of the second throttle portion in the second embodiment, FIG. Is an enlarged view of the needle portion and the auxiliary valve port in the small flow rate control range state of the electric valves of the first and second embodiments, and FIG. 7 is a diagram showing a modification of the electric valves of the first and second embodiments. In each of the following embodiments and modifications, the overall configuration of the electric valve is the same as in FIGS. 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。 Also in the electric valve of the second embodiment shown in FIG. 4, the first throttle portion is formed between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a, and the tapered portion of the needle valve 4 is controlled by a small flow rate. Similar to the first embodiment, the 41a abuts and presses the stepped portion 3a of the main valve body 3 so that the main valve body 3 does not vibrate and the controllability in the small flow rate range is improved. In addition to this, in the second embodiment, the second throttle portion 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 of FIG. 5A, a groove 6 as a “second throttle portion P” is formed at the opening edge of the main valve port 13a in the main valve seat 13. The groove 6 allows the refrigerant to flow from the main valve chamber 1R to the main valve port 13a through the groove 6 even when the small flow rate is controlled by the first throttle portion of the auxiliary valve port 33a and the straight portion 42a of the needle portion 42. To act. Therefore, the differential pressure between the auxiliary valve port 33a and the needle portion 42 before and after the throttle portion is reduced, and the refrigerant passing noise at the throttle 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. 5B, a groove 6'as a "second throttle portion P" is formed in the main valve portion 31 of the main valve 3. Then, as in the first embodiment. The groove 6'is used as a refrigerant from the main valve chamber 1R to the main valve port 13a even when the small flow rate is controlled by the first throttle portion of the auxiliary valve port 33a and the straight portion 42a of the needle portion 42. Acts to shed. Therefore, the differential pressure between the auxiliary valve port 33a and the needle portion 42 before and after the throttle portion is reduced, and the refrigerant passing noise at the throttle 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。 Further, as shown in FIG. 6, the needle portion 42 is composed of a straight portion 42a formed of a thin cylinder having an axis L as a center line and a needle 42b whose diameter is reduced toward the tip 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. Then, a small flow rate control is performed by flowing a constant flow rate of the refrigerant through the first throttle portion. Further, in 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 determined by the groove 6 (second throttle portion) formed on the sub-valve chamber 3R side of the sub-valve port 33a. Dispersed around the axis L, the differential pressure before and after the first throttle portion composed of the auxiliary valve seat 33 and the needle portion 42 is reduced, and the refrigerant passing noise in the first throttle portion can be reduced.

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 of FIG. 7, a groove 4a as a "second drawing portion" is formed in the needle portion 42. The groove 4a is formed from the base portion 42c of the needle portion 42 on the guide boss portion 44 side to the middle of the straight portion 42a. Further, a plurality of (six) grooves 4a are formed, and the grooves 4a are formed at positions rotationally symmetric with respect to the axis L at equal intervals (every 60 °) around the axis L. Further, the area of the horizontal cross section of the groove 4a becomes smaller as it approaches the auxiliary valve port 33a in the axis L direction. In this modification, since the groove 4a is formed only up to the middle of the straight portion 42a, 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 small flow rate control The flow rate at the time 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 modification, the pressure of the refrigerant flowing into the straight portion 42a and the throttle portion of the sub-valve port 33a is dispersed around the axis L from the groove 4a formed in the needle portion 42 during the small flow rate control, and the sub-valve. The differential pressure between the front and rear of the throttle portion composed of the seat 33 and the needle portion 42 is reduced, and the refrigerant passing noise in the throttle portion can be reduced.

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。 FIG. 8 is an enlarged vertical cross-sectional view of a main part of the electric valve of the third embodiment in the small flow rate control range state. The difference between the third embodiment and the first embodiment is the structure of the needle valve 4'as the "secondary valve body". The needle valve 4'of the third embodiment has 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 needle portion. It is composed of a tapered portion 44 as a truncated cone-shaped "contact portion" whose diameter gradually decreases toward the 42 side. The needle portion 42 is connected to the end portion of the tapered portion 44, and the taber portion 44 can come into contact with the step portion 3a of the main valve body 3. Further, a coil spring 7 is disposed between the guide boss portion 41'and the stepped portion 3a of the main valve body 3 via an annular spring receiver 7a made of a 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 small flow rate control is performed by flowing a constant flow rate of the refrigerant through the first throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a. In the state of small flow rate control, the tapered portion 44 of the needle valve 4'contacts 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 by the urging force of the coil spring 7. Therefore, even if the pressure of the fluid changes 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 region 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。 FIG. 9 is an enlarged vertical cross-sectional view of a main part of the electric valve of the fourth embodiment in the small flow rate control range state. This fourth embodiment eliminates the tapered portion 44 of the third embodiment. The needle valve 4 "of the fourth embodiment has a thin guide boss portion 41" (flange portion) integrally formed with the rotor shaft 51 and a needle portion as a "secondary valve body" similar to that of the first embodiment. It is composed of a 42 and a long truncated cone-shaped connecting rod 43 ″, and the needle portion 42 is connected to the end of the connecting rod 43 ″. Further, as in the third embodiment, the coil spring 7 is arranged between the guide boss portion 41 ″ and the step portion 3a of the main valve body 3 via an annular spring receiver 7a made of a lubricating resin. The lower end of the coil spring 7 constitutes an "contact portion" that abuts on 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。 With the above configuration, as in the first embodiment, a small flow rate control is performed by flowing a constant flow rate of the refrigerant through the first throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a. In the small flow rate control state, the needle valve 4 ″ presses the main valve body 3 toward the main valve seat 13 by the urging force of the coil spring 6. Therefore, the fluid flows between the main valve chamber 1R and the main valve port 13a. Even if the pressure changes, the main valve body 3 does not vibrate, and the controllability in the small flow rate region is improved.

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。 FIG. 10 is an enlarged vertical cross-sectional view of a main part of the electric valve of the fifth embodiment in the small flow rate control range state. The difference between the fifth embodiment and the first embodiment is that a groove 8 is formed in a stepped portion 3a of the main valve body 3 facing the tapered portion 41a of the needle valve 4. Also in this fifth embodiment, the small flow rate control is performed at the first throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a, and at the time of this small flow rate control, the needle valve 4 is the main valve body. By pressing 3 toward the main valve seat 13, the controllability of the small flow rate region is improved without the main valve body 3 vibrating, as in the first embodiment. The groove 8 is in a state in which the inside of the needle guide hole 32a of the main valve body 3 and the inside of the guide hole 2A of the guide member 2 are electrically connected to the sub valve chamber 3R, and the tapered portion 41a is in contact with the step portion 3a of the main valve body 3. However, the back pressure on the needle valve 4 is equalized to that of the auxiliary valve chamber 3R.

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。 FIG. 11 is an enlarged vertical cross-sectional view of a main part of the electric valve of the sixth embodiment in the small flow rate control range 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. Also in the sixth embodiment, the small flow rate control is performed at the first throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a, and at the time of this small flow rate control, the needle valve 4 is the main valve body. By pressing 3 toward the main valve seat 13, the controllability of the small flow rate region is improved without the main valve body 3 vibrating, as in the first embodiment. The groove 9 is formed from the outer peripheral side of the guide boss portion 41 to the base of the straight portion 42a of the needle portion 42. Similar to each of the above-described embodiments, the small flow rate control is performed by flowing a constant flow rate of the refrigerant through the first throttle portion between the straight portion 42a of the needle portion 42 and the auxiliary valve port 33a. The groove 9 is in a state in which the inside of the needle guide hole 32a of the main valve body 3 and the inside of the guide hole 2A of the guide member 2 are electrically connected to the sub valve chamber 3R, and the tapered portion 41a is in contact with the step portion 3a of the main valve body 3. However, the back pressure on the needle valve 4 is equalized to that of the auxiliary valve chamber 3R.

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. Refrigeration cycle systems are used, for example, in air conditioners such as home air conditioners. The electric valve 100 of the above embodiment is between the first indoor side heat exchanger 91 (operating as a dehumidifying cooler) and the second indoor side heat exchanger 92 (operating as a dehumidifying heater) of the air conditioner. It is provided and, together with the compressor 95, the four-way valve 96, the outdoor heat exchanger 94 and the electronic expansion valve 93, constitutes a heat pump type refrigeration cycle. The first indoor side heat exchanger 91, the second indoor side heat exchanger 92, and the electric 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. It constitutes a 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 electric valve 100 of the embodiment as a dehumidifying valve, the main valve body is fully opened during cooling or heating other than during dehumidification, and the first chamber heat exchanger 91 and the second chamber heat exchanger 92 are in one chamber. It is said to be a heat exchanger. The integrated indoor heat exchanger and outdoor heat exchanger 94 alternately function as an "evaporator" and a "condenser". That is, the electric valve 93 as the 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 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 embodiment, the electric valve 100 used in an air conditioner such as a home air conditioner has been illustrated, but the electric valve of the present invention is not limited to the home air conditioner, and may be a commercial air conditioner. It can be applied not only to air conditioners but also to various refrigerators.

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。 Further, in the above-described embodiment, an example in which a taber portion as an abutting portion is formed on the needle valve side and a step portion as an abutting portion is formed on the main valve body side has been described. A portion may be formed, and a mortar-shaped taber portion may be formed on the main valve body side so as to face the columnar step portion. Further, in the above-described embodiment, the second throttle portion formed in the main valve body, the main valve seat, the step portion, or the needle valve is described as a groove configuration, but the second throttle portion is limited to the groove. Instead, it may be a second throttle portion having 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。 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. However, the specific configuration is not limited to these embodiments, and the present invention is not limited to these embodiments. It is included in the present invention even if there is a design change or the like within a range not deviating from the gist.

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 1st joint pipe 12 2nd joint pipe 13 Main valve seat 13a Main valve port 14 Case 2 Guide member 2A Guide hole 21 Press-fitting part 22 Guide part 23 Guide part 24 Holder part 24a Female thread part 25 Flange Part 3 Main valve body 3R Sub valve chamber 3a Step part (contact part)
31 Main valve part 32 Holding part 32a Needle guide hole 32b Conduction hole 33 Sub valve seat 33a Sub valve port 34 Retainer 35 Main valve spring 4 Needle valve (secondary valve body)
41 Guide boss 41a Tapered part (contact part)
42 Needle part 43 Washer 5 Drive part 5A Stepping motor 51 Rotor shaft 51a Male thread part 52 Magnet rotor 53 Stator coil 54 Spring receiver 55 Coil spring 5B Thread feed mechanism 5C Stopper mechanism L Axis line 6 Groove 6'Groove 4'Needle valve (secondary valve body) )
41'Guide boss part 42 Needle part 43 Cylindrical part 44 Tapered part (contact part)
7a Spring receiver 7 Coil spring 4 ″ Needle valve (secondary valve body)
41 ″ Guide boss 42 Needle 43 ″ Connecting rod 8 Groove 9 Groove 91 1st indoor heat exchanger 92 2nd indoor heat exchanger 93 Electronic expansion valve 94 Outdoor heat exchanger 95 Compressor 96 Four-way valve 100 Electric valve

Claims (9)

弁本体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、
前記主弁体が前記主弁座に着座した状態において、前記副弁体が前記副弁座と当接することなく、前記副弁体が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。 It is provided with a main valve body that is close to or separated from the main valve seat formed on the periphery of the main valve port provided in the main valve chamber of the valve body, and a sub valve provided in the sub valve chamber inside the main valve body. A two-stage electric valve having a sub-valve seat formed on the periphery of a port and a sub-valve body that is close to or separated from the port.
In a state where the main valve body is seated on the main valve seat, the sub valve body comes into contact with the main valve body without the sub valve body coming into contact with the sub valve seat, so that the sub valve body is brought into contact with the main valve body. An electric valve characterized in that the main valve body is pressed against the main valve seat. 前記副弁室側の前記当接部より下側に、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 electric valve according to claim 1, wherein a conduction hole for communicating the main valve chamber and the sub-valve chamber is formed below the contact portion on the sub-valve chamber side. 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または２に記載の電動弁。 One of the contact portions between the sub-valve body and the main valve body is a tapered portion having the axis of the sub-valve port as the central axis, and the other is a step portion having the axis as the central axis. The electric valve according to claim 1 or 2. 前記副弁体と前記主弁体との前記当接部は、前記副弁体に設けられたフランジ部と前記主弁体に設けられた段部との間に設置されたバネを介して当接されることを特徴とする請求項１または２に記載の電動弁。 The contact portion between the sub-valve body and the main valve body is contacted via a spring installed between a flange portion provided on the sub-valve body and a step portion provided on the main valve body. The electric valve according to claim 1 or 2, characterized in that they are in contact with each other. 前記弁室からガイド部材のフランジ部に設けた前記軸線方向の孔を通って、ガイド部材のガイド部に設けた連通孔からガイド部内を通り、前記副弁体外周と前記主弁体内周との隙間を通って前記副弁室の下部に達する連通路が形成されることを特徴とする請求項１乃至４のいずれか一項に記載の電動弁。 From the valve chamber, through the axial hole provided in the flange portion of the guide member, through the communication hole provided in the guide portion of the guide member, through the guide portion, the outer periphery of the sub-valve body and the inner circumference of the main valve. The electric valve according to any one of claims 1 to 4, wherein a communication passage is formed to reach the lower part of the auxiliary valve chamber through the gap. 前記副弁体のニードル部と前記副弁ポートとの隙間からなる第１の絞り部が形成されていることを特徴とする請求項１乃至５のいずれか一項に記載の電動弁。 The electric valve according to any one of claims 1 to 5, wherein a first throttle portion formed by a gap between the needle portion of the sub-valve body and the sub-valve port is formed. 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６に記載の電動弁。 The electric valve according to claim 6, wherein a second throttle portion is formed on the main valve seat or the main valve body, and / and on 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７に記載の電動弁。 The electric valve according to claim 7, wherein the second throttle portion is formed of 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乃至８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 dehumidifying valve provided in the indoor heat exchanger. A refrigeration cycle system comprising the above, wherein the electric valve according to any one of claims 1 to 8 is used as the dehumidification valve.
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