JP2021110401A - Motor-operated valve - Google Patents

Motor-operated valve Download PDF

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Publication number
JP2021110401A
JP2021110401A JP2020003105A JP2020003105A JP2021110401A JP 2021110401 A JP2021110401 A JP 2021110401A JP 2020003105 A JP2020003105 A JP 2020003105A JP 2020003105 A JP2020003105 A JP 2020003105A JP 2021110401 A JP2021110401 A JP 2021110401A
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valve
shaft
diameter
flow path
chamber
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JP7150345B2 (en
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将志 矢沢
Masashi Yazawa
将志 矢沢
真一郎 大鹿
Shinichiro OSHIKA
真一郎 大鹿
泰利 猪野
Yasutoshi Ino
泰利 猪野
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Fujikoki Corp
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Fujikoki Corp
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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
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/44—Details of seats or valve members of double-seat valves
    • F16K1/443—Details of seats or valve members of double-seat valves the seats being in series
    • 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
    • F16K1/52—Means for additional adjustment of the rate of flow
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • F16K27/0254—Construction of housing; Use of materials therefor of lift valves with conical shaped valve members
    • 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
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/08—Guiding yokes for spindles; Means for closing housings; Dust caps, e.g. for tyre valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K47/00—Means in valves for absorbing fluid energy
    • F16K47/02—Means in valves for absorbing fluid energy for preventing water-hammer or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)
  • Valve Housings (AREA)
  • Lift Valve (AREA)

Abstract

To provide a motor-operated valve capable of performing fluid control of a small flow volume and fluid control of a large flow volume with respect to fluid flowing in the same direction, and enabling a valve stem thereof to be easily positioned and adjusted.SOLUTION: A motor-operated valve is configured in such a manner that a lift amount of a valve stem has a first range in which a flow channel cross-sectional area between a flow channel adjustment portion and a small-diameter valve port is changed while a moving valve seat body is seated on a large-diameter valve port, and a second range in which a flow channel cross-sectional area between the moving valve seat body and the large-diameter valve port is changed while the moving valve seat body is latched to an engagement portion, a prescribed clearance is formed between the flow channel adjustment portion and the small-diameter valve port when the flow channel adjustment portion is moved to a lower end position located on the a most small-diameter valve port side in the first range, piping for supplying fluid is connected to a first valve chest, and a communication hole communicating the first valve chest and a second valve chest is formed above an inner peripheral upper end of the piping.SELECTED DRAWING: Figure 11

Description

本発明は、電動弁に関する。 The present invention relates to an electric valve.

従来から、例えば流体の配管系統の途中に介在させて、流体の流路の開閉や流量制御を行う機器として電動弁が使用されている。このような電動弁においては、流量制御を正確に行わせるために、弁本体に装着されたステッピングモータなどの駆動源により弁体を駆動させている。 Conventionally, an electric valve has been used as a device for opening / closing a fluid flow path and controlling a flow rate by interposing it in the middle of a fluid piping system, for example. In such an electric valve, the valve body is driven by a drive source such as a stepping motor mounted on the valve body in order to accurately control the flow rate.

特許文献１には、正方向においては小流量の流体を流し、また逆方向においては大流量の流体を流すことが可能な電動弁において、可動弁座体をフロート型の逆止弁体としても機能させる技術が開示されている。 According to Patent Document 1, in an electric valve capable of flowing a small flow rate fluid in the forward direction and a large flow rate fluid in the reverse direction, the movable valve seat may be used as a float type check valve body. The technology to make it work is disclosed.

特開２０１３−２４１９５８号公報Japanese Unexamined Patent Publication No. 2013-241958

ここで、特許文献１の電動弁ではその構成上、同じ方向に流れる流体について、小流量の流体制御と大流量の流体制御を行うことができないという問題がある。 Here, the electric valve of Patent Document 1 has a problem that it is not possible to control a small flow rate of a fluid and a large flow rate of a fluid flowing in the same direction due to its configuration.

また、特に小流量の流体制御を高精度に行うには、弁軸の位置決めが重要となるが、特許文献１の電動弁では、部品の製造誤差と組み付け誤差の影響が大きく、位置決め調整に手間がかかるという問題もある。また、液体とガスが混合した冷媒の流体制御を行う電動弁において、異音を抑制したいという要請もある。 Further, positioning of the valve shaft is particularly important for high-precision fluid control of a small flow rate, but the electric valve of Patent Document 1 is greatly affected by the manufacturing error of parts and the assembly error, and it is troublesome to adjust the positioning. There is also the problem that it takes. There is also a demand for suppressing abnormal noise in an electric valve that controls the fluid of a refrigerant in which a liquid and a gas are mixed.

本発明は、同じ方向に流れる流体について、小流量の流体制御と大流量の流体制御を行うことが可能であり、弁軸の位置決め調整が容易な電動弁を提供することを目的とする。 An object of the present invention is to provide an electric valve capable of performing a small flow rate fluid control and a large flow rate fluid control for a fluid flowing in the same direction, and easily positioning and adjusting the valve shaft.

本発明にかかる電動弁は、
第１弁室及び大径弁口を備えた弁本体と、
前記第１弁室に挿通され、流路調整部と係合部と段差部とが設けられた弁軸と、
前記弁軸を前記大径弁口に接離する方向に変位させることによって、リフト量を変化させることが可能な弁軸駆動部と、
前記第１弁室内で前記弁軸の変位方向に移動可能に配置され、第２弁室および前記第２弁室につながる小径弁口を備えた移動弁座体と、を有し、
前記弁軸の前記リフト量は、前記移動弁座体が前記大径弁口に着座した状態で前記流路調整部と前記小径弁口との間の流路断面積を変化させる第１の範囲と、前記移動弁座体が前記係合部に係止された状態で前記移動弁座体と前記大径弁口との間の流路断面積を変化させる第２の範囲と、を有するように構成され、
前記第１の範囲内において前記流路調整部が最も前記小径弁口側に移動した下端位置のとき、前記流路調整部と前記小径弁口との間に所定の隙間を有し、
前記第１弁室には流体供給用の配管が接続されており、
前記第１弁室と前記第２弁室とを連通する連通孔が、前記配管の内周上端よりも上方に設けられていることを特徴とする。 The electric valve according to the present invention is
A valve body equipped with a first valve chamber and a large-diameter valve port,
A valve shaft inserted into the first valve chamber and provided with a flow path adjusting portion, an engaging portion, and a step portion.
A valve shaft drive unit capable of changing the lift amount by displacing the valve shaft in a direction in which the valve shaft is brought into contact with or separated from the large-diameter valve port.
It has a mobile valve seat body that is movably arranged in the first valve chamber in the displacement direction of the valve shaft and has a second valve chamber and a small-diameter valve opening that connects to the second valve chamber.
The lift amount of the valve shaft is a first range in which the flow path cross-sectional area between the flow path adjusting portion and the small diameter valve port is changed while the moving valve seat body is seated on the large diameter valve port. And a second range for changing the flow path cross-sectional area between the moving valve seat and the large-diameter valve port in a state where the moving valve seat is locked to the engaging portion. Consists of
When the flow path adjusting portion is at the lower end position where the flow path adjusting portion is most moved to the small diameter valve opening side within the first range, a predetermined gap is provided between the flow path adjusting portion and the small diameter valve opening.
A fluid supply pipe is connected to the first valve chamber.
A communication hole for communicating the first valve chamber and the second valve chamber is provided above the upper end of the inner circumference of the pipe.

本発明の電動弁によれば、同じ方向に流れる流体について、小流量の流体制御と大流量の流体制御を行うことが可能であり、弁軸の位置決め調整が容易な電動弁を提供することができる。 According to the electric valve of the present invention, it is possible to perform a small flow rate fluid control and a large flow rate fluid control for a fluid flowing in the same direction, and it is possible to provide an electric valve in which the positioning and adjustment of the valve shaft can be easily performed. can.

図１は、第１実施形態の電動弁を示す縦断面図である。FIG. 1 is a vertical cross-sectional view showing the electric valve of the first embodiment. 図２は、本実施形態の電動弁の流量測定を示す図であり、横軸に、ロータ３０を回転させるために印加される制御パルス数をとり、縦軸に供給側円管Ｔ１から排出側円管Ｔ２へと流れる冷媒の量をとって示している。FIG. 2 is a diagram showing the flow rate measurement of the electric valve of the present embodiment. The horizontal axis represents the number of control pulses applied to rotate the rotor 30, and the vertical axis represents the discharge side from the supply side circular pipe T1. The amount of the refrigerant flowing into the circular tube T2 is taken and shown. 図３は、図１に示す電動弁の弁室の周辺を示す拡大断面図であり、図２の点Ａに対応する位置に弁軸が位置する状態を示している。FIG. 3 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 1, and shows a state in which the valve shaft is located at a position corresponding to a point A in FIG. 図４は、弁部の周辺を拡大して示す図であり、図２の点Ａに対応する位置に弁軸が位置する状態を示している。FIG. 4 is an enlarged view showing the periphery of the valve portion, and shows a state in which the valve shaft is located at a position corresponding to the point A in FIG. 図５は、図１に示す電動弁の弁室の周辺を示す拡大断面図であり、図２の点Ｂに対応する位置に弁軸が位置する状態を示している。FIG. 5 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 1, and shows a state in which the valve shaft is located at a position corresponding to the point B in FIG. 図６は、弁部の周辺を拡大して示す図であり、図２の点Ｂに対応する位置に弁軸が位置する状態を示している。FIG. 6 is an enlarged view showing the periphery of the valve portion, and shows a state in which the valve shaft is located at a position corresponding to the point B in FIG. 図７は、図１に示す電動弁の弁室の周辺を示す拡大断面図であり、図２の点Ｃに対応する位置に弁軸が位置する状態を示している。FIG. 7 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 1, and shows a state in which the valve shaft is located at a position corresponding to a point C in FIG. 図８は、弁部の周辺を拡大して示す図であり、図２の点Ｃに対応する位置に弁軸が位置する状態を示している。FIG. 8 is an enlarged view showing the periphery of the valve portion, and shows a state in which the valve shaft is located at a position corresponding to the point C in FIG. 図９は、図１に示す電動弁の弁室の周辺を示す拡大断面図であり、図２の点Ｄに対応する位置に弁軸が位置する状態を示している。FIG. 9 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 1, and shows a state in which the valve shaft is located at a position corresponding to a point D in FIG. 図１０は、第２実施形態の電動弁における弁室の周辺を示す拡大断面図であり、図２の点Ａ’に対応する位置に弁軸が位置する状態を示している。FIG. 10 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve of the second embodiment, and shows a state in which the valve shaft is located at a position corresponding to a point A'in FIG. 図１１は、第３実施形態の電動弁を示す縦断面図である。FIG. 11 is a vertical cross-sectional view showing the electric valve of the third embodiment. 図１２は、図１１に示す電動弁の弁室の周辺を示す拡大断面図である。FIG. 12 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 図１３は、第４実施形態の電動弁を示す縦断面図である。FIG. 13 is a vertical cross-sectional view showing the electric valve of the fourth embodiment. 図１４は、図１３に示す電動弁の弁室の周辺を示す拡大断面図である。FIG. 14 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 図１５は、第５実施形態の電動弁を示す縦断面図である。FIG. 15 is a vertical cross-sectional view showing the electric valve of the fifth embodiment. 図１６は、図１５に示す電動弁の弁室の周辺を示す拡大断面図である。FIG. 16 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve shown in FIG. 図１７は、第６実施形態の電動弁の弁室の周辺を示す拡大断面図である。FIG. 17 is an enlarged cross-sectional view showing the periphery of the valve chamber of the electric valve of the sixth embodiment.

以下、本発明に係る電動弁の実施形態を、図面を参照しながら説明する。なお、本明細書では、ロータから弁座に向かう方向を下方とし、その逆方向を上方とする。電動弁は、下方を重力方向として使用されることが望ましい。 Hereinafter, embodiments of the electric valve according to the present invention will be described with reference to the drawings. In the present specification, the direction from the rotor to the valve seat is downward, and the opposite direction is upward. It is desirable that the electric valve be used with the lower part as the direction of gravity.

［第１実施形態］
図１は、第１実施形態の電動弁１０を示す縦断面図である。自動車等の冷凍サイクル等における冷媒（流体）の流量制御を行う電動弁１０は、弁座部材６０と、弁座部材６０を取り付けた弁本体２０と、弁本体２０に取り付けられて弁軸２４を駆動させるロータ３０を内蔵するキャン４０と、キャン４０に外嵌されロータ３０を回転駆動するステータ５０とを備えている。電動弁１０の軸線をＬとする。 [First Embodiment]
FIG. 1 is a vertical cross-sectional view showing the electric valve 10 of the first embodiment. The electric valve 10 that controls the flow rate of the refrigerant (fluid) in a refrigeration cycle of an automobile or the like includes a valve seat member 60, a valve body 20 to which the valve seat member 60 is attached, and a valve shaft 24 attached to the valve body 20. A can 40 having a built-in rotor 30 to be driven and a stator 50 fitted in the can 40 to rotate the rotor 30 are provided. Let L be the axis of the electric valve 10.

キャン４０の円筒状部分の外周には、それぞれ一対のボビン５２とステータコイル５３およびこれらを囲うヨーク５１が配置され、その外周を樹脂モールドカバー５６によって覆うことによりステータ５０が形成されている。本実施形態では、樹脂モールドカバー５６は、キャン４０の上部を含めて覆っているが、ヨーク５１の周囲のみを覆うようにしてもよい。ロータ３０とステータ５０とによりステッピングモータを構成している。 A pair of bobbins 52, a stator coil 53, and a yoke 51 surrounding them are arranged on the outer circumference of the cylindrical portion of the can 40, and the stator 50 is formed by covering the outer circumference with a resin mold cover 56. In the present embodiment, the resin mold cover 56 covers including the upper part of the can 40, but may cover only the periphery of the yoke 51. A stepping motor is composed of a rotor 30 and a stator 50.

ステータコイル５３は、基板ＣＢ及びコネクタＣＮを介して、外部の電源回路（不図示）に接続されている。 The stator coil 53 is connected to an external power supply circuit (not shown) via a substrate CB and a connector CN.

キャン４０はステンレスなどの非磁性の金属から形成され、有底円筒状をしている。キャン４０の開放した下端は、後述するように弁本体２０の上端に溶接されて固着されている。 The can 40 is made of a non-magnetic metal such as stainless steel and has a bottomed cylindrical shape. The open lower end of the can 40 is welded and fixed to the upper end of the valve body 20 as described later.

略円筒状の弁軸２４は、ステンレス又は真鍮などから形成され、上端側の第１軸部２４ａと、第１軸部２４ａより大径の第２軸部２４ｂと、第２軸部２４ｂより小径の第３軸部２４ｃと、第３軸部２４ｃより小径の第４軸部２４ｄと、下端側の弁部２４ｅとを同軸に連設してなる。流路調整部としての弁部２４ｅは、先端側に向かうにつれて小径となるテーパ形状を有している。第２軸部２４ｂと第３軸部２４ｃとの間に、上方段部（段差部）２４ｆが形成され、第３軸部２４ｃと第４軸部２４ｄとの間に、下方段部２４ｇが形成されている。 The substantially cylindrical valve shaft 24 is formed of stainless steel, brass, or the like, and has a first shaft portion 24a on the upper end side, a second shaft portion 24b having a diameter larger than that of the first shaft portion 24a, and a diameter smaller than that of the second shaft portion 24b. The third shaft portion 24c, the fourth shaft portion 24d having a diameter smaller than that of the third shaft portion 24c, and the valve portion 24e on the lower end side are coaxially provided. The valve portion 24e as the flow path adjusting portion has a tapered shape in which the diameter becomes smaller toward the tip side. An upper step portion (step portion) 24f is formed between the second shaft portion 24b and the third shaft portion 24c, and a lower step portion 24g is formed between the third shaft portion 24c and the fourth shaft portion 24d. Has been done.

略円筒状の弁軸ホルダ３２は、キャン４０内において、弁軸２４の上端側を収容するように配置されている。弁軸ホルダ３２の上端は、弁軸２４の第１軸部２４ａの上端が圧入固定されたプッシュナット３３により接合されている。 The substantially cylindrical valve shaft holder 32 is arranged in the can 40 so as to accommodate the upper end side of the valve shaft 24. The upper end of the valve shaft holder 32 is joined by a push nut 33 in which the upper end of the first shaft portion 24a of the valve shaft 24 is press-fitted and fixed.

プッシュナット３３の外周に沿って、圧縮コイルばねで構成される復帰ばね３５を取付けている。復帰ばね３５は、詳細を後述するガイドブッシュ２６の固定ねじ部２５と弁軸ホルダ３２の移動ねじ部３１との螺合が外れたときに、キャン４０の頂部内面に当接して固定ねじ部２５と移動ねじ部３１との螺合を復帰させるように付勢する機能を有する。 A return spring 35 composed of a compression coil spring is attached along the outer circumference of the push nut 33. When the fixing screw portion 25 of the guide bush 26 and the moving screw portion 31 of the valve shaft holder 32 are unscrewed, the return spring 35 comes into contact with the inner surface of the top of the can 40 and the fixing screw portion 25 It has a function of urging the screw to restore the screwing with the moving screw portion 31.

キャン４０に対して隙間を開けて配置されたロータ３０と、弁軸ホルダ３２とは、支持リング３６を介して結合されている。より具体的に支持リング３６は、ロータ３０の成形時にインサートされた黄銅製の金属リングで構成されており、支持リング３６の内周孔部に弁軸ホルダ３２の上部突部が嵌合し、上部突部の外周をかしめ固定してロータ３０、支持リング３６及び弁軸ホルダ３２を結合している。 The rotor 30 arranged with a gap with respect to the can 40 and the valve shaft holder 32 are connected via a support ring 36. More specifically, the support ring 36 is composed of a metal ring made of copper inserted at the time of molding the rotor 30, and the upper protrusion of the valve shaft holder 32 is fitted into the inner peripheral hole of the support ring 36, and the upper protrusion is formed. The outer circumference of the portion is caulked and fixed to connect the rotor 30, the support ring 36, and the valve shaft holder 32.

弁軸ホルダ３２の外周には、ストッパ機構の一方を構成する上ストッパ体３７が固着されている。上ストッパ体３７はリング状の樹脂より構成され、下方に向けて板状の上ストッパ片３７ａが突設されている。 An upper stopper body 37 constituting one of the stopper mechanisms is fixed to the outer circumference of the valve shaft holder 32. The upper stopper body 37 is made of a ring-shaped resin, and a plate-shaped upper stopper piece 37a is projected downward.

円筒状のガイドブッシュ２６が、弁軸ホルダ３２と弁軸２４との間に配置されている。ガイドブッシュ２６の下端は、後述するホルダ２２０の内周に圧入により嵌合している。ガイドブッシュ２６の外周には、ストッパ機構の他方を構成する下ストッパ体２７が固着されている。下ストッパ体２７はリング状の樹脂より構成され、上方に板状の下ストッパ片２７ａが突設されており、上記した上ストッパ片３７ａと係合可能となっている。 A cylindrical guide bush 26 is arranged between the valve shaft holder 32 and the valve shaft 24. The lower end of the guide bush 26 is press-fitted into the inner circumference of the holder 220, which will be described later. A lower stopper body 27 constituting the other side of the stopper mechanism is fixed to the outer periphery of the guide bush 26. The lower stopper body 27 is made of a ring-shaped resin, and a plate-shaped lower stopper piece 27a is projected above the lower stopper body 27 so that the lower stopper body 27 can be engaged with the above-mentioned upper stopper piece 37a.

下ストッパ体２７はガイドブッシュ２６の外周に形成された螺旋溝部分２６ａに射出成形により固着され、上ストッパ体３７は弁軸ホルダ３２の外周に形成された螺旋溝部分３２ｂに射出成形により固着されている。 The lower stopper body 27 is fixed to the spiral groove portion 26a formed on the outer periphery of the guide bush 26 by injection molding, and the upper stopper body 37 is fixed to the spiral groove portion 32b formed on the outer periphery of the valve shaft holder 32 by injection molding. ing.

弁軸ホルダ３２の内面に移動ねじ部３１が形成されており、ガイドブッシュ２６の外周に形成された固定ねじ部２５と螺合している。移動ねじ部３１と固定ねじ部２５により構成されるねじ送り機構と、ロータ３０とにより、弁軸２４を軸線Ｌ方向に進退動させる弁軸駆動部を構成する。 A moving screw portion 31 is formed on the inner surface of the valve shaft holder 32, and is screwed with a fixing screw portion 25 formed on the outer periphery of the guide bush 26. A screw feed mechanism composed of a moving screw portion 31 and a fixing screw portion 25, and a rotor 30 constitute a valve shaft driving unit that moves the valve shaft 24 forward and backward in the axis L direction.

弁軸２４は、弁軸ホルダ３２の軸線Ｌに沿って上下動可能に嵌挿されており、弁軸ホルダ３２内に縮装された圧縮コイルばね３４によって下方に付勢されている。ガイドブッシュ２６の側面には、弁室２１とキャン４０内の圧力均衡を図る均圧孔３２ａが形成されている。 The valve shaft 24 is fitted and inserted so as to be vertically movable along the axis L of the valve shaft holder 32, and is urged downward by a compression coil spring 34 compressed in the valve shaft holder 32. A pressure equalizing hole 32a for balancing pressure in the valve chamber 21 and the can 40 is formed on the side surface of the guide bush 26.

弁本体２０は、肉厚や外径が均一な金属製の直線パイプから形成される筒状本体２１０と、筒状本体２１０の上端側内周に圧入されるホルダ２２０と、弁座部材６０とを有する。ガイド部であるホルダ２２０は、中空円筒部２２１と、中空円筒部２２１の内周中間に形成された仕切り壁２２２とを有する。中空円筒部２２１は、上端近傍に拡径した拡径部２２３を有する。拡径部２２３が、筒状本体２１０の上端に形成された薄肉部２１２に嵌合することで、筒状本体２１０とホルダ２２０との軸線Ｌ方向の位置決めが行われる。また、拡径部２２３は筒状本体２１０に嵌合した状態で、その上端が突出しており、後述するキャン４０との接合の際に接合ガイドとして機能する。 The valve body 20 includes a tubular body 210 formed of a straight metal pipe having a uniform wall thickness and outer diameter, a holder 220 press-fitted into the inner circumference of the upper end side of the tubular body 210, and a valve seat member 60. Has. The holder 220, which is a guide portion, has a hollow cylindrical portion 221 and a partition wall 222 formed in the middle of the inner circumference of the hollow cylindrical portion 221. The hollow cylindrical portion 221 has a diameter-expanded portion 223 whose diameter is expanded near the upper end. By fitting the enlarged diameter portion 223 into the thin-walled portion 212 formed at the upper end of the tubular main body 210, the tubular main body 210 and the holder 220 are positioned in the axis L direction. Further, the diameter-expanded portion 223 has a protruding upper end thereof in a state of being fitted to the tubular main body 210, and functions as a joining guide at the time of joining with the can 40 described later.

中空円筒部２２１の内周に、仕切り壁２２２に下端を突き当てるようにして、ガイドブッシュ２６が圧入されている。仕切り壁２２２の中央には、円形穴２２５が形成されている。 The guide bush 26 is press-fitted into the inner circumference of the hollow cylindrical portion 221 so that the lower end abuts against the partition wall 222. A circular hole 225 is formed in the center of the partition wall 222.

筒状本体２１０の下端には、弁座部材６０がロウ付けにより固着されている。弁座部材６０の下端には、筒状本体２１０の内径より大きい外径を有する鍔部６４が形成されており、鍔部６４を筒状本体２１０の下端に突き当てることで、筒状本体２１０に対して軸線Ｌ方向における弁座部材６０の位置決めを行える。 A valve seat member 60 is fixed to the lower end of the tubular main body 210 by brazing. A collar portion 64 having an outer diameter larger than the inner diameter of the tubular main body 210 is formed at the lower end of the valve seat member 60, and by abutting the flange portion 64 against the lower end of the tubular main body 210, the tubular main body 210 is formed. The valve seat member 60 can be positioned with respect to the axis L direction.

中空円筒形状を有する弁座部材６０は、その上端に縮径した薄肉円筒部６１を有し、また薄肉円筒部６１の上端内周側に、上方に向かうにつれて拡径したテーパ状の弁座（大径弁口）６２を有している。弁座部材６０の内周中間には環状に突出した突出部６３を形成している。突出部６３の下面に上端を突き当てるようにして、排出側円管Ｔ２が弁座部材６０の内周に嵌合しロウ付けにより固着されている。薄肉円筒部６１の内径を、排出側円管Ｔ２の内径より大きくすることで、通過する冷媒の最大量を増大させることができる。 The valve seat member 60 having a hollow cylindrical shape has a thin-walled cylindrical portion 61 having a reduced diameter at the upper end thereof, and a tapered valve seat (a tapered valve seat whose diameter increases upward toward the inner peripheral side of the upper end of the thin-walled cylindrical portion 61). It has a large-diameter valve port) 62. A protruding portion 63 that protrudes in an annular shape is formed in the middle of the inner circumference of the valve seat member 60. The discharge side circular pipe T2 is fitted to the inner circumference of the valve seat member 60 and fixed by brazing so that the upper end abuts against the lower surface of the protruding portion 63. By making the inner diameter of the thin-walled cylindrical portion 61 larger than the inner diameter of the discharge-side circular pipe T2, the maximum amount of the passing refrigerant can be increased.

筒状本体２１０の外周には円孔２１１が形成され、また円孔２１１に供給側円管Ｔ１が挿通されている。中心線Ｏを持つ供給側円管Ｔ１の先端が、弁座部材６０の薄肉円筒部６１の外周に当接するようにして位置決めされ、かかる状態で供給側円管Ｔ１が筒状本体２１０にロウ付けされている。弁室２１に連通する供給側円管Ｔ１内が第１流路を構成し、弁室２１に連通する排出側円管Ｔ２内が第２流路を構成する。なお、供給側円管Ｔ１の中心線Ｏは軸線Ｌに直交している。 A circular hole 211 is formed on the outer periphery of the tubular main body 210, and a supply-side circular tube T1 is inserted through the circular hole 211. The tip of the supply-side circular tube T1 having the center line O is positioned so as to abut on the outer circumference of the thin-walled cylindrical portion 61 of the valve seat member 60, and in this state, the supply-side circular tube T1 is brazed to the tubular main body 210. Has been done. The inside of the supply-side circular pipe T1 communicating with the valve chamber 21 constitutes the first flow path, and the inside of the discharge-side circular pipe T2 communicating with the valve chamber 21 constitutes the second flow path. The center line O of the supply-side circular tube T1 is orthogonal to the axis L.

筒状本体２１０内において、ホルダ２２０と弁座部材６０との間の空間を弁室２１とする。弁室２１には、移動弁座体７０が軸線Ｌ方向に沿って変位可能に配置されている。移動弁座体７０は、有頂円筒状のスリーブ７１と、スリーブ７１の下端に接合された円盤状のシート７２とを有する。 In the tubular main body 210, the space between the holder 220 and the valve seat member 60 is defined as the valve chamber 21. In the valve chamber 21, the moving valve seat 70 is displaceably arranged along the axis L direction. The mobile valve seat 70 has a climax cylindrical sleeve 71 and a disk-shaped seat 72 joined to the lower end of the sleeve 71.

スリーブ７１は、供給側円管Ｔ１に対向する高さ位置に、４つの横穴（連通孔ともいう）７１ａを周方向に等間隔に備え、また頂壁（隔壁ともいう）７１ｂの中央に円形開口７１ｃを形成している。 The sleeve 71 is provided with four horizontal holes (also referred to as communication holes) 71a at equal intervals in the circumferential direction at a height position facing the supply side circular pipe T1 and has a circular opening in the center of the top wall (also referred to as a partition wall) 71b. It forms 71c.

後述する図３を参照して、シート７２は、円盤部７２ａと、それより小径の短円筒部７２ｂとを連設しており、円盤部７２ａの上面に突き当てるようにして、短円筒部７２ｂの外周にスリーブ７１の下端が圧入により挿入されている。 With reference to FIG. 3, which will be described later, in the sheet 72, a disk portion 72a and a short cylindrical portion 72b having a smaller diameter are connected in series, and the short cylindrical portion 72b is abutted against the upper surface of the disk portion 72a. The lower end of the sleeve 71 is press-fitted into the outer periphery of the sleeve 71.

シート７２の円盤部７２ａの下面外周には、下方に向うにつれて縮径するテーパ状のシート面７２ｃが形成されており、弁座部材６０の弁座６２に着座可能となっている。シート７２の中央には、後述する図４を参照して、上端側の円筒孔（小径弁口）７２ｄと下端側のテーパ孔７２ｅとを連設してなる連通穴７２ｆが形成されている。円筒孔７２ｄに続いて漸次拡径するテーパ孔７２ｅを設けることで、ここを通過する冷媒の通過音を減少させ、電動弁１０の静穏化を図れる。ここでは、円筒孔７２ｄが弁口を構成する。 A tapered seat surface 72c whose diameter decreases downward is formed on the outer periphery of the lower surface of the disk portion 72a of the seat 72, and can be seated on the valve seat 62 of the valve seat member 60. A communication hole 72f formed by connecting a cylindrical hole (small diameter valve opening) 72d on the upper end side and a tapered hole 72e on the lower end side is formed in the center of the sheet 72 with reference to FIG. 4 described later. By providing the tapered hole 72e whose diameter gradually increases following the cylindrical hole 72d, the passing noise of the refrigerant passing through the tapered hole 72e can be reduced, and the electric valve 10 can be made quiet. Here, the cylindrical hole 72d constitutes the valve opening.

スリーブ７１の外径は、シート面７２ｃの最小内径より小さいと好ましく、それにより弁室２１の容積を大きく確保できる。また、比較的小径の円筒孔７２ｄを採用することで、スリーブ７１の内径を小さく抑えることができ、スリーブ７１の容積や開口断面積の低減を図り、また部品の軽量化を図ることができる。 The outer diameter of the sleeve 71 is preferably smaller than the minimum inner diameter of the seat surface 72c, whereby a large volume of the valve chamber 21 can be secured. Further, by adopting the cylindrical hole 72d having a relatively small diameter, the inner diameter of the sleeve 71 can be suppressed to be small, the volume of the sleeve 71 and the opening cross-sectional area can be reduced, and the weight of the parts can be reduced.

後述する図３を参照して、弁室２１内に挿通された弁軸２４は、第２軸部２４ｂがホルダ２２０の円形穴２２５に挿通され、第３軸部２４ｃがスリーブ７１の円形開口７１ｃに挿通される。スリーブ７１内において、第３軸部２４ｃと第４軸部２４ｄとの間の下方段部２４ｇに突き当てるようにして、係合部である環状部材７３が圧入により取り付けられている。なお、第４軸部２４ｄの上端部分（下方段部２４ｇ側の部分）は、それ以外の第４軸部２４ｄより直径が大きく形成され、環状部材７３が圧入できるようになっている。 With reference to FIG. 3, which will be described later, in the valve shaft 24 inserted into the valve chamber 21, the second shaft portion 24b is inserted into the circular hole 225 of the holder 220, and the third shaft portion 24c is the circular opening 71c of the sleeve 71. Is inserted into. In the sleeve 71, the annular member 73, which is an engaging portion, is attached by press fitting so as to abut against the lower step portion 24g between the third shaft portion 24c and the fourth shaft portion 24d. The upper end portion of the fourth shaft portion 24d (the portion on the lower step portion 24g side) is formed to have a larger diameter than the other fourth shaft portion 24d so that the annular member 73 can be press-fitted.

図１において、弁本体２０の筒状本体２１０の外周に、ステンレス板（ＳＵＳ板）をプレスにより成形して円筒状に形成した筒部２４０の端部を溶接またはロウ付けにより固着している。筒部２４０をステータ５０側から延在させた板ばね２４１に係合させることで、ステータ５０に対して弁本体２０の回り止めを行っている。 In FIG. 1, an end portion of a cylindrical portion 240 formed by molding a stainless plate (SUS plate) by a press is fixed to the outer periphery of a tubular main body 210 of the valve main body 20 by welding or brazing. By engaging the tubular portion 240 with the leaf spring 241 extending from the stator 50 side, the valve body 20 is prevented from rotating with respect to the stator 50.

（弁本体の組付）
まず、弁座部材６０を、筒状本体２１０の下端に鍔部６４が突き当たるまで挿入し、排出側円管Ｔ２を弁座部材６０の下端側開口に挿入する。一方、供給側円管Ｔ１を筒状本体２１０の円孔２１１に、その先端が弁座部材６０に突き当たるまで挿通する。その後、ロウ付けにより、弁座部材６０、供給側円管Ｔ１及び排出側円管Ｔ２が筒状本体２１０と一体になるように固着する。
その後、弁軸２４にスリーブ７１を接近させ、弁軸２４が円形開口７１ｃを貫通するようにして、スリーブ７１をホルダ２２０内に挿入する。 (Assembly of valve body)
First, the valve seat member 60 is inserted until the flange portion 64 abuts on the lower end of the tubular main body 210, and the discharge side circular pipe T2 is inserted into the lower end side opening of the valve seat member 60. On the other hand, the supply-side circular pipe T1 is inserted into the circular hole 211 of the tubular main body 210 until its tip abuts on the valve seat member 60. Then, by brazing, the valve seat member 60, the supply-side circular pipe T1 and the discharge-side circular pipe T2 are fixed so as to be integrated with the tubular main body 210.
After that, the sleeve 71 is brought close to the valve shaft 24 so that the valve shaft 24 penetrates the circular opening 71c, and the sleeve 71 is inserted into the holder 220.

次いで、第４軸部２４ｄに環状部材７３を圧入して、下方段部２４ｇに突き当てる。かかる状態で、スリーブ７１の下端にシート７２の短円筒部７２ｂを圧入する。こうして組み立てた、スリーブ７１、弁軸２４、環状部材７３および短円筒部７２ｂからなるスリーブ組立体を、パイプ製の筒状本体２１０に挿入する。ホルダ２２０に対してスリーブ７１は摺動可能となっている。その後、スリーブ組立体の弁軸２４を、筒状本体２１０の円形穴２２５に挿入した状態で、筒状本体２１０内にホルダ２２０を圧入する。このとき、ホルダ２２０の外径を一部縮径することで、圧入する際に印加する荷重を減少させることができる。さらにガイドブッシュ２６をホルダ２２０内に圧入し、下ストッパ体２７ａを取り付ける。また、ガイドブッシュ２６から突出した弁軸２４に圧縮コイルばね３４、弁軸ホルダ３２、下ストッパ体２７、ロータ３０およびプッシュナット３３等を組み付ける。 Next, the annular member 73 is press-fitted into the fourth shaft portion 24d and abutted against the lower step portion 24g. In this state, the short cylindrical portion 72b of the sheet 72 is press-fitted into the lower end of the sleeve 71. The sleeve assembly composed of the sleeve 71, the valve shaft 24, the annular member 73, and the short cylindrical portion 72b assembled in this manner is inserted into the tubular main body 210 made of a pipe. The sleeve 71 is slidable with respect to the holder 220. After that, the holder 220 is press-fitted into the tubular main body 210 with the valve shaft 24 of the sleeve assembly inserted into the circular hole 225 of the tubular main body 210. At this time, by partially reducing the outer diameter of the holder 220, the load applied at the time of press fitting can be reduced. Further, the guide bush 26 is press-fitted into the holder 220, and the lower stopper body 27a is attached. Further, the compression coil spring 34, the valve shaft holder 32, the lower stopper body 27, the rotor 30, the push nut 33, and the like are assembled to the valve shaft 24 protruding from the guide bush 26.

更に、キャン４０の下端を、筒状本体２１０の上端から突き出したホルダ２２０の拡径部２２３に嵌合させた状態で、突き合わせたキャン４０の下端と筒状本体２１０の上端とに対し、全周にわたってレーザ溶接を行って溶接部Ｗを形成する。これにより、キャン４０と筒状本体２２０との同軸性を確保しつつ、キャン４０とホルダ２２０と筒状本体２１０とが１か所で接合される。ホルダ２２０は外部に対して露出しないため、経年劣化などに対して有利である。また、別工程で予め組み立てておいたステータ５０をキャン４０の外周に装着する。以上で、電動弁１０の組み付けが完了する。 Further, in a state where the lower end of the can 40 is fitted to the enlarged diameter portion 223 of the holder 220 protruding from the upper end of the tubular main body 210, the lower end of the can 40 and the upper end of the tubular main body 210 are all abutted. Laser welding is performed over the circumference to form the welded portion W. As a result, the can 40, the holder 220, and the tubular main body 210 are joined in one place while ensuring the coaxiality between the can 40 and the tubular main body 220. Since the holder 220 is not exposed to the outside, it is advantageous against aging deterioration and the like. Further, the stator 50 pre-assembled in another process is mounted on the outer circumference of the can 40. This completes the assembly of the electric valve 10.

本実施形態によれば、スリーブ７１が、ホルダ２２０の中空円筒部２２１の内周でガイドされる構造であるため、筒状本体２１０の内周をガイドとして用いる必要がなくなり、筒状本体２１０を安価なパイプ等を用いて形成することができる。また、スリーブ７１の外径を中空円筒部２２１の内径に合わせて比較的小径とすることができるため、スリーブ７１と筒状本体２１０との間に、比較的大きな弁室２１を形成でき、それにより電動弁１０としての性能を向上させることができる。 According to the present embodiment, since the sleeve 71 has a structure in which the inner circumference of the hollow cylindrical portion 221 of the holder 220 is guided, it is not necessary to use the inner circumference of the tubular main body 210 as a guide, and the tubular main body 210 can be used. It can be formed by using an inexpensive pipe or the like. Further, since the outer diameter of the sleeve 71 can be made relatively small in accordance with the inner diameter of the hollow cylindrical portion 221, a relatively large valve chamber 21 can be formed between the sleeve 71 and the tubular main body 210. Therefore, the performance of the electric valve 10 can be improved.

（電動弁の動作）
図２は、本実施形態の電動弁１０の流量測定を示す図であり、横軸に、ロータ３０を回転させるために印加される制御パルス数をとり、縦軸に供給側円管Ｔ１から排出側円管Ｔ２へと流れる冷媒の量をとって示している。制御パルス数は、弁軸２４の相対変位量（リフト量）に相当する。図２において、点Ａから点Ｃまでの制御パルス数の範囲を、小流量の制御範囲（移動弁座体７０のシート面７２ｃが弁座６２に着座した状態で第４軸部２４ｄと円筒孔７２ｄの間の流路断面積を変化させる第１の範囲）とし、点Ｃから点Ｄを、大流量の制御範囲（移動弁座体７０が環状部材７３に係止された状態で移動弁座体７０のシート面７２ｃと弁座６２との間の流路断面積を変化させる第２の範囲）とする。 (Operation of electric valve)
FIG. 2 is a diagram showing the flow rate measurement of the electric valve 10 of the present embodiment. The horizontal axis represents the number of control pulses applied to rotate the rotor 30, and the vertical axis represents discharge from the supply-side circular tube T1. The amount of the refrigerant flowing to the side circular tube T2 is taken and shown. The number of control pulses corresponds to the relative displacement amount (lift amount) of the valve shaft 24. In FIG. 2, the range of the number of control pulses from the point A to the point C is set to the control range of the small flow rate (the fourth shaft portion 24d and the cylindrical hole with the seat surface 72c of the moving valve seat body 70 seated on the valve seat 62). The first range for changing the cross-sectional area of the flow path between 72d) is set, and the points C to D are set as the control range for a large flow rate (the moving valve seat 70 is locked to the annular member 73). A second range in which the cross-sectional area of the flow path between the seat surface 72c of the body 70 and the valve seat 62 is changed).

本実施の形態にかかる電動弁１０の動作について説明する。以下、弁軸２４と円筒孔７２ｄとの間の隙間（第１の隙間）により形成される流路断面積をＳ１とし、シート面７２ｃと弁座６２との間の隙間（第２の隙間）により形成される流路断面積をＳ２とする。
図１において、外部からコネクタＣＮおよび基板ＣＢを介して給電することにより、ステータ５０のステータコイル５３に通電を行って励磁すると、発生した磁力によりロータ３０に回転力が生じるため、弁本体２０に固着されたガイドブッシュ２６に対しロータ３０及び弁軸ホルダ３２が回転駆動される。 The operation of the electric valve 10 according to the present embodiment will be described. Hereinafter, the flow path cross-sectional area formed by the gap (first gap) between the valve shaft 24 and the cylindrical hole 72d is defined as S1, and the gap (second gap) between the seat surface 72c and the valve seat 62. Let S2 be the cross-sectional area of the flow path formed by.
In FIG. 1, when the stator coil 53 of the stator 50 is energized and excited by supplying power from the outside via the connector CN and the substrate CB, the generated magnetic force generates a rotational force in the rotor 30, so that the valve body 20 is subjected to a rotational force. The rotor 30 and the valve shaft holder 32 are rotationally driven with respect to the fixed guide bush 26.

これにより、ガイドブッシュ２６の固定ねじ部２５と、弁軸ホルダ３２の移動ねじ部３１とのねじ送り機構により、弁軸ホルダ３２がその軸線Ｌ方向に変位する。ステータコイル５３への通電により、弁軸ホルダ３２が下方に変位すると、重力に従い環状部材７３に係止された状態の移動弁座体７０は弁軸ホルダ３２とともに下方に変位する。さらに弁軸ホルダ３２を下方に変位させると、移動弁座体７０のシート面７２ｃが、弁座部材６０の弁座６２に着座する。この状態からさらに弁軸ホルダ３２を下方に変位させると環状部材７３と頂壁７１ｂが離れ、その後、弁軸２４の上方段部２４ｆがスリーブ７１の頂壁７１ｂの上面に突き当たり、シート面７２ｃをコイルばね３４の弾性力により弁座６２に押し当て、シート面７２ｃと弁座６２との間の冷媒の流れを遮断する。 As a result, the valve shaft holder 32 is displaced in the axis L direction by the screw feed mechanism between the fixing screw portion 25 of the guide bush 26 and the moving screw portion 31 of the valve shaft holder 32. When the valve shaft holder 32 is displaced downward by energizing the stator coil 53, the moving valve seat 70 in a state of being locked to the annular member 73 due to gravity is displaced downward together with the valve shaft holder 32. When the valve shaft holder 32 is further displaced downward, the seat surface 72c of the moving valve seat body 70 is seated on the valve seat 62 of the valve seat member 60. When the valve shaft holder 32 is further displaced downward from this state, the annular member 73 and the top wall 71b are separated from each other, and then the upper step portion 24f of the valve shaft 24 abuts on the upper surface of the top wall 71b of the sleeve 71, and the seat surface 72c is pressed. It is pressed against the valve seat 62 by the elastic force of the coil spring 34 to block the flow of the refrigerant between the seat surface 72c and the valve seat 62.

一方、図３，４に示すように、弁軸２４の上方段部２４ｆがスリーブ７１の頂壁７１ｂの上面に突き当たった状態で、第４軸部２４ｄの下端（弁部２４ｅの上端）が移動弁座体７０の円筒孔７２ｄの範囲内に位置する。ここでは、第４軸部２４ｄと円筒孔７２ｄとの軸線Ｌ方向の重なり量をδとする。なお、δ＝０ｍｍである場合も含む。このように、第１の範囲内において第４軸部２４ｄが最も円筒孔７２ｄ側に移動した下端位置のとき、第４軸部２４ｄと円筒孔７２ｄとの間に所定の隙間Ｓ３（０ｍｍを除く）が形成される。 On the other hand, as shown in FIGS. It is located within the range of the cylindrical hole 72d of the valve seat body 70. Here, the amount of overlap of the fourth shaft portion 24d and the cylindrical hole 72d in the axis L direction is defined as δ. The case where δ = 0 mm is also included. As described above, when the fourth shaft portion 24d is at the lower end position where the fourth shaft portion 24d is moved to the most cylindrical hole 72d side within the first range, a predetermined gap S3 (excluding 0 mm) is provided between the fourth shaft portion 24d and the cylindrical hole 72d. ) Is formed.

このとき、第４軸部２４ｄと円筒孔７２ｄとの隙間Ｓ３により形成される流路断面積Ｓ１が最小となるので、その流路断面積Ｓ１に応じた流量で冷媒が通過する。換言すれば、第４軸部２４ｄと円筒孔７２ｄとの隙間は完全に閉じることがなく、その間を最小流量の冷媒が流れることとなる。より具体的には、供給側円管Ｔ１から弁室２１に供給された冷媒は、スリーブ７１の横穴７１ａを介してスリーブ７１内部へと進入し、さらに第４軸部２４ｄと円筒孔７２ｄとの間を介して弁座部材６０の内部へと流れ、排出側円管Ｔ２を介して排出される。 At this time, since the flow path cross-sectional area S1 formed by the gap S3 between the fourth shaft portion 24d and the cylindrical hole 72d is minimized, the refrigerant passes at a flow rate corresponding to the flow path cross-sectional area S1. In other words, the gap between the fourth shaft portion 24d and the cylindrical hole 72d is not completely closed, and the minimum flow rate of the refrigerant flows between the gaps. More specifically, the refrigerant supplied from the supply-side circular pipe T1 to the valve chamber 21 enters the inside of the sleeve 71 through the lateral hole 71a of the sleeve 71, and further connects the fourth shaft portion 24d and the cylindrical hole 72d. It flows into the valve seat member 60 through the space and is discharged through the discharge side circular pipe T2.

本実施形態によれば、弁軸２４の上方段部２４ｆをスリーブ７１の頂壁７１ｂの上面に突き当てることで、円筒孔７２ｄに対する弁部２４ｅの軸線Ｌ方向の位置を定めることができ、これにより流量制御を精度よく行える。すなわち、弁部２４ｅの設計位置に対する実際の位置のばらつきは、各部品の製造誤差と組み付け誤差に応じて増大するため、例えばストッパなどを用いて弁部２４ｅの位置決めを行う構成では関連する部品が多くなり、実際の位置が大きくばらつくおそれがある。これに対し本実施形態では、円筒孔７２ｄを形成したシート７２と上方段部２４ｆとの間にはスリーブ７１しか介在しないので、ばらつきの要因を極力排除して、円筒孔７２ｄに対する弁部２４ｅの位置決めを精度よく行うことができる。 According to the present embodiment, by abutting the upper step portion 24f of the valve shaft 24 against the upper surface of the top wall 71b of the sleeve 71, the position of the valve portion 24e with respect to the cylindrical hole 72d in the axis L direction can be determined. Therefore, the flow rate can be controlled accurately. That is, the variation in the actual position of the valve portion 24e with respect to the design position increases according to the manufacturing error and the assembly error of each part. Therefore, in a configuration in which the valve portion 24e is positioned using, for example, a stopper, related parts are used. There is a risk that the actual position will vary greatly. On the other hand, in the present embodiment, since only the sleeve 71 is interposed between the sheet 72 forming the cylindrical hole 72d and the upper step portion 24f, the cause of variation is eliminated as much as possible, and the valve portion 24e with respect to the cylindrical hole 72d is provided. Positioning can be performed with high accuracy.

なお、弁軸２４の上方段部２４ｆがスリーブ７１の頂壁７１ｂの上面に突き当たった状態では、上ストッパ体３７は未だ下ストッパ体２７に当接しておらず、弁軸２４とスリーブ７１と共に、ロータ３０及び弁軸ホルダ３２はさらに回転下降する。このときは弁軸２４に対する弁軸ホルダ３２の相対的な下降変位は、圧縮コイルばね３４が圧縮されることにより吸収される。 In the state where the upper step portion 24f of the valve shaft 24 abuts on the upper surface of the top wall 71b of the sleeve 71, the upper stopper body 37 has not yet come into contact with the lower stopper body 27, and together with the valve shaft 24 and the sleeve 71, The rotor 30 and the valve shaft holder 32 further rotate and descend. At this time, the relative downward displacement of the valve shaft holder 32 with respect to the valve shaft 24 is absorbed by the compression of the compression coil spring 34.

その後、ロータ３０が更に回転して弁軸ホルダ３２が下降して、上ストッパ体３７の上ストッパ片３７ａが下ストッパ体２７の下ストッパ片２７ａに当接する。これらのストッパ片２７ａ、３７ａ同士の当接によって、ステータ５０への通電が継続されても、弁軸ホルダ３２の下降は強制的に停止される。 After that, the rotor 30 further rotates and the valve shaft holder 32 is lowered, and the upper stopper piece 37a of the upper stopper body 37 comes into contact with the lower stopper piece 27a of the lower stopper body 27. Due to the contact between the stopper pieces 27a and 37a, the lowering of the valve shaft holder 32 is forcibly stopped even if the stator 50 is continuously energized.

上ストッパ体３７と下ストッパ体２７とから構成されるストッパ機構は、ロータ３０の軸方向の全長内に配置されているため、ストッパ機構が機能しているときでもロータ３０や弁軸ホルダ３２が大きく傾いたりすることが少なく作動が安定し、次にロータ３０を逆転するときでも円滑に行うことができる。 Since the stopper mechanism composed of the upper stopper body 37 and the lower stopper body 27 is arranged within the entire length in the axial direction of the rotor 30, the rotor 30 and the valve shaft holder 32 can be held even when the stopper mechanism is functioning. The operation is stable with little inclination, and can be smoothly performed even when the rotor 30 is reversed next time.

次に、ステータ５０に逆方向の通電を行うと、ガイドブッシュ２６に対しロータ３０及び弁軸ホルダ３２が上記と逆方向に回転され、上記のねじ送り機構により、弁軸ホルダ３２が上方に変位する。このとき、弁室２１内の冷媒圧が、排出側円管Ｔ２内の冷媒圧より高いため、その差圧により移動弁座体７０が下方に付勢され、シート７２のシート面７２ｃが、弁座部材６０の弁座６２に着座したままとなる。 Next, when the stator 50 is energized in the opposite direction, the rotor 30 and the valve shaft holder 32 are rotated in the opposite directions to the guide bush 26, and the valve shaft holder 32 is displaced upward by the screw feed mechanism. do. At this time, since the refrigerant pressure in the valve chamber 21 is higher than the refrigerant pressure in the discharge side circular pipe T2, the moving valve seat 70 is urged downward by the differential pressure, and the seat surface 72c of the seat 72 becomes a valve. It remains seated on the valve seat 62 of the seat member 60.

したがって、シート面７２ｃと弁座６２との間に隙間は生じず、冷媒は専ら第４軸部２４ｄと円筒孔７２ｄとの間を通過することとなる。このため図５，６に示すように、弁軸２４の第４軸部２４ｄの下端が円筒孔７２ｄの上端に到達するまでは、流路断面積Ｓ１は最小のままであるため流量は変化しない。このとき、制御パルス数と流量との関係は、図２の点Ａから点Ｂまでの実線により表される。 Therefore, no gap is formed between the seat surface 72c and the valve seat 62, and the refrigerant passes exclusively between the fourth shaft portion 24d and the cylindrical hole 72d. Therefore, as shown in FIGS. 5 and 6, the flow rate does not change because the flow path cross-sectional area S1 remains the minimum until the lower end of the fourth shaft portion 24d of the valve shaft 24 reaches the upper end of the cylindrical hole 72d. .. At this time, the relationship between the number of control pulses and the flow rate is represented by the solid line from the point A to the point B in FIG.

図５，６に示す位置よりさらに、弁軸２４の弁部２４ｅが円筒孔７２ｄの上端から上方へと変位すると、テーパ状である弁部２４ｅと円筒孔７２ｄとの間の隙間が変化し、流路断面積Ｓ１（図８参照）が増大する。すなわち、流路断面積Ｓ１を通過する冷媒の流量は、移動弁座体７０と弁軸２４の相対変位量に応じて変化するため、小流量の流体制御を行うことができる。このとき、制御パルス数と流量との関係は、図２の点Ｂから点Ｃまでの実線により表される。 When the valve portion 24e of the valve shaft 24 is further displaced upward from the upper end of the cylindrical hole 72d from the position shown in FIGS. 5 and 6, the gap between the tapered valve portion 24e and the cylindrical hole 72d changes. The flow path cross-sectional area S1 (see FIG. 8) increases. That is, since the flow rate of the refrigerant passing through the flow path cross-sectional area S1 changes according to the relative displacement amount of the moving valve seat 70 and the valve shaft 24, it is possible to control the fluid with a small flow rate. At this time, the relationship between the number of control pulses and the flow rate is represented by a solid line from point B to point C in FIG.

更に続けてステータ５０に逆方向の通電を行うと、図７，８に示すように、環状部材７３がスリーブ７１の頂壁７１ｂの下面に当接し、それ以降、移動弁座体７０は弁軸２４に引き上げられる形で、上方に共に変位する。このため、図９に示すように、移動弁座体７０のシート面７２ｃが弁座部材６０の弁座６２から離間して、シート面７２ｃと弁座６２との間の隙間により比較的大きな流路断面積Ｓ２が形成される。 Further, when the stator 50 is continuously energized in the opposite direction, as shown in FIGS. It is pulled up to 24 and is displaced upward together. Therefore, as shown in FIG. 9, the seat surface 72c of the moving valve seat body 70 is separated from the valve seat 62 of the valve seat member 60, and a relatively large flow is caused by the gap between the seat surface 72c and the valve seat 62. The road cross-sectional area S2 is formed.

さらに、逆方向への通電を続行すると、弁軸２４の変位量に応じてシート面７２ｃと弁座６２との間の流路断面積Ｓ２が拡大するので、その流路断面積Ｓ２に応じた大流量の冷媒が流れることとなる。 Further, when the energization in the opposite direction is continued, the flow path cross-sectional area S2 between the seat surface 72c and the valve seat 62 expands according to the displacement amount of the valve shaft 24, so that it corresponds to the flow path cross-sectional area S2. A large flow rate of refrigerant will flow.

かかる状態で、流路断面積Ｓ１と流路断面積Ｓ２を合計した流路を介して供給側円管Ｔ１から排出側円管Ｔ２へと冷媒が流れることとなるが、弁部２４ｅと円筒孔７２ｄとの間で相対変位は生じないため、流路断面積Ｓ１（図８）は一定であるのに対し、流路断面積Ｓ２は、弁軸２４の変位量に応じて変化する。このため、大流量の流体制御を精度よく行うことができる。弁軸２４が最大位置まで変位すると、それ以上、流路断面積Ｓ２は拡大しないため、流路断面積Ｓ１と流路断面積Ｓ２の双方が一定となり、供給側円管Ｔ１から排出側円管Ｔ２へと流れる冷媒の量は一定となる。このとき、制御パルス数と流量との関係は、図２の点Ｃから点Ｄまでの実線により表される。 In such a state, the refrigerant flows from the supply-side circular pipe T1 to the discharge-side circular pipe T2 through the flow path obtained by totaling the flow path cross-sectional area S1 and the flow path cross-sectional area S2. Since no relative displacement occurs with 72d, the flow path cross-sectional area S1 (FIG. 8) is constant, whereas the flow path cross-sectional area S2 changes according to the amount of displacement of the valve shaft 24. Therefore, it is possible to accurately control the fluid with a large flow rate. When the valve shaft 24 is displaced to the maximum position, the flow path cross-sectional area S2 does not expand any more, so that both the flow path cross-sectional area S1 and the flow path cross-sectional area S2 become constant, and the supply-side circular pipe T1 to the discharge-side circular pipe become constant. The amount of refrigerant flowing to T2 is constant. At this time, the relationship between the number of control pulses and the flow rate is represented by the solid line from the point C to the point D in FIG.

このようにロータ３０の回転量によって弁軸２４を軸線方向に変位させることで、同じ方向に流れる冷媒の通過量を調整できる。ロータ３０の回転量は、パルスモータへの入力パルス数にて規制されるため、小流量及び大流量のいずれであっても、冷媒通過量の正確な調整が可能である。 By displacing the valve shaft 24 in the axial direction according to the rotation amount of the rotor 30 in this way, the passing amount of the refrigerant flowing in the same direction can be adjusted. Since the rotation amount of the rotor 30 is regulated by the number of input pulses to the pulse motor, the amount of refrigerant passing through can be accurately adjusted regardless of whether the flow rate is small or large.

［第２実施形態］
図１０は、第２実施形態の電動弁における弁室の周辺を示す拡大断面図である。本実施形態においては、第１実施形態に対して弁軸の弁部及び弁口の形状が異なる。また、弁軸２４Ａには上方段部２４ｆに相当する構成が形成されていない。それ以外の第１実施形態と同様な構成は、同じ符号を付して重複説明を省略する。 [Second Embodiment]
FIG. 10 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve of the second embodiment. In the present embodiment, the shapes of the valve portion and the valve port of the valve shaft are different from those of the first embodiment. Further, the valve shaft 24A is not formed with a configuration corresponding to the upper step portion 24f. Other configurations similar to those of the first embodiment are designated by the same reference numerals and duplicate description will be omitted.

弁軸２４Ａの弁部２４Ａｅは、図１０に示すように２段テーパ形状となっており、より具体的には、弁部２４Ａｅは、第４軸部２４Ａｄに隣接する第１弁部２４Ａｅ１と、第１弁部２４Ａｅ１に隣接する第２弁部２４Ａｅ２とを有する。ここで、軸線Ｌを通る平面で弁軸２４Ａを切断した断面において、軸線Ｌを中心に対向する第１弁部２４Ａｅ１の両側の外形直線により挟む角をテーパ角θ１とし、軸線Ｌを中心に対向する第２弁部２４Ａｅ２の両側の外形直線により挟む角をテーパ角θ２とする。本実施形態では、テーパ角θ１はテーパ角θ２よりも大きくなっている。 The valve portion 24Ae of the valve shaft 24A has a two-step tapered shape as shown in FIG. 10, and more specifically, the valve portion 24Ae has a first valve portion 24Ae1 adjacent to the fourth shaft portion 24Ad. It has a second valve portion 24Ae2 adjacent to the first valve portion 24Ae1. Here, in a cross section obtained by cutting the valve shaft 24A on a plane passing through the axis L, the angle sandwiched by the outer straight lines on both sides of the first valve portion 24Ae1 facing the axis L is defined as the taper angle θ1, and the taper angle θ1 faces the center. The taper angle θ2 is defined as the angle sandwiched by the outer straight lines on both sides of the second valve portion 24Ae2. In the present embodiment, the taper angle θ1 is larger than the taper angle θ2.

また、弁口となるシート７２Ａの連通穴７２Ａｆは、小テーパ部７２Ａｇと、小テーパ部７２Ａｇに隣接する円筒孔７２Ａｄと、円筒孔７２Ａｄに隣接するテーパ孔７２Ａｅとを有する。 Further, the communication hole 72Af of the sheet 72A serving as the valve port has a small tapered portion 72Ag, a cylindrical hole 72Ad adjacent to the small tapered portion 72Ag, and a tapered hole 72Ae adjacent to the cylindrical hole 72Ad.

本実施形態によれば、ステータコイル５３（図１参照）への通電により、弁軸２４Ａが下方に変位すると、図１０に示すように、第１弁部２４Ａｅ１が小テーパ部７２Ａｇに着座するため、弁部２４Ａｅと連通穴７２Ａｆとの間に隙間がなくなり、その間を冷媒が通過しなくなる。また、図３を参照して、シート７２Ａのシート面７２ｃが弁座部材６０の弁座６２に着座している限り、両者間を冷媒が通過しないので、供給側円管Ｔ１から排出側円管Ｔ２への冷媒の流れは遮断される。 According to the present embodiment, when the valve shaft 24A is displaced downward by energizing the stator coil 53 (see FIG. 1), the first valve portion 24Ae1 is seated on the small taper portion 72Ag as shown in FIG. , There is no gap between the valve portion 24Ae and the communication hole 72Af, and the refrigerant does not pass between them. Further, referring to FIG. 3, as long as the seat surface 72c of the seat 72A is seated on the valve seat 62 of the valve seat member 60, the refrigerant does not pass between the two, so that the supply side circular pipe T1 to the discharge side circular pipe The flow of refrigerant to T2 is blocked.

これに対し、逆方向への通電により、弁軸２４Ａが上方に変位すると、その変位量に応じて弁部２４Ａｅと連通穴７２Ａｆとの間に隙間が生じるため、その流路断面積に応じた小流量の冷媒が流れることとなる。このとき、制御パルス数と流量との関係は、図２の点Ａ’から点Ｂまで点線、及び点Ｂから点Ｃまでの実線により表される。 On the other hand, when the valve shaft 24A is displaced upward due to energization in the opposite direction, a gap is generated between the valve portion 24Ae and the communication hole 72Af according to the amount of displacement. A small flow rate of refrigerant will flow. At this time, the relationship between the number of control pulses and the flow rate is represented by a dotted line from point A'to point B in FIG. 2 and a solid line from point B to point C.

さらに、逆方向への通電を続行すると、図９を参照して、環状部材７３がスリーブ７１の頂壁７１ｂの下面に当接して移動弁座体７０が弁軸２４Ａに引き上げられるため、移動弁座体７０のシート面７２ｃと弁座部材６０の弁座６２との間に隙間が生じる。それ以降、弁軸２４Ａの変位量に応じて、シート面７２ｃと弁座６２との間の隙間が変化するので、その流路断面積に応じた大流量の冷媒が流れることとなる。このとき、制御パルス数と流量との関係は、第１実施形態と同様に、図２の点Ｃから点Ｄまでの実線により表される。 Further, when the energization in the opposite direction is continued, the annular member 73 abuts on the lower surface of the top wall 71b of the sleeve 71 and the moving valve seat 70 is pulled up to the valve shaft 24A, so that the moving valve is pulled up. A gap is formed between the seat surface 72c of the seat body 70 and the valve seat 62 of the valve seat member 60. After that, the gap between the seat surface 72c and the valve seat 62 changes according to the displacement amount of the valve shaft 24A, so that a large flow rate of the refrigerant flows according to the cross-sectional area of the flow path. At this time, the relationship between the number of control pulses and the flow rate is represented by a solid line from the point C to the point D in FIG. 2, as in the first embodiment.

なお、図１０に図示していないが、電動弁の小テーパ部７２Ａｇに流れ方向に沿った方向の溝（ノッチ）を形成することもできる。それにより、第１弁部２４Ａｅ１を小テーパ部７２Ａｇに着座させた状態で、所定の微小流量流を確保することができる。なお、溝（ノッチ）は複数形成すると好ましい。 Although not shown in FIG. 10, a groove (notch) in the direction along the flow direction can be formed in the small tapered portion 72Ag of the electric valve. As a result, a predetermined minute flow rate can be secured with the first valve portion 24Ae1 seated on the small taper portion 72Ag. It is preferable to form a plurality of grooves (notches).

［第３実施形態］
図１１は、第３実施形態の電動弁１０Ｂを示す縦断面図である。図１２は、図１１の電動弁１０Ｂにおける弁室の周辺を示す拡大断面図である。本実施形態においては、第１実施形態に対して、移動弁座体７０Ｂのスリーブ７１Ｂの形状が異なるが、シート７２は第1実施形態と同様である。第１実施形態と同様な構成は、それぞれ同じ符号を付して重複説明を省略する。 [Third Embodiment]
FIG. 11 is a vertical cross-sectional view showing the electric valve 10B of the third embodiment. FIG. 12 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve 10B of FIG. In the present embodiment, the shape of the sleeve 71B of the mobile valve seat body 70B is different from that of the first embodiment, but the seat 72 is the same as that of the first embodiment. The same configurations as those in the first embodiment are designated by the same reference numerals, and duplicate description will be omitted.

より具体的には、スリーブ７１Ｂの横穴（連通孔）７１Ｂａは、第１実施形態のものよりも上方にシフトして、ホルダ２２０の下端近傍に配置されている。本実施形態では、横穴７１Ｂａの内周下端は、供給側円管（流体供給用の配管）Ｔ１の内周上端より上方に位置すると好ましいが、横穴７１Ｂａの内周上端が供給側円管Ｔ１の内周上端より若干下方に位置していてもよい。
なお、具体的には、本実施形態の横穴７１Ｂａの内周下端７１Ｂ１は、図１２に示すように、供給側円管Ｔ１の内周上端から軸線Ｌに直交且つ中心線Ｏに平行な延長線Ａよりも上方（図１２では反重力方向）に位置している。 More specifically, the lateral hole (communication hole) 71Ba of the sleeve 71B is shifted upward from that of the first embodiment and is arranged near the lower end of the holder 220. In the present embodiment, the lower end of the inner circumference of the horizontal hole 71Ba is preferably located above the upper end of the inner circumference of the supply-side circular pipe (pipe for fluid supply) T1, but the upper end of the inner circumference of the horizontal hole 71Ba is the supply-side circular pipe T1. It may be located slightly below the upper end of the inner circumference.
Specifically, as shown in FIG. 12, the inner peripheral lower end 71B1 of the horizontal hole 71Ba of the present embodiment is an extension line orthogonal to the axis L and parallel to the center line O from the inner peripheral upper end of the supply-side circular tube T1. It is located above A (in the direction of antigravity in FIG. 12).

また、筒状本体２１０とスリーブ７１Ｂとの間の空間を第１弁室ＶＳ１とし、スリーブ７１Ｂ内の隔壁７１ｂより下方の空間を第２弁室ＶＳ２とする。横穴７１Ｂａは、第１弁室ＶＳ１と第２弁室ＶＳ２とを連通している。 Further, the space between the tubular main body 210 and the sleeve 71B is referred to as the first valve chamber VS1, and the space below the partition wall 71b in the sleeve 71B is referred to as the second valve chamber VS2. The lateral hole 71Ba communicates the first valve chamber VS1 and the second valve chamber VS2.

本実施形態によれば、ステータコイル５３への通電により、弁軸ホルダ３２が下方に変位すると、重力に従い環状部材７３に係止された状態の移動弁座体７０は弁軸ホルダ３２とともに下方に変位する。さらに弁軸ホルダ３２を下方に変位させると、移動弁座体７０のシート面７２ｃが、弁座部材６０の弁座６２に着座する。この状態からさらに弁軸ホルダ３２を下方に変位させると環状部材７３と頂壁７１Ｂｂが離れ、その後、弁軸２４の上方段部２４ｆがスリーブ７１の頂壁７１Ｂｂの上面に突き当たり、シート面７２ｃをコイルばね３４の弾性力により弁座６２に押し当て、シート面７２ｃと弁座６２との間の冷媒の流れを遮断する。 According to the present embodiment, when the valve shaft holder 32 is displaced downward by energizing the stator coil 53, the moving valve seat 70 in a state of being locked to the annular member 73 according to gravity moves downward together with the valve shaft holder 32. Displace. When the valve shaft holder 32 is further displaced downward, the seat surface 72c of the moving valve seat body 70 is seated on the valve seat 62 of the valve seat member 60. When the valve shaft holder 32 is further displaced downward from this state, the annular member 73 and the top wall 71Bb are separated from each other, and then the upper step portion 24f of the valve shaft 24 abuts on the upper surface of the top wall 71Bb of the sleeve 71, and the seat surface 72c is pressed. It is pressed against the valve seat 62 by the elastic force of the coil spring 34 to block the flow of the refrigerant between the seat surface 72c and the valve seat 62.

一方、弁軸２４の上方段部２４ｆがスリーブ７１Ｂの頂壁７１Ｂｂの上面に突き当たった状態で、第４軸部２４ｄと円筒孔７２ｄとの間に隙間が生じるため、その隙間に応じた流量で冷媒が通過する。 On the other hand, in a state where the upper step portion 24f of the valve shaft 24 abuts on the upper surface of the top wall 71Bb of the sleeve 71B, a gap is generated between the fourth shaft portion 24d and the cylindrical hole 72d. Refrigerant passes through.

これに対し、逆方向への通電により、弁軸２４が上方に変位すると、その変位量に応じて第４軸部２４ｄと円筒孔７２ｄとの間に隙間が生じるため、その流路断面積に応じた小流量の冷媒が流れることとなる。 On the other hand, when the valve shaft 24 is displaced upward by energization in the opposite direction, a gap is generated between the fourth shaft portion 24d and the cylindrical hole 72d according to the amount of the displacement. A corresponding small flow rate of refrigerant will flow.

ところで、供給側円管Ｔ１から、液体とガスが混合された冷媒（混合冷媒）が第１弁室ＶＳ１に供給されたとき、かかる混合冷媒が、流路断面積が最も小さい小径弁口を通過する際に、液体とガスとが交互に通過することにより異音を発生させる場合がある。 By the way, when a refrigerant (mixed refrigerant) in which a liquid and a gas are mixed is supplied from the supply-side circular pipe T1 to the first valve chamber VS1, the mixed refrigerant passes through the small-diameter valve port having the smallest flow path cross-sectional area. When the liquid and the gas pass alternately, an abnormal noise may be generated.

本実施形態によれば、供給側円管Ｔ１から混合冷媒が第１弁室ＶＳ１に供給されたとき、比較的比重が重い液体はシート７２側に留まるが、比較的比重が軽いガス（気体）はスリーブ７１Ｂの上部側へと移動し、横穴７１Ｂａを介して第２弁室ＶＳ２へと移動し、第２弁室ＶＳ２の上部に貯留される。このため、第２弁室ＶＳ２から小径弁口を通過する冷媒は気体のみとなり、冷媒通過時の異音の発生を抑制することができる。 According to the present embodiment, when the mixed refrigerant is supplied to the first valve chamber VS1 from the supply side circular pipe T1, the liquid having a relatively heavy specific density stays on the seat 72 side, but the gas (gas) having a relatively light specific density. Moves to the upper side of the sleeve 71B, moves to the second valve chamber VS2 through the lateral hole 71Ba, and is stored in the upper part of the second valve chamber VS2. Therefore, the refrigerant passing through the small-diameter valve port from the second valve chamber VS2 is only gas, and the generation of abnormal noise when passing through the refrigerant can be suppressed.

［第４実施形態］
図１３は、第４実施形態の電動弁１０Ｃを示す縦断面図である。図１４は、図１３の電動弁１０Ｃにおける弁室の周辺を示す拡大断面図である。本実施形態においては、第１実施形態に対して、弁本体２０Ｃ、弁軸２４Ｃ、移動弁座体７０Ｃの構成が異なる。また、シート７２は第１実施形態と同様な構成を有するが、供給側配管Ｔ１との相対位置関係が異なる。第１実施形態と同様な構成は、それぞれ同じ符号を付して重複説明を省略する。 [Fourth Embodiment]
FIG. 13 is a vertical cross-sectional view showing the electric valve 10C of the fourth embodiment. FIG. 14 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve 10C of FIG. In the present embodiment, the configurations of the valve body 20C, the valve shaft 24C, and the moving valve seat body 70C are different from those of the first embodiment. Further, the sheet 72 has the same configuration as that of the first embodiment, but the relative positional relationship with the supply side pipe T1 is different. The same configurations as those in the first embodiment are designated by the same reference numerals, and duplicate description will be omitted.

図１３，１４に示すように、ホルダ２２０Ｃには、中空円筒部２２１Ｃの下部外周に縮径部２２６が形成されている。縮径部２２６の上端は、仕切り壁２２２Ｃの下面位置とほぼ同じ高さである。筒状本体２１０Ｃの円孔２１１に挿通された供給側円管（流体供給用の配管）Ｔ１は、その先端が縮径部２２６の下端に当接することにより、筒状本体２１０Ｃに対して位置決めされている。かかる状態で、供給側円管Ｔ１は筒状本体２１０Ｃにロウ付けされる。 As shown in FIGS. 13 and 14, the holder 220C is formed with a reduced diameter portion 226 on the lower outer circumference of the hollow cylindrical portion 221C. The upper end of the reduced diameter portion 226 is substantially the same height as the lower surface position of the partition wall 222C. The supply-side circular pipe (pipe for fluid supply) T1 inserted into the circular hole 211 of the tubular main body 210C is positioned with respect to the tubular main body 210C by contacting the tip end with the lower end of the reduced diameter portion 226. ing. In this state, the supply-side circular tube T1 is brazed to the tubular main body 210C.

筒状本体２１０Ｃ内で軸線Ｌ方向に変位可能な移動弁座体７０Ｃは、図１４において、中空円筒部２２１Ｃの下端内周に摺動可能に嵌合する円筒状のスリーブ７１Ｃと、スリーブ７１Ｃの下端に接合された円盤状のシート７２とを有する。スリーブ７１Ｃは、円筒周壁７１Ｃａと、円筒周壁７１Ｃａの軸線方向中間に形成された隔壁７１Ｃｂとを有する。隔壁７１Ｃｂの中央に、円形開口７１Ｃｃが形成されている。円形開口７１Ｃｃの周囲には、溝（ノッチ）７６が形成されている。弁軸２４Ｃの段部２４Ｃｆが隔壁７１Ｃｂに当接した状態でも、溝（ノッチ）７６を介して冷媒の移動が可能である。 In FIG. 14, the movable valve seat body 70C that can be displaced in the axial direction L direction in the tubular main body 210C is a cylindrical sleeve 71C and a sleeve 71C that are slidably fitted to the inner circumference of the lower end of the hollow cylindrical portion 221C. It has a disk-shaped sheet 72 joined to the lower end. The sleeve 71C has a cylindrical peripheral wall 71Ca and a partition wall 71Cb formed in the middle of the cylindrical peripheral wall 71Ca in the axial direction. A circular opening 71Cc is formed in the center of the partition wall 71Cb. A groove (notch) 76 is formed around the circular opening 71 Cc. Even when the step portion 24Cf of the valve shaft 24C is in contact with the partition wall 71Cb, the refrigerant can move through the groove (notch) 76.

図１３に示すように、弁軸２４Ｃは、第１軸部２４Ｃａと、第２軸部２４Ｃｂと、第３軸部２４Ｃｃと、第４軸部２４Ｃｄと、弁部２４Ｃｅとを同軸に連設してなるが、第１実施形態に対し、第２軸部２４Ｃｂの長さが長くなっている。 As shown in FIG. 13, in the valve shaft 24C, the first shaft portion 24Ca, the second shaft portion 24Cb, the third shaft portion 24Cc, the fourth shaft portion 24Cd, and the valve portion 24Ce are coaxially provided in series. However, the length of the second shaft portion 24Cb is longer than that of the first embodiment.

筒状本体２１０Ｃとスリーブ７１Ｃとの間の空間を第１弁室ＶＳ１とし、スリーブ７１Ｃ内の隔壁７１Ｃｂより下方の空間を第２弁室ＶＳ２とする。 The space between the tubular main body 210C and the sleeve 71C is referred to as the first valve chamber VS1, and the space below the partition wall 71Cb in the sleeve 71C is referred to as the second valve chamber VS2.

さらに本実施形態では、ホルダ２２０Ｃと、ホルダ２２０Ｃに嵌合するスリーブ７１Ｃ（隔壁７１Ｃｂの上方）との間に第３弁室ＶＳ３を形成している。第１弁室ＶＳ１と第３弁室ＶＳ３とは、供給側円管Ｔ１から上方に離間して縮径部２２６に設けた貫通開口（貫通穴）２２７を介して連通しており、第３弁室ＶＳ３と第２弁室ＶＳ２とは、弁軸２４Ｃと円形穴２２５Ｃとの隙間（溝７６を含む）を介して連通している。 Further, in the present embodiment, the third valve chamber VS3 is formed between the holder 220C and the sleeve 71C (above the partition wall 71Cb) fitted to the holder 220C. The first valve chamber VS1 and the third valve chamber VS3 communicate with each other through a through opening (through hole) 227 provided in the reduced diameter portion 226 so as to be separated upward from the supply side circular pipe T1 and communicate with the third valve. The chamber VS3 and the second valve chamber VS2 communicate with each other through a gap (including the groove 76) between the valve shaft 24C and the circular hole 225C.

シート７２が着座する弁座部材６０Ｃは、第１実施形態に対して上端側の薄肉円筒部６１Ｃを上方に延長した点のみが異なる。本実施形態においては、供給側円管Ｔ１は薄肉円筒部６１Ｃに接しておらず、それから上方に離間している。第１弁室ＶＳ１の一部であって、弁座部材６０Ｃと、供給側円管Ｔ１の内周最下端との間（シート７２および薄肉円筒部６１Ｃの周囲）、すなわち弁本体２０Ｂの底部に液だまり空間ＬＳを形成している。薄肉円筒部６１Ｃを上方に延長することにより、液だまり空間ＬＳの容積を増大させることができる。 The valve seat member 60C on which the seat 72 is seated differs only in that the thin-walled cylindrical portion 61C on the upper end side is extended upward with respect to the first embodiment. In the present embodiment, the supply-side circular tube T1 is not in contact with the thin-walled cylindrical portion 61C, but is separated upward from the thin-walled cylindrical portion 61C. A part of the first valve chamber VS1 between the valve seat member 60C and the lowermost end of the inner circumference of the supply-side circular pipe T1 (around the seat 72 and the thin cylindrical portion 61C), that is, at the bottom of the valve body 20B. It forms a liquid pool space LS. By extending the thin-walled cylindrical portion 61C upward, the volume of the liquid pool space LS can be increased.

本実施形態においても、供給側円管Ｔ１から混合冷媒が第１弁室ＶＳ１に供給されたとき、比較的比重が重い液体はシート７２側へと移動して液だまり空間ＬＳ内に滞留する。一方、比較的比重が軽いガスはスリーブ７１Ｃの上部側へと移動して、筒状本体部２１０Ｃと縮径部２２６との間を通り、貫通開口２２７を介して第３弁室ＶＳ３へと移動し、第３弁室ＶＳ３に貯留される。このため、第２弁室ＶＳ２から小径弁口を通過する冷媒は気体のみとなり、冷媒通過時の異音の発生を抑制することができる。 Also in the present embodiment, when the mixed refrigerant is supplied to the first valve chamber VS1 from the supply side circular pipe T1, the liquid having a relatively heavy specific gravity moves to the seat 72 side and stays in the liquid pool space LS. On the other hand, the gas having a relatively light specific gravity moves to the upper side of the sleeve 71C, passes between the tubular main body portion 210C and the diameter reduction portion 226, and moves to the third valve chamber VS3 through the through opening 227. Then, it is stored in the third valve chamber VS3. Therefore, the refrigerant passing through the small-diameter valve port from the second valve chamber VS2 is only gas, and the generation of abnormal noise when passing through the refrigerant can be suppressed.

［第５実施形態］
図１５は、第５実施形態の電動弁１０Ｄを示す縦断面図である。図１６は、図１５の電動弁１０Ｄにおける弁室の周辺を示す拡大断面図である。本実施形態においては、第４実施形態に対して、移動弁座体７０Ｄのスリーブ７１Ｄの形状が異なるが、シート７２は第４の実施形態と同様である。第４実施形態と同様な構成は、同じ符号を付して重複説明を省略する。 [Fifth Embodiment]
FIG. 15 is a vertical cross-sectional view showing the electric valve 10D of the fifth embodiment. FIG. 16 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve 10D of FIG. In the present embodiment, the shape of the sleeve 71D of the mobile valve seat body 70D is different from that of the fourth embodiment, but the seat 72 is the same as that of the fourth embodiment. The same configurations as in the fourth embodiment are designated by the same reference numerals and duplicate description will be omitted.

本実施形態において、スリーブ７１Ｄは、隔壁７１Ｄｂに溝（ノッチ）を設ける代わりに、段部２４Ｃｆの径方向外側に、１つ又は複数の鉛直孔７７を有している。 In the present embodiment, the sleeve 71D has one or a plurality of vertical holes 77 on the radial outer side of the step portion 24Cf instead of providing a groove (notch) in the partition wall 71Db.

本実施形態においても、供給側円管Ｔ１から混合冷媒が第１弁室ＶＳ１に供給されたとき、比較的比重が重い液体はシート７２側へと移動して液だまり空間ＬＳ内に滞留する。一方、比較的比重が軽いガスはスリーブ７１Ｄの上部側へと移動して、貫通開口２２７を介して第３弁室ＶＳ３へと移動し、第３弁室ＶＳ３に貯留される。また、第３弁室ＶＳ３に液体が進入した場合、かかる液体は鉛直孔７７を介して第２弁室ＶＳ２へと移動する。このため、第２弁室ＶＳ２から小径弁口を通過する冷媒は気体のみとなり、冷媒通過時の異音の発生を抑制することができる。 Also in the present embodiment, when the mixed refrigerant is supplied to the first valve chamber VS1 from the supply side circular pipe T1, the liquid having a relatively heavy specific gravity moves to the seat 72 side and stays in the liquid pool space LS. On the other hand, the gas having a relatively light specific gravity moves to the upper side of the sleeve 71D, moves to the third valve chamber VS3 through the through opening 227, and is stored in the third valve chamber VS3. Further, when a liquid enters the third valve chamber VS3, the liquid moves to the second valve chamber VS2 through the vertical hole 77. Therefore, the refrigerant passing through the small-diameter valve port from the second valve chamber VS2 is only gas, and the generation of abnormal noise when passing through the refrigerant can be suppressed.

［第６実施形態］
図１７は、第６実施形態の電動弁における弁室の周辺を示す拡大断面図である。本実施形態においては、第３実施形態に対して弁軸２４Ｅと，移動弁座体７０Ｅのシート７２Ｅの形状が異なる。ただし、スリーブ７１は第３実施形態と同様である。また、弁軸２４Ｅには上方段部２４ｆに相当する構成が形成されていない。第３実施形態と同様な構成は、同じ符号を付して重複説明を省略する。 [Sixth Embodiment]
FIG. 17 is an enlarged cross-sectional view showing the periphery of the valve chamber in the electric valve of the sixth embodiment. In the present embodiment, the shapes of the valve shaft 24E and the seat 72E of the moving valve seat body 70E are different from those of the third embodiment. However, the sleeve 71 is the same as that of the third embodiment. Further, the valve shaft 24E is not formed with a configuration corresponding to the upper stage portion 24f. The same configurations as in the third embodiment are designated by the same reference numerals, and duplicate description will be omitted.

弁軸２４Ｅの弁部２４Ｅｅは、図１７に示すように２段テーパ形状となっており、より具体的には、弁部２４Ｅｅは、第４軸部２４Ｅｄに隣接する第１弁部２４Ｅｅ１と、第１弁部２４Ｅｅ１に隣接する第２弁部２４Ｅｅ２とを有する。第３実施形態と同様に、第１弁部２４Ｅｅ１のテーパ角は、第２弁部２４Ｅｅ２のテーパ角よりも大きくなっている。 The valve portion 24Ee of the valve shaft 24E has a two-step tapered shape as shown in FIG. 17, and more specifically, the valve portion 24Ee has a first valve portion 24Ee1 adjacent to the fourth shaft portion 24Ed. It has a second valve portion 24Ee2 adjacent to the first valve portion 24Ee1. Similar to the third embodiment, the taper angle of the first valve portion 24Ee1 is larger than the taper angle of the second valve portion 24Ee2.

また、弁口となるシート７２Ｅの連通穴７２Ｅｆは、小テーパ部７２Ｅｇと、小テーパ部７２Ｅｇに隣接する円筒孔７２Ｅｄと、円筒孔７２Ｅｄに隣接するテーパ孔７２Ｅｅとを有する。 Further, the communication hole 72Ef of the sheet 72E serving as the valve port has a small tapered portion 72Eg, a cylindrical hole 72Ed adjacent to the small tapered portion 72Eg, and a tapered hole 72Ee adjacent to the cylindrical hole 72Ed.

本実施形態によれば、ステータコイル５３（図１参照）への通電により、弁軸２４Ｅが下方に変位すると、第１弁部２４Ｅｅ１が小テーパ部７２Ｅｇに着座するため、弁部２４Ｅｅと連通穴７２Ｅｆとの間に隙間がなくなり、その間を冷媒が通過しなくなる。また、シート７２Ｅのシート面７２ｃが弁座部材６０の弁座６２に着座している限り、両者間を冷媒が通過しないので、供給側円管Ｔ１から排出側円管Ｔ２への冷媒の流れは遮断される。 According to the present embodiment, when the valve shaft 24E is displaced downward by energizing the stator coil 53 (see FIG. 1), the first valve portion 24Ee1 is seated on the small taper portion 72Eg, so that the communication hole with the valve portion 24Ee is formed. There is no gap between the 72Ef and the refrigerant, and the refrigerant does not pass between them. Further, as long as the seat surface 72c of the seat 72E is seated on the valve seat 62 of the valve seat member 60, the refrigerant does not pass between the two, so that the flow of the refrigerant from the supply side circular pipe T1 to the discharge side circular pipe T2 It is blocked.

これに対し、逆方向への通電により、弁軸２４Ｅが上方に変位すると、その変位量に応じて弁部２４Ｅｅと連通穴７２Ｅｆとの間に隙間が生じるため、その流路断面積に応じた小流量の冷媒が流れることとなる。 On the other hand, when the valve shaft 24E is displaced upward due to energization in the opposite direction, a gap is generated between the valve portion 24Ee and the communication hole 72Ef according to the amount of displacement. A small flow rate of refrigerant will flow.

さらに、逆方向への通電を続行すると、図１１を参照して、環状部材７３がスリーブ７１の頂壁７１ｂの下面に当接して移動弁座体７０Ｅが弁軸２４Ｅに引き上げられるため、移動弁座体７０Ｅのシート面７２ｃと弁座部材６０の弁座６２との間に隙間が生じる。それ以降、弁軸２４Ｅの変位量に応じて、シート面７２ｃと弁座６２との間の隙間が変化するので、その流路断面積に応じた大流量の冷媒が流れることとなる。 Further, when the energization in the opposite direction is continued, the annular member 73 abuts on the lower surface of the top wall 71b of the sleeve 71 and the moving valve seat 70E is pulled up to the valve shaft 24E, so that the moving valve is pulled up. A gap is formed between the seat surface 72c of the seat body 70E and the valve seat 62 of the valve seat member 60. After that, the gap between the seat surface 72c and the valve seat 62 changes according to the displacement amount of the valve shaft 24E, so that a large flow rate of the refrigerant flows according to the cross-sectional area of the flow path.

また、電動弁の小テーパ部７２Ｅｇに流れ方向に沿った方向の溝（ノッチ）不図示を形成すれば、第１弁部２４Ｅｅ１を小テーパ部７２Ｅｇに着座させた状態（図２の制御パルス数０から点Ａ’までの範囲）で、所定の微小流量流（図２の点Ａと同等の流量）にすることができる。なお、かかる溝（ノッチ）は複数形成すると好ましい。 Further, if a groove (notch) in the direction along the flow direction is not shown in the small taper portion 72Eg of the electric valve, the first valve portion 24Ee1 is seated in the small taper portion 72Eg (the number of control pulses in FIG. 2). In the range (range from 0 to point A'), a predetermined minute flow rate (flow rate equivalent to that of point A in FIG. 2) can be obtained. It is preferable to form a plurality of such grooves (notches).

なお、本発明は、上述の実施形態に限定されない。本発明の範囲内において、上述の実施形態の任意の構成要素の変形が可能である。また、上述の実施形態において任意の構成要素の追加または省略が可能である。 The present invention is not limited to the above-described embodiment. Within the scope of the present invention, any component of the above-described embodiment can be modified. In addition, any component can be added or omitted in the above-described embodiment.

１０，１０Ｂ，１０Ｃ，１０Ｄ 電動弁
２０，２０Ｂ，２０Ｃ 弁本体
２１ 弁室
２４，２４Ａ，２４Ｃ，２４Ｅ 弁軸
２５ 固定ねじ部（雄ねじ部）
２６ ガイドブッシュ
２７ 下ストッパ体
３０ ロータ
３１ 移動ねじ部（雌ねじ部）
３２ 弁軸ホルダ
３３ プッシュナット
３４ 圧縮コイルばね
３５ 復帰ばね
３６ 支持リング
３７ 上ストッパ体
４０ キャン
４１ 環状板
５０ ステータ
６０，６０Ｃ 弁座部材
７０，７０Ｂ，７０Ｃ，７０Ｄ，７０Ｅ 移動弁座体
ＶＳ１ 第１弁室
ＶＳ２ 第２弁室
ＶＳ３ 第３弁室

10,10B, 10C, 10D Electric valve 20, 20B, 20C Valve body 21 Valve chamber 24, 24A, 24C, 24E Valve shaft 25 Fixed screw part (male thread part)
26 Guide bush 27 Lower stopper body 30 Rotor 31 Moving thread part (female thread part)
32 Valve shaft holder 33 Push nut 34 Compression coil spring 35 Return spring 36 Support ring 37 Upper stopper body 40 Can 41 Circular plate 50 Stator 60, 60C Valve seat member 70, 70B, 70C, 70D, 70E Mobile valve seat body VS1 1st Valve chamber VS2 2nd valve chamber VS3 3rd valve chamber

本発明にかかる電動弁は、
第１弁室及び大径弁口を備えた弁本体と、
前記第１弁室に挿通され、流路調整部と係合部と段差部とが設けられた弁軸と、
前記弁軸を前記大径弁口に接離する方向に変位させることによって、リフト量を変化させることが可能な弁軸駆動部と、
前記第１弁室内で前記弁軸の変位方向に移動可能に配置され、第２弁室および前記第２弁室につながる小径弁口を備えた移動弁座体と、を有し、
前記弁軸の前記リフト量の変化する範囲に、前記移動弁座体が前記大径弁口に着座した状態で前記流路調整部と前記小径弁口との間の流路断面積を変化させる第１の範囲と、前記移動弁座体が前記係合部に係止された状態で前記移動弁座体と前記大径弁口との間の流路断面積を変化させる第２の範囲と、を有するように構成され、
前記第１の範囲内において前記流路調整部が最も前記小径弁口側に移動した下端位置のとき、前記流路調整部と前記小径弁口との間に所定の隙間を有し、
前記第１弁室には流体供給用の配管が接続されており、
前記第１弁室と前記第２弁室とを連通する連通孔が、前記配管の内周上端よりも上方に設けられていることを特徴とする。
The electric valve according to the present invention is
A valve body equipped with a first valve chamber and a large-diameter valve port,
A valve shaft inserted into the first valve chamber and provided with a flow path adjusting portion, an engaging portion, and a step portion.
A valve shaft drive unit capable of changing the lift amount by displacing the valve shaft in a direction in which the valve shaft is brought into contact with or separated from the large-diameter valve port.
It has a mobile valve seat body that is movably arranged in the first valve chamber in the displacement direction of the valve shaft and has a second valve chamber and a small-diameter valve opening that connects to the second valve chamber.
Within the range where the lift amount of the valve shaft changes, the flow path cross-sectional area between the flow path adjusting portion and the small diameter valve port is changed with the moving valve seat body seated on the large diameter valve port. The first range and the second range in which the flow path cross-sectional area between the moving valve seat and the large-diameter valve port is changed while the moving valve seat is locked to the engaging portion. Is configured to have,
When the flow path adjusting portion is at the lower end position where the flow path adjusting portion is most moved to the small diameter valve opening side within the first range, a predetermined gap is provided between the flow path adjusting portion and the small diameter valve opening.
A fluid supply pipe is connected to the first valve chamber.
A communication hole for communicating the first valve chamber and the second valve chamber is provided above the upper end of the inner circumference of the pipe.

Claims (11)

第１弁室及び大径弁口を備えた弁本体と、
前記第１弁室に挿通され、流路調整部と係合部と段差部とが設けられた弁軸と、
前記弁軸を前記大径弁口に接離する方向に変位させることによって、リフト量を変化させることが可能な弁軸駆動部と、
前記第１弁室内で前記弁軸の変位方向に移動可能に配置され、第２弁室および前記第２弁室につながる小径弁口を備えた移動弁座体と、を有し、
前記弁軸の前記リフト量は、前記移動弁座体が前記大径弁口に着座した状態で前記流路調整部と前記小径弁口との間の流路断面積を変化させる第１の範囲と、前記移動弁座体が前記係合部に係止された状態で前記移動弁座体と前記大径弁口との間の流路断面積を変化させる第２の範囲と、を有するように構成され、
前記第１の範囲内において前記流路調整部が最も前記小径弁口側に移動した下端位置のとき、前記流路調整部と前記小径弁口との間に所定の隙間を有し、
前記第１弁室には流体供給用の配管が接続されており、
前記第１弁室と前記第２弁室とを連通する連通孔が、前記配管の内周上端よりも上方に設けられている、
ことを特徴とする電動弁。 A valve body equipped with a first valve chamber and a large-diameter valve port,
A valve shaft inserted into the first valve chamber and provided with a flow path adjusting portion, an engaging portion, and a step portion.
A valve shaft drive unit capable of changing the lift amount by displacing the valve shaft in a direction in which the valve shaft is brought into contact with or separated from the large-diameter valve port.
It has a mobile valve seat body that is movably arranged in the first valve chamber in the displacement direction of the valve shaft and has a second valve chamber and a small-diameter valve opening that connects to the second valve chamber.
The lift amount of the valve shaft is a first range in which the flow path cross-sectional area between the flow path adjusting portion and the small diameter valve port is changed while the moving valve seat body is seated on the large diameter valve port. And a second range for changing the flow path cross-sectional area between the moving valve seat and the large-diameter valve port in a state where the moving valve seat is locked to the engaging portion. Consists of
When the flow path adjusting portion is at the lower end position where the flow path adjusting portion is most moved to the small diameter valve opening side within the first range, a predetermined gap is provided between the flow path adjusting portion and the small diameter valve opening.
A fluid supply pipe is connected to the first valve chamber.
A communication hole for communicating the first valve chamber and the second valve chamber is provided above the upper end of the inner circumference of the pipe.
An electric valve characterized by that. 前記弁軸の前記段差部が前記移動弁座体に当接したときに、前記流路調整部が前記下端位置になる、
ことを特徴とする請求項１に記載の電動弁。 When the stepped portion of the valve shaft comes into contact with the moving valve seat body, the flow path adjusting portion becomes the lower end position.
The electric valve according to claim 1. 前記流路調整部は、テーパ部である、
ことを特徴とする請求項１又は２に記載の電動弁。 The flow path adjusting portion is a tapered portion.
The electric valve according to claim 1 or 2. 前記移動弁座体は、前記小径弁口を備え前記大径弁口に当接するシートと、前記シートに連結され隔壁を備えたスリーブとを有し、前記スリーブの隔壁に形成された開口を介して、前記弁軸が前記第2弁室に挿通されている、
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 moving valve seat body has a sheet having the small-diameter valve port and abutting on the large-diameter valve port, and a sleeve connected to the sheet and having a partition wall, through an opening formed in the partition wall of the sleeve. The valve shaft is inserted into the second valve chamber.
The electric valve according to any one of claims 1 to 3. 前記スリーブの周壁に、前記連通孔を有する、
ことを特徴とする請求項４に記載の電動弁。 The communication hole is provided in the peripheral wall of the sleeve.
The electric valve according to claim 4. 前記隔壁を挟んで前記弁軸の一方の側に前記段差部が配設され、前記弁軸の他方の側に前記係合部が配設されている、
ことを特徴とする請求項４又は５に記載の電動弁。 The step portion is arranged on one side of the valve shaft with the partition wall interposed therebetween, and the engaging portion is arranged on the other side of the valve shaft.
The electric valve according to claim 4 or 5. 前記流体供給用の配管は、前記シートに対して上方に離間している、
ことを特徴とする請求項４〜６のいずれか一項に記載の電動弁。 The fluid supply pipe is separated upward from the seat.
The electric valve according to any one of claims 4 to 6, wherein the electric valve according to any one of claims 4 to 6. 前記弁本体は、パイプ材から形成された本体と、前記本体の内側に配設され前記移動弁座体を案内するガイド部とを有し、前記ガイド部に前記連通孔を有する、
ことを特徴とする請求項１〜７のいずれか一項に記載の電動弁。 The valve body has a body formed of a pipe material and a guide portion disposed inside the main body to guide the moving valve seat body, and the guide portion has the communication hole.
The electric valve according to any one of claims 1 to 7. 前記ガイド部と前記移動弁座体との間に第３弁室が形成され、前記連通孔を介して、前記第１弁室と前記第３弁室とが連通する、
ことを特徴とする請求項８に記載の電動弁。 A third valve chamber is formed between the guide portion and the moving valve seat body, and the first valve chamber and the third valve chamber communicate with each other through the communication hole.
The electric valve according to claim 8. 前記弁本体内において前記流体供給用の配管の下方に液だまり空間を有する、
ことを特徴とする請求項８又は９に記載の電動弁。 A liquid pool space is provided below the fluid supply pipe in the valve body.
The electric valve according to claim 8 or 9. 前記流体供給用の配管は、前記ガイド部に当接することにより位置決めされる、
ことを特徴とする請求項８〜１０のいずれか一項に記載の電動弁。

The fluid supply pipe is positioned by abutting on the guide portion.
The electric valve according to any one of claims 8 to 10.
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