JP7422409B2 - electric valve - Google Patents

electric valve Download PDF

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JP7422409B2
JP7422409B2 JP2021097288A JP2021097288A JP7422409B2 JP 7422409 B2 JP7422409 B2 JP 7422409B2 JP 2021097288 A JP2021097288 A JP 2021097288A JP 2021097288 A JP2021097288 A JP 2021097288A JP 7422409 B2 JP7422409 B2 JP 7422409B2
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hole
valve
rectifying
valve seat
electric valve
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JP2022188975A (en
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泰利 猪野
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Fujikoki Corp
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Fujikoki Corp
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Priority to CN202210257888.1A priority patent/CN115467983A/en
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Priority to JP2024001176A priority patent/JP2024038287A/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
    • F16K1/385—Valve members of conical shape contacting in the closed position, over a substantial axial length, a seat surface having the same inclination
    • 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
    • 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
    • F16K31/047—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/50—Mechanical actuating means with screw-spindle or internally threaded actuating 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

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

Description

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

冷凍サイクルにおいて流量制御弁として使用される電動弁は、モータにより回転駆動される弁軸の雄ねじ部を弁本体に設けられた雌ねじ孔に螺合させてなるねじ機構を有し、このねじ機構により回転運動を軸線方向運動に変換することによって、弁軸を軸線方向に変位させ、流量を制御している。 An electric valve used as a flow control valve in a refrigeration cycle has a screw mechanism in which the male threaded part of the valve shaft, which is rotationally driven by a motor, is screwed into a female threaded hole provided in the valve body. By converting rotational motion into axial motion, the valve shaft is displaced in the axial direction and the flow rate is controlled.

例えば特許文献１には、絞り機能と気泡細分化機能を発揮する多数の小孔を備えた薄板部材（パンチングプレート）を本体に取り付けて、冷媒を通過させる電動弁が開示されている。かかる薄板部材によれば、二相流状態で通過する冷媒の整流機能、絞り機能、二相流状態の冷媒中の気泡を細分化する機能を発揮し、気泡に起因する冷媒通過音を効果的に低減させることができる。 For example, Patent Document 1 discloses an electric valve in which a thin plate member (punching plate) having a large number of small holes that exhibits a throttling function and a bubble segmentation function is attached to a main body, and allows refrigerant to pass therethrough. According to such a thin plate member, the refrigerant passing in a two-phase flow state has a rectifying function, a throttling function, and a function to subdivide air bubbles in the refrigerant in a two-phase flow state, and can effectively reduce the sound of refrigerant passing caused by air bubbles. can be reduced to

特開２００７－１０７６２３号公報Japanese Patent Application Publication No. 2007-107623

冷凍サイクルにおいて、冷媒は、一般的には気液二相流状態で配管から電動弁の弁本体に流入するため、本来的に気泡を含んでいる。また、冷媒がオリフィスを通過する際に圧力降下が生じて、一部の冷媒が気化することにより気泡が発生する。このような気泡が破裂する際に騒音を発生することとなる。 In the refrigeration cycle, the refrigerant generally flows from piping into the valve body of the motor-operated valve in a gas-liquid two-phase flow state, so it inherently contains air bubbles. Further, when the refrigerant passes through the orifice, a pressure drop occurs, and some of the refrigerant vaporizes, thereby generating bubbles. When such bubbles burst, noise is generated.

特許文献１の電動弁によれば、気泡に起因する冷媒通過音を減少させることができるが、さらなる静穏化の余地がある。 According to the electric valve disclosed in Patent Document 1, it is possible to reduce the refrigerant passage noise caused by air bubbles, but there is still room for further quietening.

本発明者らは、特許文献１の電動弁において、オリフィスを通過した冷媒が、圧力回復の過程で薄板部材の小孔を通過し、より大径のパイプ内に進入する際に、乱流が発生して騒音が発生することを見出した。また、特許文献１の電動弁は薄板部材を必要とするため、部品点数が増加し、組み付けに手間がかかるという問題もある。 The present inventors discovered that in the electric valve of Patent Document 1, turbulence occurs when the refrigerant that has passed through the orifice passes through the small hole in the thin plate member and enters the larger diameter pipe during the pressure recovery process. It was discovered that this caused noise. Further, since the motor-operated valve of Patent Document 1 requires a thin plate member, the number of parts increases, and there are also problems in that it takes time and effort to assemble.

そこで本発明は、コストを抑制しつつ、騒音をさらに低減できる電動弁を提供することを目的とする。 Therefore, an object of the present invention is to provide an electric valve that can further reduce noise while suppressing costs.

上記課題を解決するために、本発明の電動弁は、
弁室を備えた弁本体と、
前記弁本体に取り付けられ、弁座を備えた弁座部材と、
前記弁室内に配置され、前記弁座に接近又は離間する方向に昇降可能な弁体と、を有し、
前記弁座部材は、配管に接続可能であり、前記弁座に隣接するオリフィス部と、前記オリフィス部に繋がる整流孔と、前記オリフィス部の端部に形成された底壁とを備えた電動弁であって、
前記電動弁の軸線と前記整流孔の中心軸線が通る面で前記電動弁を切断したときに、当該切断面において、前記弁座よりも前記底壁側において、前記電動弁の軸線と前記整流孔の中心軸線が交わり、
前記整流孔の中心軸線は、前記配管の内壁に交わることを特徴とする。 In order to solve the above problems, the electric valve of the present invention has the following features:
a valve body having a valve chamber;
a valve seat member attached to the valve body and including a valve seat;
a valve body disposed within the valve chamber and movable up and down in a direction toward or away from the valve seat;
The valve seat member is connectable to piping, and includes an orifice portion adjacent to the valve seat, a rectifying hole connected to the orifice portion, and a bottom wall formed at an end of the orifice portion. And,
When the motor-operated valve is cut along a plane through which the axis of the motor-operated valve and the central axis of the rectifier hole pass, in the cut plane, the axis of the motor-operated valve and the rectifier hole are closer to the bottom wall than the valve seat. The central axes of intersect,
The center axis of the rectifying hole intersects with the inner wall of the piping.

本発明によれば、コストを抑制しつつ、騒音をさらに低減できる電動弁を提供することができる。 According to the present invention, it is possible to provide an electric valve that can further reduce noise while suppressing costs.

図１は、本発明の第１の実施形態に係る電動弁を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing an electric valve according to a first embodiment of the present invention. 図２は、第１の実施形態に係る弁座部材の縦断面図である。FIG. 2 is a longitudinal sectional view of the valve seat member according to the first embodiment. 図３は、第１の実施形態に係る弁座部材を下方向から見た斜視図である。FIG. 3 is a perspective view of the valve seat member according to the first embodiment viewed from below. 図４は、第１の実施形態に係る弁座部材の下面図である。FIG. 4 is a bottom view of the valve seat member according to the first embodiment. 図５は、第２の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 5 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the second embodiment. 図６は、第３の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 6 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the third embodiment. 図７は、第４の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 7 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the fourth embodiment. 図８は、第５の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 8 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the fifth embodiment. 図９は、第６の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 9 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the sixth embodiment. 図１０は、第７の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 10 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the seventh embodiment. 図１１は、第８の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 11 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the eighth embodiment. 図１２は、第９の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 12 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the ninth embodiment. 図１３は、第１０の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 13 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the tenth embodiment. 図１４は、第１１の実施形態に係る電動弁に用いることができる弁座部材の縦断面図である。FIG. 14 is a longitudinal cross-sectional view of a valve seat member that can be used in the electric valve according to the eleventh embodiment. 図１５は、本実施形態の変形例に係る電動弁に用いることができる弁座部材と多孔質フィルタとを組み合わせた構成を示す図である。FIG. 15 is a diagram showing a configuration in which a valve seat member and a porous filter are combined, which can be used in an electric valve according to a modification of the present embodiment.

以下、図面を参照して、本発明にかかる実施形態について説明する。 Embodiments according to the present invention will be described below with reference to the drawings.

［第１の実施形態］
図１は、本発明の第１の実施形態に係る電動弁１を示す縦断面図である。ここで、電動弁１におけるロータ側を上方といい、ニードル弁側を下方という。また、「オリフィス」とは、開弁時におけるニードル弁と弁座との隙間をいい、隙間が最小となる位置のニードル弁の外径と弁座の内径とで形成される環状面の面積が「オリフィス断面積」である。「オリフィス部」とは、弁座から下流側の部位であって整流孔との境界までの流路をいう。さらに「流路断面積」とは、冷媒が流れる方向に直交する流路の断面積をいう。 [First embodiment]
FIG. 1 is a longitudinal sectional view showing an electric valve 1 according to a first embodiment of the present invention. Here, the rotor side of the motor-operated valve 1 is referred to as the upper side, and the needle valve side is referred to as the lower side. In addition, "orifice" refers to the gap between the needle valve and the valve seat when the valve is open, and the area of the annular surface formed by the outer diameter of the needle valve and the inner diameter of the valve seat at the position where the gap is minimum is This is the "orifice cross-sectional area." The “orifice portion” refers to a flow path located downstream from the valve seat and extending to the boundary with the rectifying hole. Further, the term "flow path cross-sectional area" refers to the cross-sectional area of the flow path perpendicular to the direction in which the refrigerant flows.

（流量制御弁の構成）
電動弁１は、上端が開口した有底円筒状の弁本体１０と、弁本体１０の上端面に下端部が溶接等により密封接合された有頂円筒状のキャン４５と、弁本体１０の内側に固定されたガイドステム１５と、ガイドステム１５の内側に配設された弁軸２１と、弁軸２１に対し一体的に回動可能に連結固定されたロータ３０と、を備えている。ロータ３０の周囲には、ロータ３０を回転駆動すべく、キャン４５の外周に外嵌されたステータが配設されるが、ここでは図示を省略する。ロータ３０とステータとで、ステッピングモータが構成される。電動弁１の軸線をＬとする。 (Configuration of flow control valve)
The electric valve 1 includes a bottomed cylindrical valve body 10 with an open upper end, a capped cylindrical can 45 whose lower end is hermetically joined to the upper end surface of the valve body 10 by welding, etc., and an inner side of the valve body 10. The valve shaft 21 includes a guide stem 15 fixed to the guide stem 15, a valve shaft 21 disposed inside the guide stem 15, and a rotor 30 connected and fixed to the valve shaft 21 so as to be integrally rotatable. A stator fitted around the outer periphery of the can 45 is disposed around the rotor 30 in order to rotationally drive the rotor 30, but is not shown here. The rotor 30 and the stator constitute a stepping motor. Let L be the axis of the electric valve 1.

弁本体１０は、中空円筒部１０ａと底壁部１０ｂとを連設してなる。弁本体１０はＳＵＳ製の板材をプレス成形することによって形成できるが、ＳＵＳ素材を圧造することによって形成してもよい。ただし、弁本体１０は、ＳＵＳ（ステンレス）以外の素材（例えば真鍮）を用いることができるし、プレス加工や圧造以外の加工方法（例えば削り出し加工)を用いても形成できる。 The valve body 10 is made up of a hollow cylindrical portion 10a and a bottom wall portion 10b. The valve body 10 can be formed by press-molding a SUS plate material, but may also be formed by forging a SUS material. However, the valve body 10 can be made of a material other than SUS (stainless steel) (for example, brass), and can also be formed using a processing method other than pressing or heading (for example, cutting).

底壁部１０ｂにおいて、その中央に円形の開口１０ｄが形成されており、開口１０ｄには、弁座部材１１がロウ付け等で固定されている。 A circular opening 10d is formed in the center of the bottom wall portion 10b, and the valve seat member 11 is fixed to the opening 10d by brazing or the like.

図２は、弁座部材１１の縦断面図であり、図３は、弁座部材１１を下方向から見た斜視図であり、図４は、弁座部材１１の下面図である。 2 is a longitudinal sectional view of the valve seat member 11, FIG. 3 is a perspective view of the valve seat member 11 seen from below, and FIG. 4 is a bottom view of the valve seat member 11.

略円筒状の弁座部材１１は、上部円筒部１１ａと、上部円筒部１１ａより大径の中部円筒部１１ｂと、中部円筒部１１ｂより大径の下部円筒部１１ｃと、中部円筒部１１ｂと下部円筒部１１ｃの境界付近から径方向内方へと延在する隔壁部１１ｄと、隔壁部１１ｄから下方に向かって延在する内側円筒部１１ｅとを連設してなる。内側円筒部１１ｅの下端は、円錐台形部１１ｆを備える。 The substantially cylindrical valve seat member 11 includes an upper cylindrical part 11a, a middle cylindrical part 11b having a larger diameter than the upper cylindrical part 11a, a lower cylindrical part 11c having a larger diameter than the middle cylindrical part 11b, and a middle cylindrical part 11b and a lower part. The partition wall 11d extends radially inward from near the boundary of the cylindrical portion 11c, and the inner cylindrical portion 11e extends downward from the partition wall 11d. The lower end of the inner cylindrical portion 11e includes a truncated conical portion 11f.

中部円筒部１１ｂが開口１０ｄに嵌合し、上部円筒部１１ａは弁本体１０の内部に突出し、下部円筒部１１ｃは弁本体１０の外部に配設される。また下部円筒部１１ｃと、内側円筒部１１ｅとの間には、環状空間ＳＰが形成される。下部円筒部１１ｃの下端内周側には、段部１１ｇが形成されている。環状空間ＳＰ内に進入させた第一の配管Ｔ１(図１)の端部が、内側円筒部１１ｅの外周に嵌挿され、ロウ付けなどにより接続される。段部１１ｇは、配管Ｔ１をロウ付けする際に、ロウ材を貯留する部位となる。 The middle cylindrical part 11b fits into the opening 10d, the upper cylindrical part 11a projects inside the valve body 10, and the lower cylindrical part 11c is arranged outside the valve body 10. Further, an annular space SP is formed between the lower cylindrical portion 11c and the inner cylindrical portion 11e. A stepped portion 11g is formed on the inner peripheral side of the lower end of the lower cylindrical portion 11c. The end of the first pipe T1 (FIG. 1) entered into the annular space SP is fitted onto the outer periphery of the inner cylindrical portion 11e and connected by brazing or the like. The stepped portion 11g serves as a portion for storing brazing material when brazing the pipe T1.

内側円筒部１１ｅの上端から軸線Ｌに沿って下方に向かい、底壁１１ｈまで延在する円筒孔１１ｉが軸線Ｌと同軸に形成されている。円筒孔１１ｉの下端外周から斜め外方に延在する整流孔１１ｊが、周方向に分岐して等間隔に４本形成されており、各整流孔１１ｊの外方端は、円錐台形部１１ｆの外周面に位置する。このため整流孔１１ｊは、弁座部材１１に組付けた第一の配管Ｔ１の内壁を向いており、具体的には整流孔１１ｊの中心軸線Ｘに沿って整流孔１１ｊの断面を投影したときに、その投影像は第一の配管Ｔ１の内壁と重なる。換言すれば、整流孔１１ｊの中心軸線Ｘは第一の配管Ｔ１の内壁と交差する。整流孔１１ｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θ（中心軸線Ｘとの交点から下方に延在する軸線Ｌと、中心軸線Ｘとで挟む角とする、以下同じ）で交差する。整流孔１１ｊの数は、２本、３本あるいは５本以上であってもよいが、周方向に等間隔に配置されていると好ましい。円筒孔１１ｉがオリフィス部を構成する。内側円筒部１１ｅの上端内周には、弁座１１ｋが形成されている。なお、中心軸線Ｘと軸線Ｌが空間的に交差しない(ねじれの関係となる）ように配置した構造では、側面視（軸線Ｌの直交方向からの視点)で中心軸線Ｘと軸線Ｌの交差する角度を交差角θとする。 A cylindrical hole 11i is formed coaxially with the axis L, extending downward from the upper end of the inner cylindrical portion 11e to the bottom wall 11h. Four rectifying holes 11j extending obliquely outward from the outer periphery of the lower end of the cylindrical hole 11i are branched in the circumferential direction and formed at equal intervals, and the outer end of each rectifying hole 11j is connected to the truncated conical portion 11f. Located on the outer surface. Therefore, the rectifying hole 11j faces the inner wall of the first pipe T1 assembled to the valve seat member 11, and specifically, when the cross section of the rectifying hole 11j is projected along the central axis X of the rectifying hole 11j. Then, the projected image overlaps with the inner wall of the first pipe T1. In other words, the center axis X of the rectifying hole 11j intersects with the inner wall of the first pipe T1. The central axis X of the rectifying hole 11j is at an intersection angle θ greater than 0 degrees and less than 90 degrees with respect to the axis L (an angle between the axis L extending downward from the intersection with the central axis X and the central axis X). , hereinafter the same). The number of rectifying holes 11j may be two, three, or five or more, but it is preferable that they are arranged at equal intervals in the circumferential direction. The cylindrical hole 11i constitutes an orifice portion. A valve seat 11k is formed on the inner periphery of the upper end of the inner cylindrical portion 11e. In addition, in a structure arranged so that the central axis X and the axis L do not intersect spatially (in a twisted relationship), the central axis X and the axis L intersect in a side view (viewed from a direction orthogonal to the axis L). Let the angle be the intersection angle θ.

本実施形態において、整流孔１１ｊの長さは、整流孔１１ｊの内径より長く、また円筒孔１１ｉの内周半径より長い。整流孔１１ｊの長さとは、軸線Ｌ及び中心軸線Ｘを通る面で電動弁１を切断した断面(ここでは図２)において、整流孔１１ｊの内壁が中心軸線Ｘを挟んだ一対の線分として表され、該内壁の線分の一端同士を結ぶ直線（図２の点線）ＰＬ１と、他端同士を結ぶ直線（図２の点線）ＰＬ２に、整流孔１１ｊの中心軸線Ｘが点ＰＴ１、ＰＴ２で交差したときに、その点ＰＴ１、ＰＴ２間の距離をいう。 In this embodiment, the length of the rectifying hole 11j is longer than the inner diameter of the rectifying hole 11j and longer than the inner peripheral radius of the cylindrical hole 11i. The length of the rectifying hole 11j is defined as the length of the inner wall of the rectifying hole 11j as a pair of line segments sandwiching the central axis X in a cross section of the electric valve 1 taken along the axis L and the central axis The central axis X of the rectifying hole 11j is located at points PT1 and PT2 on a straight line (dotted line in FIG. 2) PL1 connecting one end of the line segment of the inner wall and a straight line PL2 (dotted line in FIG. 2) connecting the other ends of the line segment. This is the distance between the points PT1 and PT2 when they intersect.

さらに、４本の整流孔１１ｊの流路断面積の合計は、ニードル弁(弁体)２５の最大リフト時(最大開弁時)における円錐部２５ｄと弁座１１ｋとの間に形成される流路断面積（すなわちオリフィス断面積）よりも大きい。また、円筒孔１１ｉの流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１ｊの流路断面積の合計は、円筒孔１１ｉの流路断面積より大きいと好ましい。 Furthermore, the total cross-sectional area of the flow passages of the four rectifying holes 11j is the flow rate formed between the conical portion 25d and the valve seat 11k when the needle valve (valve body) 25 is at its maximum lift (at its maximum opening). larger than the path cross-sectional area (i.e., the orifice cross-sectional area). Further, the flow passage cross-sectional area of the cylindrical hole 11i is greater than or equal to the orifice cross-sectional area at the maximum valve opening. The total cross-sectional area of the flow passages of the rectifying holes 11j is preferably larger than the cross-sectional area of the flow passages of the cylindrical holes 11i.

図１において、弁本体１０の中空円筒部１０ａには、入口開口１０ｅが形成されており、入口開口１０ｅに第二の配管Ｔ２の端部が嵌挿され、ロウ付けなどにより接続されている。入口開口１０ｅの軸線をＯとする。 In FIG. 1, an inlet opening 10e is formed in the hollow cylindrical portion 10a of the valve body 10, and the end of the second pipe T2 is fitted into the inlet opening 10e and connected by brazing or the like. Let O be the axis of the inlet opening 10e.

弁本体１０の上端にキャン４５の下端が突き当てられた状態で、キャン４５の下端内周に鍔状円盤１８が嵌合しており、これらは溶接により接合されている。これにより、弁本体１０とキャン４５とが密閉した状態で一体化される。 With the lower end of the can 45 abutting against the upper end of the valve body 10, the flange-shaped disc 18 is fitted to the inner periphery of the lower end of the can 45, and these are joined by welding. Thereby, the valve body 10 and the can 45 are integrated in a sealed state.

鍔状円盤１８は、複数の貫通孔(不図示)を備えており、この貫通孔を介して、冷媒が弁本体１０側とキャン４５側との間で移動することは可能になる。 The brim-like disk 18 includes a plurality of through holes (not shown), and the refrigerant can move between the valve body 10 side and the can 45 side via the through holes.

ロータ３０の内側に配設された樹脂製のガイドステム１５は、中実円筒状の本体１５ａと、中空円筒部１５ｂとを連設してなる。本体１５ａは、軸線Ｌに沿って雌ねじ孔１５ｃを有する。またガイドステム１５の上方に、閉弁方向用可動ストッパ３５を設置している。 The guide stem 15 made of resin and arranged inside the rotor 30 is made up of a solid cylindrical main body 15a and a hollow cylindrical portion 15b. The main body 15a has a female screw hole 15c along the axis L. Further, a movable stopper 35 for the valve closing direction is installed above the guide stem 15.

中空円筒部１５ｂの中間部外周には、弁本体１０の上端に溶接された鍔状円盤１８が配設されており、この鍔状円盤１８を介して、ガイドステム１５は弁本体１０に対して固定される。中空円筒部１５ｂには、均圧穴１５ｄが形成されている。 A flange-shaped disk 18 welded to the upper end of the valve body 10 is disposed on the outer periphery of the intermediate portion of the hollow cylindrical portion 15b, and the guide stem 15 is attached to the valve body 10 via this flange-shaped disk 18. Fixed. A pressure equalizing hole 15d is formed in the hollow cylindrical portion 15b.

また、ロータ３０及び弁軸２１の制御用原点位置を設定すべく、ガイドステム１５の本体１５ａの上面には、断面矩形状の閉弁方向用固定ストッパ５５が上向きに突設されており、またガイドステム１５の本体１５ａの下面には、断面矩形状の開弁方向用固定ストッパ５６が下向きに突設されている。ここで、ロータ３０及び弁軸２１の制御用原点位置とは、閉弁方向用可動ストッパ３５が閉弁方向用固定ストッパ５５に当接して係止され、ロータ３０及び弁軸２１が最下降位置に達した時の位置のことである。 Further, in order to set the control origin positions of the rotor 30 and the valve shaft 21, a fixed stopper 55 for the valve closing direction with a rectangular cross section is provided upwardly protruding on the upper surface of the main body 15a of the guide stem 15. On the lower surface of the main body 15a of the guide stem 15, a fixed stopper 56 for the valve opening direction having a rectangular cross section is provided to protrude downward. Here, the control origin position of the rotor 30 and the valve shaft 21 means that the movable stopper 35 for the valve closing direction abuts and locks the fixed stopper 55 for the valve closing direction, and the rotor 30 and the valve shaft 21 are at the lowest position. It is the position when the point is reached.

金属製の弁軸２１は、ロータ３０に取り付けられた環状の連結体３２が外嵌した端部２１ａと、雌ねじ孔１５ｃに螺合する雄ねじ部２１ｂと、下端近傍に形成された鍔状部２１ｃと、下端連結部２１ｄとを同軸に連設してなる。 The metal valve shaft 21 has an end portion 21a into which an annular connecting body 32 attached to the rotor 30 is fitted, a male screw portion 21b that screws into the female screw hole 15c, and a flange portion 21c formed near the lower end. and the lower end connecting portion 21d are coaxially connected.

弁軸２１に固定された閉弁方向用可動ストッパ３５が、雄ねじ部２１ｂの上端付近に配設され、ロータ３０の上壁下面に係止されている。閉弁方向用可動ストッパ３５の下面には、断面矩形状のストッパ部３５ａが形成されている。 A movable stopper 35 for the valve closing direction fixed to the valve shaft 21 is disposed near the upper end of the male threaded portion 21b and is locked to the lower surface of the upper wall of the rotor 30. A stopper portion 35a having a rectangular cross section is formed on the lower surface of the movable stopper 35 for the valve closing direction.

また、弁軸２１の雄ねじ部２１ｂの下端近傍には、鍔状部２１ｃの上面に突き当てるようにして、開弁方向用可動ストッパ３６が圧入により嵌合している。開弁方向用可動ストッパ３６の上面には、断面矩形状のストッパ部３６ａが形成されている。ここでは、開弁方向用可動ストッパ３６の内周に雌ねじを形成して、雄ねじ部２１ｂと螺合させることにより、開弁方向用可動ストッパ３６と弁軸２１との固定を行っている。 Further, a movable stopper 36 for the valve opening direction is press-fitted near the lower end of the male threaded portion 21b of the valve shaft 21 so as to abut against the upper surface of the brim portion 21c. A stopper portion 36a having a rectangular cross section is formed on the upper surface of the movable stopper 36 for the valve opening direction. Here, the movable stopper 36 for the valve opening direction and the valve shaft 21 are fixed by forming a female thread on the inner periphery of the movable stopper 36 for the valve opening direction and screwing it into the male threaded portion 21b.

弁軸２１の下方において、弁ホルダ２３が、中空円筒部１５ｂの内側に摺動可能に嵌合して配設されている。弁ホルダ２３は、中空円筒部２３ａと、上壁２３ｂとを連設した有頂円筒形状を有している。上壁２３ｂの中央には、段付き開口２３ｃが形成されており、中空円筒部２３ａは連通穴２３ｄを有する。弁ホルダ２３の中空円筒部２３ａの開放した下端は、閉弁状態で第二の配管Ｔ２より下方に配設され、カシメ固定された環状部材２７により閉止されている。 A valve holder 23 is disposed below the valve shaft 21 so as to be slidably fitted inside the hollow cylindrical portion 15b. The valve holder 23 has a cylindrical shape with a top and a hollow cylindrical portion 23a and an upper wall 23b. A stepped opening 23c is formed in the center of the upper wall 23b, and the hollow cylindrical portion 23a has a communication hole 23d. The open lower end of the hollow cylindrical portion 23a of the valve holder 23 is disposed below the second pipe T2 in the closed state and is closed by an annular member 27 fixed by caulking.

段付き開口２３ｃの段部に弁軸２１の鍔状部２１ｃが当接した状態で、下端連結部２１ｄが段付き開口２３ｃを貫通しており、この下端連結部２１ｄを拡径するようにカシメ加工することで、弁軸２１と弁ホルダ２３とが固定連結されている。弁本体１０と弁ホルダ２３との間に、弁室２９が画成される。 With the flanged portion 21c of the valve shaft 21 in contact with the stepped portion of the stepped opening 23c, the lower end connecting portion 21d passes through the stepped opening 23c, and the lower end connecting portion 21d is caulked to expand its diameter. By machining, the valve shaft 21 and the valve holder 23 are fixedly connected. A valve chamber 29 is defined between the valve body 10 and the valve holder 23.

環状部材２７を通して弁ホルダ２３から突出するようにして、ニードル弁２５が配置されている。ニードル弁２５は、円柱状の軸部２５ａと、弁鍔部２５ｂと、弁円筒部２５ｃと、下方に向かうにしたがって縮径する円錐部２５ｄと、複数の円錐形状を段階的に形成した先細部２５ｅとを連設してなる。円錐部２５ｄのテーパ角(軸線Ｌと交差する角度）は、円錐部２５ｄに接する先細部２５ｅのテーパ角よりも大きい。 A needle valve 25 is arranged to protrude from the valve holder 23 through the annular member 27 . The needle valve 25 includes a cylindrical shaft portion 25a, a valve collar portion 25b, a valve cylindrical portion 25c, a conical portion 25d whose diameter decreases toward the bottom, and a tapered portion in which a plurality of conical shapes are formed in stages. 25e are installed in series. The taper angle (the angle that intersects the axis L) of the conical portion 25d is larger than the taper angle of the tapered portion 25e that is in contact with the conical portion 25d.

軸部２５ａの外周には、リング状部材３１が圧入等により嵌合している。リング状部材３１の外径は、環状部材２７の内径より大きいため、弁ホルダ２３からニードル弁２５が脱落することが阻止される。リング状部材３１と環状部材２７との間には、ワッシャ２８が配設されており、リング状部材３１と環状部材２７との相対回転時の摩擦を軽減する。 A ring-shaped member 31 is fitted onto the outer periphery of the shaft portion 25a by press-fitting or the like. Since the outer diameter of the ring-shaped member 31 is larger than the inner diameter of the annular member 27, the needle valve 25 is prevented from falling off from the valve holder 23. A washer 28 is disposed between the ring-shaped member 31 and the annular member 27 to reduce friction when the ring-shaped member 31 and the annular member 27 rotate relative to each other.

弁ホルダ２３の上壁２３ｂと、ニードル弁２５との間に、下端鍔部２６ａを有する円筒状のばね受け部材２６が配設されている。さらに上壁２３ｂと下端鍔部２６ａとの間には、コイルバネ２４が配設され、弁ホルダ２３に対してばね受け部材２６を下方に向かって付勢している。 A cylindrical spring receiving member 26 having a lower end flange 26a is disposed between the upper wall 23b of the valve holder 23 and the needle valve 25. Further, a coil spring 24 is disposed between the upper wall 23b and the lower end flange 26a, and biases the spring receiving member 26 downward with respect to the valve holder 23.

円錐部２５ｄが弁座部材１１の弁座１１ｋに着座して、上方に向かう反力を受けたときに、ニードル弁２５により上向きに付勢されたばね受け部材２６が弁ホルダ２３の上壁２３ｂの下面（または下端連結部２１ｄ）に当接することで、ニードル弁２５は弁軸２１に対して軸線方向に係止される。 When the conical portion 25d is seated on the valve seat 11k of the valve seat member 11 and receives an upward reaction force, the spring receiving member 26, which is urged upward by the needle valve 25, pushes against the upper wall 23b of the valve holder 23. By coming into contact with the lower surface (or the lower end connecting portion 21d), the needle valve 25 is locked to the valve shaft 21 in the axial direction.

上記した弁軸２１、弁ホルダ２３、ニードル弁２５、及びコイルバネ２４は、ニードル弁２５が弁座１１ｋから離間している状態（開弁状態）においては、ガイドステム１５に対して実質的に一体的に回転しながら昇降する。 The above-mentioned valve shaft 21, valve holder 23, needle valve 25, and coil spring 24 are substantially integral with the guide stem 15 when the needle valve 25 is spaced apart from the valve seat 11k (open state). Go up and down while rotating.

（流量制御弁の動作）
電動弁１の動作を、具体的に説明する。
ここで、第二の配管Ｔ２から弁室２９内に冷媒（流体）が進入しているものとする。 (Operation of flow control valve)
The operation of the electric valve 1 will be specifically explained.
Here, it is assumed that the refrigerant (fluid) is entering the valve chamber 29 from the second pipe T2.

外部の制御装置から不図示のステータにパルス給電が行われることにより、ロータ３０及び弁軸２１が一方向に回転駆動され、雌ねじ孔１５ｃと雄ねじ部２１ｂからなるねじ送り機構により、弁軸２１及び閉弁方向用可動ストッパ３５が回転しながら下降し、ニードル弁２５が弁座１１ｋに着座してオリフィスが閉止される。これにより、弁室２９から第一の配管Ｔ１側へ向かう冷媒の流れを遮断する。 By supplying pulse power to a stator (not shown) from an external control device, the rotor 30 and the valve shaft 21 are rotationally driven in one direction. The movable stopper 35 for the valve closing direction is rotated and lowered, and the needle valve 25 is seated on the valve seat 11k, and the orifice is closed. This blocks the flow of refrigerant from the valve chamber 29 toward the first pipe T1.

この時点では、可動ストッパ３５は未だ固定ストッパ５５に当接しておらず、ロータ３０及び弁軸２１の回転下降は停止されず、コイルバネ２４が所定量圧縮されるまでパルス給電が継続される。それにより、ニードル弁２５が弁座１１ｋに着座したまま回転が制止される一方、ロータ３０、弁軸２１、弁ホルダ２３等はさらに回転しながら下降する。 At this point, the movable stopper 35 has not yet come into contact with the fixed stopper 55, and the rotation and descent of the rotor 30 and the valve shaft 21 is not stopped, and the pulse power supply continues until the coil spring 24 is compressed by a predetermined amount. As a result, the rotation of the needle valve 25 is stopped while remaining seated on the valve seat 11k, while the rotor 30, valve shaft 21, valve holder 23, etc. further rotate and descend.

このとき、着座したニードル弁２５に対して弁軸２１及び弁ホルダ２３が下降するため、コイルバネ２４が縮長圧縮され、これにより弁軸２１及び弁ホルダ２３の下降力が吸収される。その後、コイルバネ２４の圧縮量が所定量となったとき、可動ストッパ３５が固定ストッパ５５に当接して係止され、ロータ３０及び弁軸２１が最下降位置に達し、ステータに対しパルス給電が継続されてもロータ３０及び弁軸２１の下降は強制的に停止される。 At this time, since the valve shaft 21 and the valve holder 23 are lowered relative to the seated needle valve 25, the coil spring 24 is compressed and compressed, thereby absorbing the downward force of the valve shaft 21 and the valve holder 23. Thereafter, when the amount of compression of the coil spring 24 reaches a predetermined amount, the movable stopper 35 comes into contact with the fixed stopper 55 and is locked, the rotor 30 and the valve shaft 21 reach the lowest position, and pulse power supply to the stator continues. Even if the rotor 30 and the valve shaft 21 are lowered, the lowering of the rotor 30 and the valve shaft 21 is forcibly stopped.

このように、ニードル弁２５が弁座１１ｋに着座してオリフィス１１ｄが閉止された後においても、可動ストッパ３５が固定ストッパ５５に当接して係止される制御用原点位置に達するまでは、ロータ３０、弁軸２１、及び弁ホルダ２３の回転下降が継続されることにより、コイルバネ２４が圧縮される。そのため、コイルバネ２４の付勢力によりニードル弁２５が弁座１１ｋに強く押し付けられ、冷媒漏れ等を確実に防止できる。 In this way, even after the needle valve 25 is seated on the valve seat 11k and the orifice 11d is closed, the rotor remains in position until the movable stopper 35 comes into contact with the fixed stopper 55 and reaches the control origin position. 30, the valve shaft 21, and the valve holder 23 continue to rotate and descend, thereby compressing the coil spring 24. Therefore, the needle valve 25 is strongly pressed against the valve seat 11k by the urging force of the coil spring 24, and refrigerant leakage etc. can be reliably prevented.

一方、上記制御用原点位置からステータに、逆極性のパルス給電を行うと、ロータ３０及び弁軸２１が閉弁時とは逆方向に回転駆動され、雌ねじ孔１５ｃと雄ねじ部２１ｂからなるねじ送り機構により、ロータ３０、弁軸２１、弁ホルダ２３及び開弁方向用可動ストッパ３６が回転しながら上昇する。これに伴い、ニードル弁２５に対する押圧力が弱められ、コイルバネ２４が伸張して、ニードル弁２５が弁座１１ｋから離れると、オリフィスが開放される。これにより、第二の配管Ｔ２から弁室２９内へと進入した冷媒は、円錐部２５ｄと弁座１１ｋとの間の隙間を通過して、円筒孔１１ｉを通って第一の配管Ｔ１へと流れる。 On the other hand, when pulse power of opposite polarity is supplied to the stator from the control origin position, the rotor 30 and the valve shaft 21 are driven to rotate in the opposite direction to the direction when the valve is closed, and the screw feed consisting of the female threaded hole 15c and the male threaded portion 21b is driven. Due to the mechanism, the rotor 30, the valve shaft 21, the valve holder 23, and the movable stopper 36 for the valve opening direction move up while rotating. Accordingly, the pressing force on the needle valve 25 is weakened, the coil spring 24 is expanded, and when the needle valve 25 is separated from the valve seat 11k, the orifice is opened. As a result, the refrigerant that has entered the valve chamber 29 from the second pipe T2 passes through the gap between the conical portion 25d and the valve seat 11k, passes through the cylindrical hole 11i, and enters the first pipe T1. flows.

この場合、ステータへのパルス給電に応じてニードル弁２５のリフト量が定まるため、冷媒の流量制御を行える。さらにパルス給電を続けることで、最終的にニードル弁２５が全開状態となる。さらにパルス給電が継続された場合、可動ストッパ３６が開弁方向用固定ストッパ５６に当接して係止され、これにより、ロータ３０、弁軸２１、及び弁ホルダ２３の回転及び上昇が強制的に停止せしめられる。 In this case, since the lift amount of the needle valve 25 is determined according to the pulse power supply to the stator, the flow rate of the refrigerant can be controlled. By further continuing the pulse power supply, the needle valve 25 is finally fully opened. When the pulse power supply continues further, the movable stopper 36 comes into contact with the fixed stopper 56 for the valve opening direction and is locked, thereby forcing the rotor 30, the valve shaft 21, and the valve holder 23 to rotate and rise. forced to stop.

本実施形態によれば、開弁時に円錐部２５ｄと弁座１１ｋとの間の隙間を通過して、弁座部材１１の円筒孔１１ｉに進入した冷媒は、底壁１１ｈに当接して流れの向きを変えられ、円筒状の整流孔１１ｊを介して弁座部材１１の外部へと流出する。このとき、冷媒は整流孔１１ｊを通過することで整流効果が発揮されるため、気液二相状態中の気泡及びオリフィス通過時に発生した気泡を微小化して、気泡が破裂した際の騒音を低減できる。また、冷媒が４本の整流孔１１ｊを通過することで、流れの力が分散され、圧力回復が早まり、騒音の原因となる気泡の発生を抑制できる。また、弁座部材１１に整流効果を持たせることで、別個に整流部材を設ける必要がなくなり、部品点数が削減される。 According to this embodiment, when the valve is opened, the refrigerant that has passed through the gap between the conical portion 25d and the valve seat 11k and entered the cylindrical hole 11i of the valve seat member 11 comes into contact with the bottom wall 11h and the flow is stopped. The direction is changed and flows out of the valve seat member 11 through the cylindrical rectifying hole 11j. At this time, the refrigerant exerts a rectifying effect by passing through the rectifying hole 11j, so the bubbles in the gas-liquid two-phase state and the bubbles generated when passing through the orifice are miniaturized, reducing the noise when the bubbles burst. can. Furthermore, since the refrigerant passes through the four straightening holes 11j, the force of the flow is dispersed, pressure recovery is accelerated, and the generation of bubbles that cause noise can be suppressed. Further, by providing the valve seat member 11 with a rectifying effect, there is no need to provide a separate rectifying member, and the number of parts can be reduced.

加えて、本実施形態によれば、オリフィス部である円筒孔１１ｉを通過した冷媒を、整流孔１１ｊから第一の配管Ｔ１の内壁に衝突させるように流出させているため、冷媒の流速を強制的に低減し、乱流が発生する前に冷媒圧力を回復させることができる。これにより、騒音の原因となる気泡の発生を抑制できる。 In addition, according to the present embodiment, the refrigerant that has passed through the cylindrical hole 11i, which is the orifice portion, flows out from the rectifying hole 11j so as to collide with the inner wall of the first pipe T1, so that the flow rate of the refrigerant is forced. This allows the refrigerant pressure to be restored before turbulence occurs. This makes it possible to suppress the generation of bubbles that cause noise.

なお、冷媒が第一の配管Ｔ１から第二の配管Ｔ２に向かって流れる場合、第一の配管Ｔ１から弁座部材１１内に進入した冷媒は、整流孔１１ｊによって流れの向きを変えられ、ストレートにオリフィスに向かわない。したがって、流速が早い冷媒がオリフィスを通過しないため、開弁時におけるニードル弁２５の振動を抑制できる。 Note that when the refrigerant flows from the first pipe T1 toward the second pipe T2, the refrigerant that has entered the valve seat member 11 from the first pipe T1 is changed in flow direction by the rectifying hole 11j and flows straight. does not go toward the orifice. Therefore, since the refrigerant having a high flow rate does not pass through the orifice, vibration of the needle valve 25 when the valve is opened can be suppressed.

［第２の実施形態］
図５は、第２の実施形態に係る電動弁に用いることができる弁座部材１１Ａの縦断面図である。弁座部材１１Ａ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Second embodiment]
FIG. 5 is a longitudinal sectional view of a valve seat member 11A that can be used in the electric valve according to the second embodiment. The electrically operated valve configuration other than the valve seat member 11A is the same as that of the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ａは、図２に示す弁座部材１１に対して、底壁１１Ａｈに、円筒孔１１Ａｉの下端となるテーパ状部１１Ａｍを形成した点が主として異なる。テーパ状部１１Ａｍの一部に、整流孔１１Ａｊが接している。整流孔１１Ａｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ａｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。本実施形態においても、内側円筒部１１Ａｅの下端は、円錐台形部１１Ａｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11A of this embodiment differs from the valve seat member 11 shown in FIG. 2 mainly in that a tapered portion 11Am, which becomes the lower end of the cylindrical hole 11Ai, is formed on the bottom wall 11Ah. A rectifying hole 11Aj is in contact with a part of the tapered portion 11Am. The center axis X of the rectifying hole 11Aj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Aj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. Also in this embodiment, the lower end of the inner cylindrical portion 11Ae includes a truncated conical portion 11Af. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ａｉに沿って流れてテーパ状部１１Ａｍに至る。冷媒の少なくとも一部はテーパ状部１１Ａｍで滞留した後、整流孔１１Ａｊに進入するため、冷媒圧力を回復させやすいという効果がある。また、冷媒がテーパ状部１１Ａｍのエッジ部を通過する際に、気泡を分散化する効果もある。なお、テーパ状部１１Ａｍは、例えばドリルなどの切削工具を用いて円筒孔１１Ａｉを形成する際に、工具先端形状を転写することで形成できる。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Ai, which is the orifice portion, and reaches the tapered portion 11Am. At least a portion of the refrigerant remains in the tapered portion 11Am and then enters the rectifying hole 11Aj, which has the effect of easily restoring the refrigerant pressure. Further, when the refrigerant passes through the edge portion of the tapered portion 11Am, there is also an effect of dispersing air bubbles. Note that the tapered portion 11Am can be formed, for example, by transferring the shape of the tip of the tool when forming the cylindrical hole 11Ai using a cutting tool such as a drill.

［第３の実施形態］
図６は、第３の実施形態に係る電動弁に用いることができる弁座部材１１Ｂの縦断面図である。弁座部材１１Ｂ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Third embodiment]
FIG. 6 is a longitudinal sectional view of a valve seat member 11B that can be used in the electric valve according to the third embodiment. The electrically operated valve configuration other than the valve seat member 11B is the same as that of the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ｂは、図２に示す弁座部材１１に対して、各整流孔１１Ｂｊの中間位置から、軸線Ｌに平行に底壁１１Ｂｈを貫通して、端部が円錐台形部１１ｆの頂面(下面)に位置する連通開口１１Ｂｍを形成した点が主として異なる。連通開口１１Ｂｍの内径は、整流孔Ｂｊの内径の１／４以下であると好ましい。整流孔１１Ｂｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｂｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。本実施形態においても、内側円筒部１１Ｂｅの下端は、円錐台形部１１Ｂｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11B of this embodiment penetrates the bottom wall 11Bh parallel to the axis L from the intermediate position of each rectifying hole 11Bj with respect to the valve seat member 11 shown in FIG. 2, and has a truncated conical end. The main difference is that a communication opening 11Bm located on the top surface (lower surface) of 11f is formed. The inner diameter of the communication opening 11Bm is preferably 1/4 or less of the inner diameter of the rectifying hole Bj. The center axis X of the rectifying hole 11Bj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Bj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. Also in this embodiment, the lower end of the inner cylindrical portion 11Be includes a truncated conical portion 11Bf. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｂｉに沿って流れて底壁１１Ｂｈに至る。ここから、冷媒は整流孔１１Ｂｊを通過して弁座部材１１Ｂの外部へと流出するが、その際に第一の配管Ｔ１の内壁に衝突して渦を形成することがある。かかる渦が冷媒の圧力回復を妨げるおそれがある。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Bi, which is the orifice portion, and reaches the bottom wall 11Bh. From here, the refrigerant passes through the rectifying hole 11Bj and flows out of the valve seat member 11B, but at that time, it may collide with the inner wall of the first pipe T1 and form a vortex. Such a vortex may hinder pressure recovery of the refrigerant.

これに対し、本実施形態によれば、冷媒が連通開口１１Ｂｍの上端を通過する際に連通開口１１Ｂｍの内部に負圧が発生するため、連通開口１１Ｂｍの下端から冷媒を吸い上げる。これにより、第一の配管Ｔ１の内壁に衝突して形成される渦を速やかに消失させることができる。 In contrast, according to the present embodiment, negative pressure is generated inside the communication opening 11Bm when the refrigerant passes through the upper end of the communication opening 11Bm, so the refrigerant is sucked up from the lower end of the communication opening 11Bm. Thereby, the vortex formed by colliding with the inner wall of the first pipe T1 can be quickly eliminated.

［第４の実施形態］
図７は、第４の実施形態に係る電動弁に用いることができる弁座部材１１Ｃの縦断面図である。弁座部材１１Ｃ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Fourth embodiment]
FIG. 7 is a longitudinal sectional view of a valve seat member 11C that can be used in the electric valve according to the fourth embodiment. The electric valve configuration other than the valve seat member 11C is the same as that in the first embodiment, and therefore, repeated explanation will be omitted.

本実施形態の弁座部材１１Ｃは、内側円筒部１１Ｃｅおよび整流孔１１Ｃｊの形状が主として異なる。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11C of this embodiment differs mainly in the shapes of the inner cylindrical portion 11Ce and the rectifying hole 11Cj. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

隔壁部１１ｄから下方に向かって延在する内側円筒部１１Ｃｅは、隔壁部１１ｄ側の拡径部１１Ｃｅ１と、拡径部１１Ｃｅ１より外径が小さい先端側の縮径部１１Ｃｅ２とからなる。第一の配管Ｔ１（図１）は、拡径部１１Ｃｅ１にのみ嵌合する。 The inner cylindrical portion 11Ce extending downward from the partition wall portion 11d is composed of an enlarged diameter portion 11Ce1 on the partition wall portion 11d side and a reduced diameter portion 11Ce2 on the tip side having a smaller outer diameter than the enlarged diameter portion 11Ce1. The first pipe T1 (FIG. 1) fits only into the enlarged diameter portion 11Ce1.

内側円筒部１１Ｃｅの内部に形成された円筒孔１１Ｃｉの下端から、複数の整流孔１１Ｃｊが弁座１１ｋ側に向かって斜めに延在するように形成されている。整流孔１１Ｃｊは、弁座部材１１Ｃに組付けた第一の配管Ｔ１の内壁を向いている。すなわち整流孔１１Ｃｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｃｊの中心軸線Ｘは、軸線Ｌに対して、９０度を超え１８０度未満の交差角θで交差する。 A plurality of rectifying holes 11Cj are formed to extend obliquely toward the valve seat 11k from the lower end of the cylindrical hole 11Ci formed inside the inner cylindrical portion 11Ce. The rectifying hole 11Cj faces the inner wall of the first pipe T1 assembled to the valve seat member 11C. That is, the center axis X of the rectifying hole 11Cj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Cj intersects the axis L at an intersection angle θ of more than 90 degrees and less than 180 degrees.

本実施形態においても、整流孔１１Ｃｊの長さ（孔内壁の軸線方向最短長）は、整流孔１１Ｃｊの内径より長く、また円筒孔１１Ｃｉの内周半径より長い。また、４本の整流孔１１Ｃｊの流路断面積の合計は、最大開弁時のオリフィス断面積よりも大きい。また、円筒孔１１Ｃｉの流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１Ｃｊの流路断面積の合計は、円筒孔１１Ｃｉの流路断面積より大きいと好ましい。 Also in this embodiment, the length of the rectifying hole 11Cj (the shortest length in the axial direction of the inner wall of the hole) is longer than the inner diameter of the rectifying hole 11Cj and longer than the inner circumferential radius of the cylindrical hole 11Ci. Further, the total flow path cross-sectional area of the four rectifying holes 11Cj is larger than the orifice cross-sectional area at the maximum valve opening. Further, the flow passage cross-sectional area of the cylindrical hole 11Ci is greater than or equal to the orifice cross-sectional area when the valve is opened to the maximum. The total cross-sectional area of the flow passages of the rectifying holes 11Cj is preferably larger than the cross-sectional area of the flow passages of the cylindrical holes 11Ci.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｃｉに沿って流れて底壁１１Ｃｈに至る。ここで、冷媒は流れの方向を鋭角に曲げられ、整流孔１１Ｃｊを通過して弁座部材１１Ｃの外部へと流出する。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Ci, which is the orifice portion, and reaches the bottom wall 11Ch. Here, the flow direction of the refrigerant is bent at an acute angle, passes through the rectifying hole 11Cj, and flows out of the valve seat member 11C.

第一の配管Ｔ１と縮径部１１Ｃｅ２との間には間隙があるため、縮径部１１Ｃｅ２から流れ出る冷媒は、第一の配管Ｔ１の内壁に当たり、さらに第一の配管Ｔ１と縮径部１１Ｃｅ２との間隙を通過して下方に向かう。このとき、第一の配管Ｔ１と縮径部１１Ｃｅ２との間から流れ出る冷媒の流速は、最大開弁時のオリフィス断面積を通過する冷媒の流速よりも遅くなる。 Since there is a gap between the first pipe T1 and the reduced diameter part 11Ce2, the refrigerant flowing out from the reduced diameter part 11Ce2 hits the inner wall of the first pipe T1, and further between the first pipe T1 and the reduced diameter part 11Ce2. Pass through the gap and head downwards. At this time, the flow rate of the refrigerant flowing out from between the first pipe T1 and the reduced diameter portion 11Ce2 is slower than the flow rate of the refrigerant passing through the orifice cross-sectional area when the valve is opened to the maximum.

［第５の実施形態］
図８は、第５の実施形態に係る電動弁に用いることができる弁座部材１１Ｄの縦断面図である。弁座部材１１Ｄ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Fifth embodiment]
FIG. 8 is a longitudinal cross-sectional view of a valve seat member 11D that can be used in the electric valve according to the fifth embodiment. The electric valve configuration other than the valve seat member 11D is the same as that of the first embodiment, so a repeated explanation will be omitted.

本実施形態の弁座部材１１Ｄは、内側円筒部１１Ｄｅおよび整流孔１１Ｄｊの形状が主として異なる。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11D of this embodiment differs mainly in the shapes of the inner cylindrical portion 11De and the rectifying hole 11Dj. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

隔壁部１１ｄから下方に向かって延在する内側円筒部１１Ｄｅは、隔壁部１１ｄ側の拡径部１１Ｄｅ１と、拡径部１１Ｄｅ１より外径が小さい先端側の縮径部１１Ｄｅ２とからなる。第一の配管Ｔ１（図１）は、拡径部１１Ｄｅ１にのみ嵌合する。 The inner cylindrical portion 11De extending downward from the partition wall portion 11d is composed of an enlarged diameter portion 11De1 on the partition wall portion 11d side and a reduced diameter portion 11De2 on the tip side having a smaller outer diameter than the enlarged diameter portion 11De1. The first pipe T1 (FIG. 1) fits only into the enlarged diameter portion 11De1.

内側円筒部１１Ｄｅの内部に形成された円筒孔１１Ｄｉの下端から、整流孔１１Ｄｊが軸線Ｌに直交する方向に延在するように形成されており、すなわちオリフィス部である円筒孔１１Ｄｉに対して整流孔１１Ｄｊは直角に交差する。整流孔１１Ｄｊは、弁座部材１１Ｄに組付けた第一の配管Ｔ１の内壁を向いている。換言すれば、整流孔１１Ｄｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｄｊの中心軸線Ｘは、軸線Ｌに対して、９０度の交差角θで交差する。 A rectifying hole 11Dj is formed to extend in a direction perpendicular to the axis L from the lower end of the cylindrical hole 11Di formed inside the inner cylindrical portion 11De. The holes 11Dj intersect at right angles. The rectifying hole 11Dj faces the inner wall of the first pipe T1 assembled to the valve seat member 11D. In other words, the center axis X of the rectifying hole 11Dj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Dj intersects the axis L at an intersection angle θ of 90 degrees.

本実施形態においても、整流孔１１Ｄｊの長さは、整流孔１１Ｄｊの内径より長く、また円筒孔１１Ｄｉの内周半径より長いと好ましい。また、整流孔１１Ｄｊの流路断面積は、最大開弁時のオリフィス断面積よりも大きい。また、円筒孔１１Ｄｉの最小流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１Ｄｊの流路断面積は、円筒孔１１Ｄｉの流路断面積より大きいと好ましい。 Also in this embodiment, the length of the rectifying hole 11Dj is preferably longer than the inner diameter of the rectifying hole 11Dj and longer than the inner circumferential radius of the cylindrical hole 11Di. Further, the flow passage cross-sectional area of the rectifying hole 11Dj is larger than the orifice cross-sectional area at the time of maximum valve opening. Further, the minimum flow passage cross-sectional area of the cylindrical hole 11Di is greater than or equal to the orifice cross-sectional area when the valve is opened at its maximum. The flow passage cross-sectional area of the rectifying hole 11Dj is preferably larger than the flow passage cross-sectional area of the cylindrical hole 11Di.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｄｉに沿って流れて底壁１１Ｄｈに至る。ここで、冷媒は流れの方向を直角に曲げられ、整流孔１１Ｄｊを通過して弁座部材１１Ｄの外部へと流出する。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Di, which is the orifice portion, and reaches the bottom wall 11Dh. Here, the flow direction of the refrigerant is bent at right angles, passes through the rectifying hole 11Dj, and flows out of the valve seat member 11D.

第一の配管Ｔ１と縮径部１１Ｄｅ２との間には間隙があるため、縮径部１１Ｄｅ２から流れ出る冷媒は、第一の配管Ｔ１の内壁に当たり、さらに第一の配管Ｔ１と縮径部１１Ｄｅ２との間隙を通過して下方に向かう。このとき、第一の配管Ｔ１と縮径部１１Ｄｅ２の間から流れ出る冷媒の流速は、最大開弁時のオリフィス断面積を通過する冷媒の流速よりも遅くなる。 Since there is a gap between the first pipe T1 and the reduced diameter part 11De2, the refrigerant flowing out from the reduced diameter part 11De2 hits the inner wall of the first pipe T1, and further between the first pipe T1 and the reduced diameter part 11De2. Pass through the gap and head downwards. At this time, the flow rate of the refrigerant flowing out from between the first pipe T1 and the reduced diameter portion 11De2 becomes slower than the flow rate of the refrigerant passing through the cross-sectional area of the orifice when the valve is opened to the maximum.

［第６の実施形態］
図９は、第６の実施形態に係る電動弁に用いることができる弁座部材１１Ｅの縦断面図である。弁座部材１１Ｅ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Sixth embodiment]
FIG. 9 is a longitudinal sectional view of a valve seat member 11E that can be used in the electric valve according to the sixth embodiment. The electric valve configuration other than the valve seat member 11E is the same as that in the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ｅは、円筒孔１１Ｅｉの形状が主として異なる。本実施形態においても、整流孔１１Ｅｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｅｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｅｅの下端は、円錐台形部１１Ｅｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11E of this embodiment differs mainly in the shape of the cylindrical hole 11Ei. Also in this embodiment, the center axis X of the rectifying hole 11Ej intersects with the inner wall of the first pipe T1 (see FIG. 1). The center axis X of the rectifying hole 11Ej intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ee includes a truncated conical portion 11Ef. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

円筒孔１１Ｅｉは、弁座１１ｋの下方に配設された第１孔１１Ｅｉ１と、第１孔１１Ｅｉ１より大径の第２孔１１Ｅｉ２と、第２孔１１Ｅｉ２より大径の第３孔１１Ｅｉ３とを有する。第１孔１１Ｅｉ１と第２孔１１Ｅｉ２とは、第１テーパ部１１Ｅｉ４により連結され、第２孔１１Ｅｉ２と第３孔１１Ｅｉ３とは、第２テーパ部１１Ｅｉ５により連結されている。第３孔１１Ｅｉ３（及び第２テーパ部１１Ｅｉ５）の下端に、４本の整流孔１１Ｅｊが連通している。なお、円筒孔１１Ｅｉは、例えばシャンク径が刃先外径より小さいエンドミル工具などを用いて加工形成できる。また、第１孔１１Ｅｉ１の流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１Ｅｊの流路断面積の合計は、第１孔１１Ｅｉ１の流路断面積より大きいと好ましい。 The cylindrical hole 11Ei has a first hole 11Ei1 arranged below the valve seat 11k, a second hole 11Ei2 with a larger diameter than the first hole 11Ei1, and a third hole 11Ei3 with a larger diameter than the second hole 11Ei2. . The first hole 11Ei1 and the second hole 11Ei2 are connected by a first taper portion 11Ei4, and the second hole 11Ei2 and the third hole 11Ei3 are connected by a second taper portion 11Ei5. Four rectifying holes 11Ej communicate with the lower end of the third hole 11Ei3 (and the second tapered portion 11Ei5). Note that the cylindrical hole 11Ei can be formed by processing using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Further, the flow passage cross-sectional area of the first hole 11Ei1 is greater than or equal to the orifice cross-sectional area when the valve is opened to the maximum. It is preferable that the total cross-sectional area of the flow passages of the rectifying holes 11Ej is larger than the cross-sectional area of the flow passages of the first holes 11Ei1.

開弁時にオリフィスを通過した冷媒は、第１孔１１Ｅｉ１と、第１テーパ部１１Ｅｉ４と、第２孔１１Ｅｉ２と、第２テーパ部１１Ｅｉ５と、第３孔１１Ｅｉ３に沿って流れて底壁１１Ｅｈに至る。このときオリフィスから底壁１１Ｅｈに至るまでに、流路断面積が三段階で拡大する。これにより冷媒圧力を徐々に回復させることができる。 The refrigerant that has passed through the orifice when the valve is opened flows along the first hole 11Ei1, the first tapered portion 11Ei4, the second hole 11Ei2, the second taper portion 11Ei5, and the third hole 11Ei3, and reaches the bottom wall 11Eh. . At this time, the cross-sectional area of the flow path expands in three stages from the orifice to the bottom wall 11Eh. This allows the refrigerant pressure to be gradually restored.

さらに、冷媒は、斜め下方を向いた整流孔１１Ｅｊを通過して弁座部材１１Ｅの外部へと流出して、第一の配管Ｔ１の内壁に当たることで、冷媒の流速を強制的に低減し、乱流が発生する前に冷媒圧力を回復させることができる。 Furthermore, the refrigerant flows out of the valve seat member 11E through the straightening hole 11Ej facing diagonally downward, and hits the inner wall of the first pipe T1, thereby forcibly reducing the flow velocity of the refrigerant. Refrigerant pressure can be restored before turbulence occurs.

［第７の実施形態］
図１０は、第７の実施形態に係る電動弁に用いることができる弁座部材１１Ｆの縦断面図である。弁座部材１１Ｆ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Seventh embodiment]
FIG. 10 is a longitudinal sectional view of a valve seat member 11F that can be used in the electric valve according to the seventh embodiment. The electrically operated valve configuration other than the valve seat member 11F is the same as that in the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ｆは、円筒孔１１Ｆｉの形状が主として異なる。本実施形態においても、整流孔１１Ｆｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｆｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｆｅの下端は、円錐台形部１１Ｆｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11F of this embodiment differs mainly in the shape of the cylindrical hole 11Fi. Also in this embodiment, the central axis X of the rectifying hole 11Fj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Fj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Fe includes a truncated conical portion 11Ff. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

円筒孔１１Ｆｉは、弁座１１ｋの下方に配設された第１孔１１Ｆｉ１と、第１孔１１Ｆｉ１より大径の第２孔１１Ｆｉ２とを有する。第１孔１１Ｆｉ１と第２孔１１Ｆｉ２とは、テーパ部１１Ｆｉ３により連結される。第２孔１１Ｆｉ２の下端に、４本の整流孔１１Ｆｊが連通している。なお、円筒孔１１Ｆｉは、例えばシャンク径が刃先外径より小さいエンドミル工具などを用いて加工形成できる。また、第１孔１１Ｆｉ１の流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１Ｆｊの流路断面積の合計は、第１孔１１Ｆｉ１の流路断面積より大きいと好ましい。 The cylindrical hole 11Fi has a first hole 11Fi1 disposed below the valve seat 11k and a second hole 11Fi2 having a larger diameter than the first hole 11Fi1. The first hole 11Fi1 and the second hole 11Fi2 are connected by a tapered portion 11Fi3. Four rectifying holes 11Fj communicate with the lower end of the second hole 11Fi2. The cylindrical hole 11Fi can be formed using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Further, the flow passage cross-sectional area of the first hole 11Fi1 is greater than or equal to the orifice cross-sectional area at the maximum valve opening. It is preferable that the total cross-sectional area of the flow passages of the rectifying holes 11Fj is larger than the cross-sectional area of the flow passages of the first holes 11Fi1.

開弁時にオリフィスを通過した冷媒は、第１孔１１Ｆｉ１と、テーパ部１１Ｆｉ３と、第２孔１１Ｆｉ２に沿って流れて底壁１１Ｆｈに至る。このときオリフィスから底壁１１Ｆｈに至るまでに、流路断面積が二段階で拡大する。これにより冷媒圧力を徐々に回復させることができる。 The refrigerant that has passed through the orifice when the valve is opened flows along the first hole 11Fi1, the tapered portion 11Fi3, and the second hole 11Fi2, and reaches the bottom wall 11Fh. At this time, the cross-sectional area of the flow path expands in two stages from the orifice to the bottom wall 11Fh. This allows the refrigerant pressure to be gradually restored.

さらに、冷媒は、斜め下方を向いた整流孔１１Ｆｊを通過して弁座部材１１Ｆの外部へと流出して、第一の配管Ｔ１の内壁に当たることで、冷媒の流速を強制的に低減し、乱流が発生する前に冷媒圧力を回復させることができる。 Further, the refrigerant flows out of the valve seat member 11F through the straightening hole 11Fj facing diagonally downward, and hits the inner wall of the first pipe T1, thereby forcibly reducing the flow velocity of the refrigerant, Refrigerant pressure can be restored before turbulence occurs.

［第８の実施形態］
図１１は、第８の実施形態に係る電動弁に用いることができる弁座部材１１Ｇの縦断面図である。弁座部材１１Ｇ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Eighth embodiment]
FIG. 11 is a longitudinal cross-sectional view of a valve seat member 11G that can be used in the electric valve according to the eighth embodiment. The electric valve configuration other than the valve seat member 11G is the same as that in the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ｇは、円筒孔１１Ｇｉにつながる中央孔１１Ｇｎを底壁１１Ｇｈに形成した点が主として異なる。本実施形態においても、整流孔１１Ｇｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｇｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｇｅの下端は、円錐台形部１１Ｇｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11G of this embodiment differs mainly in that a central hole 11Gn connected to the cylindrical hole 11Gi is formed in the bottom wall 11Gh. Also in this embodiment, the center axis X of the rectifying hole 11Gj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Gj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ge includes a truncated conical portion 11Gf. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

中央孔１１Ｇｎは、円筒孔１１Ｇｉと同軸であり、円筒孔１１Ｇｉ及び整流孔１１Ｇｊの内径よりも小さい内径を有する。円筒孔１１Ｇｉと整流孔１１Ｇｊとは、端部同士が接していてもよいし、互いに離間していてもよい。 The central hole 11Gn is coaxial with the cylindrical hole 11Gi, and has an inner diameter smaller than the inner diameters of the cylindrical hole 11Gi and the rectifying hole 11Gj. The ends of the cylindrical hole 11Gi and the rectifying hole 11Gj may be in contact with each other, or may be spaced apart from each other.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｇｉに沿って流れて底壁１１Ｇｈに至る。ここで、冷媒の一部は、整流孔１１Ｇｊを通過して弁座部材１１Ｇの外部へと流出し、第一の配管Ｔ１に衝突するが、このとき渦が形成される場合がある。一方、底壁１１Ｇｈに到達した冷媒の残りは、ストレートに中央孔１１Ｇｎを通過して、弁座部材１１Ｇの外部へと流出するが、それにより第一の配管Ｔ１の内壁に形成された渦を消失させる効果がある。これにより速やかな冷媒の圧力回復を図ることができる。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Gi, which is the orifice portion, and reaches the bottom wall 11Gh. Here, a part of the refrigerant flows out of the valve seat member 11G through the rectifying hole 11Gj and collides with the first pipe T1, but a vortex may be formed at this time. On the other hand, the rest of the refrigerant that has reached the bottom wall 11Gh passes straight through the central hole 11Gn and flows out of the valve seat member 11G, but this eliminates the vortex formed on the inner wall of the first pipe T1. It has the effect of disappearing. This makes it possible to quickly recover the pressure of the refrigerant.

［第９の実施形態］
図１２は、第９の実施形態に係る電動弁に用いることができる弁座部材１１Ｈの縦断面図である。弁座部材１１Ｈ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Ninth embodiment]
FIG. 12 is a longitudinal cross-sectional view of a valve seat member 11H that can be used in the electric valve according to the ninth embodiment. The electrically operated valve configuration other than the valve seat member 11H is the same as that of the first embodiment, and therefore, redundant explanation will be omitted.

図１２を参照して、整流孔１１Ｈｊの長さは、軸線Ｌ及び中心軸線Ｘを通る面で電動弁１を切断した断面(ここでは図１２)において、整流孔１１Ｈｊの内壁が中心軸線Ｘを挟んだ一対の線分として表され、該内壁の線分の一端同士を結ぶ直線（図１２の点線）ＰＬ１と、他端同士を結ぶ直線（図１２の点線）ＰＬ２に、整流孔１１Ｈｊの中心軸線Ｘが点ＰＴ１、ＰＴ２で交差したときに、その点ＰＴ１、ＰＴ２間の距離である。本実施形態においても、整流孔１１Ｈｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｈｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｈｅの下端は、円錐台形部１１Ｈｆを備える。 Referring to FIG. 12, the length of the rectifying hole 11Hj is such that the inner wall of the rectifying hole 11Hj crosses the central axis The center of the rectifying hole 11Hj is expressed as a pair of sandwiched line segments, and the straight line PL1 connecting one end of the line segment of the inner wall (dotted line in FIG. 12) and the straight line PL2 connecting the other ends (dotted line in FIG. 12) When the axis X intersects at the points PT1 and PT2, it is the distance between the points PT1 and PT2. Also in this embodiment, the center axis X of the rectifying hole 11Hj intersects with the inner wall of the first pipe T1 (see FIG. 1). The center axis X of the rectifying hole 11Hj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11He includes a truncated conical portion 11Hf.

本実施形態の弁座部材１１Ｈは、円筒孔１１Ｈｉの形状、および円筒孔１１Ｈｉにつながる中央孔１１Ｈｎを底壁１１Ｈｈに形成した点が主として異なる。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11H of this embodiment differs mainly in the shape of the cylindrical hole 11Hi and that a central hole 11Hn connected to the cylindrical hole 11Hi is formed in the bottom wall 11Hh. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

円筒孔１１Ｈｉは、弁座１１ｋの下方に配設された第１孔１１Ｈｉ１と、第１孔１１Ｈｉ１より大径の第２孔１１Ｈｉ２とを有する。第１孔１１Ｈｉ１と第２孔１１Ｈｉ２とは、テーパ部１１Ｈｉ３により連結される。第２孔１１Ｈｉ２の下端に、４本の整流孔１１Ｈｊが連通している。なお、円筒孔１１Ｈｉは、例えばシャンク径が刃先外径より小さいエンドミル工具などを用いて加工形成できる。また、第１孔１１Ｈｉ１の流路断面積は、最大開弁時のオリフィス断面積以上である。整流孔１１Ｈｊの流路断面積の合計は、第１孔１１Ｈｉ１の流路断面積より大きいと好ましい。 The cylindrical hole 11Hi has a first hole 11Hi1 disposed below the valve seat 11k and a second hole 11Hi2 having a larger diameter than the first hole 11Hi1. The first hole 11Hi1 and the second hole 11Hi2 are connected by a tapered portion 11Hi3. Four rectifying holes 11Hj communicate with the lower end of the second hole 11Hi2. The cylindrical hole 11Hi can be formed using, for example, an end mill tool whose shank diameter is smaller than the outer diameter of the cutting edge. Further, the flow passage cross-sectional area of the first hole 11Hi1 is greater than or equal to the orifice cross-sectional area when the valve is opened to the maximum. It is preferable that the total cross-sectional area of the flow passages of the rectifying holes 11Hj is larger than the cross-sectional area of the flow passages of the first holes 11Hi1.

中央孔１１Ｈｎは、円筒孔１１Ｈｉと同軸であり、円筒孔１１Ｈｉ及び整流孔１１Ｈｊの内径よりも小さい内径を有する。 The central hole 11Hn is coaxial with the cylindrical hole 11Hi, and has an inner diameter smaller than the inner diameters of the cylindrical hole 11Hi and the rectifying hole 11Hj.

開弁時にオリフィスを通過した冷媒は、第１孔１１Ｈｉ１と、テーパ部１１Ｈｉ３と、第２孔１１Ｈｉ２に沿って流れて底壁１１Ｈｈに至る。このときオリフィスから底壁１１Ｈｈに至るまでに、流路断面積が二段階で拡大する。これにより冷媒圧力を徐々に回復させることができる。 The refrigerant that has passed through the orifice when the valve is opened flows along the first hole 11Hi1, the tapered portion 11Hi3, and the second hole 11Hi2, and reaches the bottom wall 11Hh. At this time, the cross-sectional area of the flow path expands in two stages from the orifice to the bottom wall 11Hh. This allows the refrigerant pressure to be gradually restored.

底壁１１Ｈｈに到達した冷媒の一部は、整流孔１１Ｈｊを通過して弁座部材１１Ｈの外部へと流出し、第一の配管Ｔ１に衝突するが、このとき渦が形成される場合がある。一方、底壁１１Ｈｈに到達した冷媒の残りは、ストレートに中央孔１１Ｈｎを通過して、弁座部材１１Ｈの外部へと流出するが、それにより第一の配管Ｔ１の内壁に形成された渦を消失させる効果がある。このため、速やかな冷媒の圧力回復を図ることができる。 A part of the refrigerant that has reached the bottom wall 11Hh passes through the rectifying hole 11Hj, flows out of the valve seat member 11H, and collides with the first pipe T1, but a vortex may be formed at this time. . On the other hand, the rest of the refrigerant that has reached the bottom wall 11Hh passes straight through the central hole 11Hn and flows out of the valve seat member 11H, but this eliminates the vortex formed on the inner wall of the first pipe T1. It has the effect of disappearing. Therefore, the pressure of the refrigerant can be quickly recovered.

［第１０の実施形態］
図１３は、第１０の実施形態に係る電動弁に用いることができる弁座部材１１Ｉの縦断面図である。弁座部材１１Ｉ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Tenth embodiment]
FIG. 13 is a longitudinal sectional view of a valve seat member 11I that can be used in the electric valve according to the tenth embodiment. The electric valve configuration other than the valve seat member 11I is the same as that in the first embodiment, and therefore, repeated explanation will be omitted.

本実施形態の弁座部材１１Ｉは、円筒孔１１Ｉｉと整流孔１１Ｉｊとの位置関係が、主として異なる。本実施形態においても、整流孔１１Ｉｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｉｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｉｅの下端は、円錐台形部１１Ｉｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11I of this embodiment differs mainly in the positional relationship between the cylindrical hole 11Ii and the rectifying hole 11Ij. Also in this embodiment, the center axis X of the rectifying hole 11Ij intersects with the inner wall of the first pipe T1 (see FIG. 1). The center axis X of the rectifying hole 11Ij intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ie includes a truncated conical portion 11If. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

本実施形態においては、円筒孔１１Ｉｉの下端と上端との間に整流孔１１Ｉｊを連結している。これにより、円筒孔１１Ｉｉの下端には、整流孔１１Ｉｊとの連結部まで、冷媒の滞留部１１Ｉｐが底壁１１Ｉｈに形成されることとなる。 In this embodiment, the rectifying hole 11Ij is connected between the lower end and the upper end of the cylindrical hole 11Ii. As a result, a refrigerant retention portion 11Ip is formed in the bottom wall 11Ih at the lower end of the cylindrical hole 11Ii up to the connecting portion with the rectification hole 11Ij.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｉｉに沿って流れて底壁１１Ｉｈの滞留部１１Ｉｐに至る。ここで、冷媒の流れはＵターンして、整流孔１１Ｉｊを通過して弁座部材１１Ｉの外部へと流出するため、その際に冷媒の圧力回復がなされ、気泡を減少させることができる。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Ii, which is the orifice portion, and reaches the retention portion 11Ip of the bottom wall 11Ih. Here, the flow of the refrigerant makes a U-turn, passes through the rectifying hole 11Ij, and flows out of the valve seat member 11I, so that the pressure of the refrigerant is recovered at this time, and bubbles can be reduced.

［第１１の実施形態］
図１４は、第１１の実施形態に係る電動弁に用いることができる弁座部材１１Ｋの縦断面図である。弁座部材１１Ｋ以外の電動弁構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Eleventh embodiment]
FIG. 14 is a longitudinal cross-sectional view of a valve seat member 11K that can be used in the electric valve according to the eleventh embodiment. The electrically operated valve configuration other than the valve seat member 11K is the same as that of the first embodiment, so a redundant explanation will be omitted.

本実施形態の弁座部材１１Ｋは、内側円筒部１１Ｋｅの構成が主として異なる。本実施形態においても、整流孔１１Ｋｊの中心軸線Ｘは第一の配管Ｔ１（図１参照）の内壁と交差する。整流孔１１Ｋｊの中心軸線Ｘは、軸線Ｌに対して、０度を超え９０度未満の交差角θで交差する。内側円筒部１１Ｋｅの下端は、円錐台形部１１Ｋｆを備える。第１の実施形態と共通する構成については、同じ符号を付して重複説明を省略する。 The valve seat member 11K of this embodiment differs mainly in the configuration of the inner cylindrical portion 11Ke. Also in this embodiment, the center axis X of the rectifying hole 11Kj intersects with the inner wall of the first pipe T1 (see FIG. 1). The central axis X of the rectifying hole 11Kj intersects the axis L at an intersection angle θ of more than 0 degrees and less than 90 degrees. The lower end of the inner cylindrical portion 11Ke includes a truncated conical portion 11Kf. Components that are common to those in the first embodiment are given the same reference numerals and redundant explanation will be omitted.

隔壁部１１ｄから下方に向かって延在する内側円筒部１１Ｋｅは、隔壁部１１ｄ側の拡径部１１Ｋｅ１と、拡径部１１Ｋｅ１より外径が小さい先端側の縮径部１１Ｋｅ２とからなる。縮径部１１Ｋｅ２の下端には、円錐台形部１１Ｋｆが形成されている。第一の配管Ｔ１（図１）は、拡径部１１Ｋｅ１にのみ嵌合する。 The inner cylindrical portion 11Ke extending downward from the partition wall portion 11d includes an enlarged diameter portion 11Ke1 on the partition wall portion 11d side, and a reduced diameter portion 11Ke2 on the tip side having a smaller outer diameter than the enlarged diameter portion 11Ke1. A truncated conical portion 11Kf is formed at the lower end of the reduced diameter portion 11Ke2. The first pipe T1 (FIG. 1) fits only into the enlarged diameter portion 11Ke1.

内側円筒部１１Ｋｅの内部に形成された円筒孔１１Ｋｉの下端から、複数の整流孔１１Ｋｊが弁座１１ｋ側に下方に向かって斜めに延在するように形成されている。また、各整流孔１１Ｋｊの中間位置から、隔壁部１１ｄ側に向かって斜めに延在する連通開口１１Ｋｎを形成している。連通開口１１Ｋｎの内径は、整流孔Ｋｊの内径の１／４以下であると好ましい。 A plurality of rectifying holes 11Kj are formed to extend diagonally downward toward the valve seat 11k from the lower end of the cylindrical hole 11Ki formed inside the inner cylindrical portion 11Ke. Further, a communication opening 11Kn is formed that extends obliquely from the intermediate position of each rectifying hole 11Kj toward the partition wall portion 11d. The inner diameter of the communication opening 11Kn is preferably 1/4 or less of the inner diameter of the rectifying hole Kj.

開弁時にオリフィスを通過した冷媒は、オリフィス部である円筒孔１１Ｋｉに沿って流れて底壁１１Ｋｈに至る。ここから、冷媒は整流孔１１Ｋｊを通過して弁座部材１１Ｋの外部へと流出するが、その際に第一の配管Ｔ１の内壁に衝突して渦を形成することがある。かかる渦が冷媒の圧力回復を妨げるおそれがある。 The refrigerant that has passed through the orifice when the valve is opened flows along the cylindrical hole 11Ki, which is the orifice portion, and reaches the bottom wall 11Kh. From here, the refrigerant passes through the rectifying hole 11Kj and flows out of the valve seat member 11K, but at that time, it may collide with the inner wall of the first pipe T1 and form a vortex. Such a vortex may hinder pressure recovery of the refrigerant.

これに対し、本実施形態によれば、冷媒が連通開口１１Ｋｎの下端を通過する際に連通開口１１Ｋｎの内部に負圧が発生するため、連通開口１１Ｋｎの上端から冷媒を吸い込む。これにより、第一の配管Ｔ１の内壁に衝突して形成される渦を速やかに消失させることができる。 On the other hand, according to the present embodiment, when the refrigerant passes through the lower end of the communication opening 11Kn, a negative pressure is generated inside the communication opening 11Kn, so that the refrigerant is sucked in from the upper end of the communication opening 11Kn. Thereby, the vortex formed by colliding with the inner wall of the first pipe T1 can be quickly eliminated.

［変形例］
図１５は、本実施形態の変形例に係る電動弁に用いることができる弁座部材１１と多孔質フィルタＦＴとを組み合わせた構成を示す図であり、左半部が縦断面図であって、右半部が側面図である。多孔質フィルタＦＴ以外の構成については、第１の実施形態と同様であるため、重複説明を省略する。 [Modified example]
FIG. 15 is a diagram showing a configuration in which a valve seat member 11 and a porous filter FT are combined, which can be used in an electric valve according to a modification of the present embodiment, and the left half is a longitudinal cross-sectional view, The right half is a side view. The configurations other than the porous filter FT are the same as those in the first embodiment, so redundant explanation will be omitted.

弁座部材１１の内側円筒部１１ｅの周囲にて、点線で示す位置から円錐台形部１１ｆの下方まで覆うようにして、金属製または樹脂製の多孔質フィルタＦＴが配設されている。多孔質フィルタＦＴは、例えば発泡金属、網状の素材またはパンチングメタルなどから円筒状に形成され、整流孔１１ｊの外方端を覆うようにして内側円筒部１１ｅの外周に巻き付けられている。 A porous filter FT made of metal or resin is disposed around the inner cylindrical portion 11e of the valve seat member 11 so as to cover from the position shown by the dotted line to below the truncated conical portion 11f. The porous filter FT is formed into a cylindrical shape from, for example, foamed metal, a net-like material, or punched metal, and is wound around the outer periphery of the inner cylindrical portion 11e so as to cover the outer end of the rectifying hole 11j.

整流孔１１ｊから流れ出た冷媒は、多孔質フィルタＦＴを通過することで、気泡が細分化されるため、さらに騒音の低減に効果がある。多孔質フィルタＦＴと組み合わせる弁座部材は、第１の実施形態に限られず、それ以外の実施形態と組み合わせてもよい。 The refrigerant flowing out from the rectifying hole 11j passes through the porous filter FT, and the air bubbles are divided into smaller particles, which is further effective in reducing noise. The valve seat member to be combined with the porous filter FT is not limited to the first embodiment, and may be combined with other embodiments.

以上の実施形態において、交差角θは、９０度未満である場合、１５度以上、７５度以下であると好ましく、より好ましくは３０度以上、６０度以下であり、また９０度を超えている場合、１０５度以上、１６５度以下であると好ましく、より好ましくは１２０度以上、１５０度以下である。 In the above embodiments, when the intersection angle θ is less than 90 degrees, it is preferably 15 degrees or more and 75 degrees or less, more preferably 30 degrees or more and 60 degrees or less, and more than 90 degrees. In this case, the temperature is preferably 105 degrees or more and 165 degrees or less, more preferably 120 degrees or more and 150 degrees or less.

１ 電動弁
１０ 弁本体
１１～１１Ｋ 弁座部材
１１ｅ 弁座
１５ ガイドステム
２１ 弁軸
２３ 弁ホルダ
２４ コイルバネ
２５ ニードル弁
２６ ばね受け部材
２７ 環状部材
２９ 弁室
３０ ロータ
３５ 閉弁方向用可動ストッパ
３６ 開弁方向用可動ストッパ
５５ 閉弁方向用固定ストッパ
５６ 開弁方向用固定ストッパ
ＦＴ 多孔質フィルタ

 1 Motor operated valve 10 Valve body 11 to 11K Valve seat member 11e Valve seat 15 Guide stem 21 Valve shaft 23 Valve holder 24 Coil spring 25 Needle valve 26 Spring receiving member 27 Annular member 29 Valve chamber 30 Rotor 35 Movable stopper 36 for valve closing direction Open Movable stopper for valve direction 55 Fixed stopper for valve closing direction 56 Fixed stopper for valve opening direction FT Porous filter

Claims (15)

弁室を備えた弁本体と、
前記弁本体に取り付けられ、弁座を備えた弁座部材と、
前記弁室内に配置され、前記弁座に接近又は離間する方向に昇降可能な弁体と、を有し、
前記弁座部材は、配管に接続可能であり、前記弁座に隣接するオリフィス部と、前記オリフィス部に繋がる整流孔と、前記オリフィス部の端部に形成された底壁とを備えた電動弁であって、
前記電動弁の軸線と前記整流孔の中心軸線が通る面で前記電動弁を切断したときに、当該切断面において、前記弁座よりも前記底壁側において、前記電動弁の軸線と前記整流孔の中心軸線が交わり、
前記整流孔の中心軸線は、前記配管の内壁に交わる、
ことを特徴とする電動弁。 a valve body having a valve chamber;
a valve seat member attached to the valve body and including a valve seat;
a valve body disposed within the valve chamber and movable up and down in a direction toward or away from the valve seat;
The valve seat member is connectable to piping, and includes an orifice portion adjacent to the valve seat, a rectifying hole connected to the orifice portion, and a bottom wall formed at an end of the orifice portion. And,
When the motor-operated valve is cut along a plane where the axis of the motor-operated valve and the center axis of the rectifier hole pass, the axis of the motor-operated valve and the rectifier hole are located closer to the bottom wall than the valve seat in the cut plane. The central axes of intersect,
The center axis of the rectifying hole intersects with the inner wall of the piping,
An electric valve characterized by: 前記電動弁の軸線と前記整流孔の中心軸線が通る前記断面において、前記オリフィス部内で前記電動弁の軸線と前記整流孔の中心軸線が交わる、In the cross section through which the axis of the electric valve and the central axis of the rectifying hole pass, the axis of the electric valve and the central axis of the rectifying hole intersect within the orifice portion.
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, characterized in that: 前記整流孔は、前記オリフィス部から複数本に分岐する、
ことを特徴とする請求項１または２に記載の電動弁。 The rectifying hole branches into a plurality of holes from the orifice portion.
The electric valve according to claim 1 or 2 , characterized in that: 前記整流孔の流路断面積の合計は、最大開弁時におけるオリフィス断面積よりも大きい、
ことを特徴とする請求項１～３のいずれかに記載の電動弁。 The total cross-sectional area of the flow path of the rectifying hole is larger than the cross-sectional area of the orifice at maximum valve opening.
The electric valve according to any one of claims 1 to 3, characterized in that: 前記オリフィス部の流路断面積は、最大開弁時におけるオリフィス断面積以上である、
ことを特徴とする請求項４に記載の電動弁。 The flow passage cross-sectional area of the orifice portion is greater than or equal to the orifice cross-sectional area at the time of maximum valve opening.
The electric valve according to claim 4 , characterized in that: 前記整流孔の流路断面積の合計は、前記オリフィス部の流路断面積より大きい、
ことを特徴とする請求項４または５に記載の電動弁。 The total cross-sectional area of the flow passages of the rectifying holes is larger than the cross-sectional area of the flow passages of the orifice portion.
The electric valve according to claim 4 or 5, characterized in that: 前記整流孔の長さは、前記整流孔の内径より長く、且つ前記オリフィス部の内周半径より長い、
ことを特徴とする請求項１～６のいずれか一項に記載の電動弁。 The length of the rectifying hole is longer than the inner diameter of the rectifying hole and longer than the inner circumferential radius of the orifice portion.
The electric valve according to any one of claims 1 to 6 , characterized in that: 前記弁座部材は、前記オリフィス部を内部に形成するとともに前記配管内に配置される円筒部を備えている、
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 seat member includes a cylindrical portion that forms the orifice portion therein and is disposed within the piping.
The electric valve according to any one of claims 1 to 7 , characterized in that: 前記円筒部の端部に円錐台形部が形成されており、前記整流孔の外方端は、前記円錐台形部の外周面に位置する、
ことを特徴とする請求項８に記載の電動弁。 A truncated conical part is formed at an end of the cylindrical part, and an outer end of the rectifying hole is located on an outer peripheral surface of the truncated conical part.
The electric valve according to claim 8 , characterized in that: 前記オリフィス部の前記配管側の内方端にテーパ状部が形成されている、
ことを特徴とする請求項８または９に記載の電動弁。 a tapered portion is formed at an inner end of the orifice portion on the piping side ;
The electric valve according to claim 8 or 9, characterized in that: 前記整流孔から前記弁座部材の外部へと延在する連通開口を有し、前記連通開口の内径は前記整流孔の内径より小さい、
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。 It has a communication opening extending from the rectification hole to the outside of the valve seat member, and the inner diameter of the communication opening is smaller than the inner diameter of the rectification hole.
The electric valve according to any one of claims 8 to 10 , characterized in that: 前記整流孔は、前記オリフィス部に対して直角に交差する、
ことを特徴とする請求項８に記載の電動弁。 The rectifying hole intersects the orifice part at right angles,
The electric valve according to claim 8 , characterized in that: 前記オリフィス部は、前記弁座側から順に、第１孔と、前記第１孔より大径の第２孔とを有する、
ことを特徴とする請求項１～１２のいずれか一項に記載の電動弁。 The orifice portion has, in order from the valve seat side, a first hole and a second hole having a larger diameter than the first hole.
The electric valve according to any one of claims 1 to 12, characterized in that: 前記オリフィス部は、前記弁座側から順に、第１孔と、前記第１孔より大径の第２孔と、前記第２孔より大径の第３孔とを有する、
ことを特徴とする請求項１～１２のいずれか一項に記載の電動弁。 The orifice portion has, in order from the valve seat side, a first hole, a second hole with a larger diameter than the first hole, and a third hole with a larger diameter than the second hole.
The electric valve according to any one of claims 1 to 12, characterized in that: 前記オリフィス部に繋がり、前記オリフィス部と同方向に延在する中央孔を有し、前記中央孔の内径は、前記整流孔の内径より小さい、
ことを特徴とする請求項１～１４のいずれか一項に記載の電動弁。 It has a central hole connected to the orifice portion and extending in the same direction as the orifice portion, and the inner diameter of the central hole is smaller than the inner diameter of the rectifying hole.
The electric valve according to any one of claims 1 to 14, characterized in that:
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JP2005069645A (en) 2003-08-27 2005-03-17 Daikin Ind Ltd Multi-stage electric expansion valve and refrigerator
JP2006266667A (en) 2005-02-28 2006-10-05 Daikin Ind Ltd Expansion valve and freezing apparatus
JP2008232290A (en) 2007-03-20 2008-10-02 Saginomiya Seisakusho Inc Needle valve, and refrigerating cycle device having the same
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