JP2020165539A

JP2020165539A - Motor-operated valve and refrigeration cycle system

Info

Publication number: JP2020165539A
Application number: JP2020109630A
Authority: JP
Inventors: 大樹中川; Daiki Nakagawa
Original assignee: Saginomiya Seisakusho Inc
Current assignee: Saginomiya Seisakusho Inc
Priority date: 2020-06-25
Filing date: 2020-06-25
Publication date: 2020-10-08
Anticipated expiration: 2037-01-31
Also published as: JP7157105B2

Abstract

To properly weld and fix a fixing member 23 of a magnetic rotor 2 and a rotor shaft 1 in a motor-operated valve 100.SOLUTION: A fixing member 23 is disposed on the center of a magnetic rotor 2. The fixing member 23 is composed of a columnar fixing member main body portion 231 and a cylindrical portion 232. The cylindrical portion 232 has a diameter smaller than that of the fixing member main body portion 231. A volume of the cylindrical portion 232 is smaller than a volume of the fixing member main body portion 231. An insertion hole 23a for inserting a rotor shaft 1 (first shaft portion 11) is formed on the center of the fixing member 23. On an opening end portion at a cylindrical portion 232 side, of the insertion hole 23a of the fixing member 23, the fixing member 23 and the rotor shaft 1 are partially welded at two spots (a part) around an axis L. Two melted solidified portions 4, 4 by welding of proper depth are formed.SELECTED DRAWING: Figure 2

Description

本発明は、冷凍サイクルシステムなどに使用する電動弁及び冷凍サイクルシステムに関する。 The present invention relates to an electric valve and a refrigeration cycle system used for a refrigeration cycle system or the like.

従来、この種の電動弁として、ステッピングモータのマグネットロータの回転によりねじ送り機構を介してロータ軸を直動させ、このロータ軸に連結された弁部材で弁ポートを開閉するものがある。このような電動弁は例えば特開２０１６−１５６４４７号公報（特許文献１）及び特開２０１５−９０２０４号公報（特許文献２）に開示されている。 Conventionally, as an electric valve of this type, there is one in which a rotor shaft is linearly moved via a screw feed mechanism by rotation of a magnet rotor of a stepping motor, and a valve member connected to the rotor shaft opens and closes a valve port. Such an electric valve is disclosed in, for example, Japanese Patent Application Laid-Open No. 2016-156447 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2015-090204 (Patent Document 2).

特許文献１の従来の電動弁は、マグネットロータと弁軸（ロータ軸）とを固定する構造として、マグネットロータの軸芯部分に設けた連結体（固定部材）に弁軸を挿通し、この連結体と弁軸とを溶接等で固定するようにしている。 The conventional electric valve of Patent Document 1 has a structure for fixing a magnet rotor and a valve shaft (rotor shaft) by inserting a valve shaft through a connecting body (fixing member) provided in a shaft core portion of the magnet rotor and connecting the valve shaft. The body and valve shaft are fixed by welding or the like.

特開２０１６−１５６４４７号公報JP-A-2016-156447 特開２０１５−９０２０４号公報JP-A-2015-90204

上述したように、マグネットロータの軸芯部分に設けた連結体（固定部材）と弁軸（ロータ軸）とを溶接により固定する場合、連結体と弁軸とのそれぞれの熱容量を適切な関係とすることが要求される。例えば、連結体に比べて弁軸の熱容量が小さい場合、過大な溶接熱が弁軸に加わり、弁軸が変形してしまう虞がある。また、弁軸が先に溶融して連結体の溶融が足りずに十分な固定強度が得られず、連結体が弁軸から外れてしまう虞もある。 As described above, when the connecting body (fixing member) provided on the shaft core portion of the magnet rotor and the valve shaft (rotor shaft) are fixed by welding, the heat capacities of the connecting body and the valve shaft are appropriately related to each other. Is required to do. For example, if the heat capacity of the valve shaft is smaller than that of the connected body, excessive welding heat may be applied to the valve shaft and the valve shaft may be deformed. In addition, the valve shaft may melt first and the coupling may not be sufficiently melted to obtain sufficient fixing strength, and the coupling may come off from the valve shaft.

本発明は、モータ部がマグネットロータ及びロータ軸を回転させて、ロータ軸の回転に伴う弁部材の進退移動によって弁ポートを開閉させる電動弁において、マグネットロータの固定部材とロータ軸とを溶接固定し、ロータ軸の変形を防止できるとともに、固定強度を向上させた電動弁を提供することを課題とする。 According to the present invention, in an electric valve in which a motor unit rotates a magnet rotor and a rotor shaft to open and close a valve port by moving the valve member forward and backward with the rotation of the rotor shaft, the fixing member of the magnet rotor and the rotor shaft are welded and fixed. However, it is an object of the present invention to provide an electric valve which can prevent deformation of the rotor shaft and has improved fixing strength.

請求項１の電動弁は、モータ部がマグネットロータ及び金属製のロータ軸を回転させるとともに、前記ロータ軸の回転に伴う弁部材の進退移動によって弁ポートを開閉させる電動弁において、前記マグネットロータは、磁性を有したマグネット本体と、前記マグネット本体の中央に該マグネット本体と一体成形された金属製の固定部材と、を有し、前記固定部材は、前記一体成形にて前記マグネット本体に結合された固定部材本体部と、前記固定部材本体部の外径より小径で、かつ、前記固定部材本体部の体積より体積の小さな円筒状の円筒部と、を有して形成されるとともに、前記固定部材本体部と前記円筒部とを前記ロータ軸の軸線方向に貫通する挿通孔が設けられ、前記ロータ軸が前記挿通孔に挿通されるとともに、前記円筒部と前記ロータ軸とが、前記挿通孔の開口端部の周囲の一部にて溶接により固定されており、前記ロータ軸の軸線回りの回転対称な複数箇所において前記円筒部の前記挿通孔の前記開口端部と前記ロータ軸とが溶接されており、前記溶接による各溶融凝固部が、前記軸線回りの９０°以下の角度範囲に亘って形成されていることを特徴とする。 The electric valve according to claim 1 is an electric valve in which a motor unit rotates a magnet rotor and a metal rotor shaft and opens and closes a valve port by moving the valve member forward and backward with the rotation of the rotor shaft. The magnet body has a magnet body and a metal fixing member integrally molded with the magnet body in the center of the magnet body, and the fixing member is coupled to the magnet body by the integral molding. It is formed by having a fixing member main body portion and a cylindrical cylindrical portion having a diameter smaller than the outer diameter of the fixing member main body portion and a volume smaller than the volume of the fixing member main body portion, and the fixing. An insertion hole is provided through the member main body portion and the cylindrical portion in the axial direction of the rotor shaft, the rotor shaft is inserted into the insertion hole, and the cylindrical portion and the rotor shaft are inserted into the insertion hole. It is fixed by welding at a part around the open end portion of the cylinder, and the open end portion of the insertion hole of the cylindrical portion and the rotor shaft are welded at a plurality of rotationally symmetric points around the axis of the rotor shaft. Each of the melt-solidified portions formed by the welding is formed over an angle range of 90 ° or less around the axis.

請求項２の電動弁は、請求項１に記載の電動弁であって、前記ロータ軸の軸線回りの対向する２箇所において前記円筒部の前記挿通孔の前記開口端部と前記ロータ軸とが溶接されており、前記溶接による各溶融凝固部が、前記軸線回りの４５°〜９０°の範囲内に形成されていることを特徴とする。 The motorized valve according to claim 2 is the motorized valve according to claim 1, wherein the open end portion of the insertion hole of the cylindrical portion and the rotor shaft are formed at two facing positions around the axis of the rotor shaft. It is welded, and each melt-solidified portion formed by the welding is formed within a range of 45 ° to 90 ° around the axis.

請求項３の電動弁は、請求項１又は２に記載の電動弁であって、前記円筒部の前記開口端部の内径角部の形状が、前記糸面取り形状に替えて、前記ロータ軸の外周に接するエッジ形状、または、Ｃ０．１以下の糸面取り形状、であることを特徴とする。 The motorized valve according to claim 3 is the motorized valve according to claim 1 or 2, wherein the shape of the inner diameter corner portion of the opening end portion of the cylindrical portion is replaced with the thread chamfered shape of the rotor shaft. It is characterized by having an edge shape in contact with the outer periphery or a thread chamfering shape having a C of 0.1 or less.

請求項４の電動弁は、請求項１乃至３のいずれか一項に記載の電動弁であって、前記ロータ軸と前記固定部材とが同材質であることを特徴とする。 The motorized valve according to claim 4 is the motorized valve according to any one of claims 1 to 3, wherein the rotor shaft and the fixing member are made of the same material.

請求項５の電動弁は、請求項１乃至４のいずれか一項に記載の電動弁であって、前記固定部材本体部が円柱形状であり、前記固定部材本体部の前記軸線方向の寸法が、前記円筒部の前記軸線方向の寸法より大であることを特徴とする。 The motorized valve according to claim 5 is the motorized valve according to any one of claims 1 to 4, wherein the fixing member main body has a cylindrical shape, and the dimension of the fixing member main body in the axial direction is large. , The cylindrical portion is larger than the axial dimension.

請求項６の電動弁は、請求項１乃至５のいずれか一項に記載の電動弁であって、前記ロータ軸の径をＤ、前記円筒部の径方向の肉厚をｔ、前記円筒部の前記軸線方向の寸法をＨ、としたとき、
ｔ＜Ｄ／２，Ｈ／ｔ≧１
であることを特徴とする。
請求項７の電動弁は、請求項１乃至６のいずれか一項に記載の電動弁であって、前記ロータ軸が、前記弁部材とは反対側に位置する第１軸部と、当該第１軸部における前記弁部材側の端部に隣接して位置し、前記第１軸部の長さ以下の長さで前記第１軸部よりも径が大きい第２軸部とを有し、前記固定部材における前記弁部材側の面が前記第１軸部と前記第２軸部との境界部に位置するように、前記円筒部と前記ロータ軸とが固定されていることを特徴とする。
請求項８の電動弁は、請求項１乃至７のいずれか一項に記載の電動弁であって、前記マグネット本体は、円筒状のマグネット部と、当該マグネット部の内部の前記軸線方向の略中央部に延在し、前記弁部材側に突出したボス部が中央に設けられた円盤部と、を有し、前記固定部材本体部は、前記軸線方向について、前記円盤部における前記弁部材とは反対側の面から前記ボス部における前記弁部材側の端部に至るまで延在するように前記円盤部に結合されていることを特徴とする。 The motor-operated valve according to claim 6 is the motor-operated valve according to any one of claims 1 to 5, wherein the diameter of the rotor shaft is D, the radial wall thickness of the cylindrical portion is t, and the cylindrical portion. When the dimension in the axial direction of is H,
t <D / 2, H / t ≧ 1
It is characterized by being.
The motorized valve according to claim 7 is the motorized valve according to any one of claims 1 to 6, wherein the rotor shaft is located on a side opposite to the valve member, and the first shaft portion and the first shaft portion. It has a second shaft portion that is located adjacent to the end portion of the one shaft portion on the valve member side, has a length equal to or less than the length of the first shaft portion, and has a diameter larger than that of the first shaft portion. The cylindrical portion and the rotor shaft are fixed so that the surface of the fixing member on the valve member side is located at the boundary between the first shaft portion and the second shaft portion. ..
The motorized valve according to claim 8 is the motorized valve according to any one of claims 1 to 7, wherein the magnet main body has a cylindrical magnet portion and an axial direction inside the magnet portion. It has a disk portion extending to the central portion and having a boss portion projecting toward the valve member side provided in the center, and the fixing member main body portion has the valve member in the disk portion in the axial direction. Is coupled to the disk portion so as to extend from the opposite surface to the end portion of the boss portion on the valve member side.

請求項９の冷凍サイクルシステムは、圧縮機と、凝縮器と、膨張弁と、蒸発器と、を含む冷凍サイクルシステムであって、請求項１乃至８のいずれか一項に記載の電動弁が、前記膨張弁として用いられていることを特徴とする。 The refrigeration cycle system according to claim 9 is a refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, and the electric valve according to any one of claims 1 to 8 is used. , It is characterized in that it is used as the expansion valve.

請求項１乃至８の電動弁によれば、固定部材本体部の外径より小径で体積が小さく熱容量の小さな円筒部において、全周溶接ではなく部分的に溶接されているので、溶接時に過大な溶接熱の発生を抑えるように溶接できて、溶接熱によるロータ軸の変形のない範囲で溶け込み量を増やせるため、部分的強度が全体の接合強度の向上として作用し、マグネットロータ（その一部の固定部材）がロータ軸から外れなくなる。また、マグネット本体に結合された固定部材本体部の方が、溶接で接合される円筒部よりも外径が大きいので、マグネットロータの回転時にマグネット本体のトルクを固定部材本体部に無理なく伝達することができ、マグネット本体から固定部材が外れなくなる。 According to the electric valves of claims 1 to 8, the cylindrical portion having a diameter smaller than the outer diameter of the fixing member main body and having a small volume and a small heat capacity is partially welded instead of being welded all around, so that it is excessive at the time of welding. Welding can be performed so as to suppress the generation of welding heat, and the amount of penetration can be increased within the range where the rotor shaft is not deformed by the welding heat. Therefore, the partial strength acts as an improvement in the overall joint strength, and the magnet rotor (a part of it). The fixing member) will not come off from the rotor shaft. In addition, since the fixed member main body connected to the magnet main body has a larger outer diameter than the cylindrical portion joined by welding, the torque of the magnet main body is reasonably transmitted to the fixed member main body when the magnet rotor rotates. It is possible to prevent the fixing member from coming off from the magnet body.

また、請求項３の電動弁によれば、円筒部の上端の内径角部をエッジ形状、または、Ｃ０．１以下の糸面取り形状としたので、固定部材（円筒部）の端部において、ロータ軸との隙間が小さくなり、部品ばらつきや溶接ばらつきに対しても、溶接性が向上し、固定強度がさらに向上する。 Further, according to the electric valve of claim 3, since the inner diameter corner portion of the upper end of the cylindrical portion has an edge shape or a thread chamfer shape of C0.1 or less, the rotor is formed at the end portion of the fixing member (cylindrical portion). The gap between the shaft and the shaft is reduced, and the weldability is improved and the fixing strength is further improved against component variations and welding variations.

請求項４の電動弁によれば、ロータ軸と固定部材とを同材質としたので、熱伝導率が同じであり、ロータ軸と固定部材とが均等に溶融し、さらに固定強度が向上する。例えば、ロータ軸が先に溶融してしまうこともない。 According to the electric valve of claim 4, since the rotor shaft and the fixing member are made of the same material, the thermal conductivity is the same, the rotor shaft and the fixing member are uniformly melted, and the fixing strength is further improved. For example, the rotor shaft does not melt first.

請求項５の電動弁によれば、固定部材本体部が円柱形状であり、固定部材本体部の軸線方向の寸法が、円筒部の軸線方向の寸法より大である。したがって、固定部材本体部の熱容量を十分に確保でき、マグネット本体に対する溶接熱の影響を抑制できる。 According to the electric valve of claim 5, the fixing member main body portion has a cylindrical shape, and the axial dimension of the fixing member main body portion is larger than the axial dimension of the cylindrical portion. Therefore, a sufficient heat capacity of the fixing member main body can be secured, and the influence of welding heat on the magnet main body can be suppressed.

請求項９の冷凍サイクルシステムによれば、請求項１乃至８と同様な効果が得られる。 According to the refrigeration cycle system of claim 9, the same effect as that of claims 1 to 8 can be obtained.

本発明の実施形態の電動弁の縦断面図である。It is a vertical cross-sectional view of the electric valve of embodiment of this invention. 実施形態の電動弁におけるマグネットロータ及びロータ軸の要部拡大断面図である。FIG. 5 is an enlarged cross-sectional view of a main part of a magnet rotor and a rotor shaft in the motorized valve of the embodiment. 図２のＡ−Ａ矢視図である。FIG. 2 is a view taken along the line AA of FIG. 図２のＢ−Ｂ断面図及び一部拡大図である。FIG. 2 is a sectional view taken along line BB and a partially enlarged view of FIG. 実施形態の固定部材の変形例１を示す図である。It is a figure which shows the modification 1 of the fixing member of an embodiment. 実施形態の固定部材の変形例２を示す図である。It is a figure which shows the modification 2 of the fixing member of an embodiment. 実施形態の固定部材の変形例３を示す図である。It is a figure which shows the modification 3 of the fixing member of an embodiment. 実施形態の冷凍サイクルシステムを示す図である。It is a figure which shows the refrigeration cycle system of an embodiment.

次に、本発明の電動弁及び冷凍サイクルシステムの実施形態を図面を参照して説明する。図１は実施形態の電動弁の縦断面図、図２は実施形態の電動弁におけるマグネットロータ及びロータ軸の要部拡大断面図、図３は図２のＡ−Ａ矢視図、図４は図２のＢ−Ｂ断面図及び一部拡大図である。なお、以下の説明における「上下」の概念は図１の図面における上下に対応する。 Next, an embodiment of the motorized valve and the refrigeration cycle system of the present invention will be described with reference to the drawings. FIG. 1 is a vertical cross-sectional view of the motor-operated valve of the embodiment, FIG. 2 is an enlarged cross-sectional view of a main part of the magnet rotor and the rotor shaft of the motor-operated valve of the embodiment, FIG. FIG. 2 is a sectional view taken along line BB and a partially enlarged view of FIG. The concept of "up and down" in the following description corresponds to the top and bottom in the drawing of FIG.

この電動弁１００は、「モータ部」としてのステッピングモータ１０と、弁ハウジング４０と、弁機構部５０と、非磁性体からなる密閉ケース６０とを備えている。 The motorized valve 100 includes a stepping motor 10 as a "motor portion", a valve housing 40, a valve mechanism portion 50, and a sealed case 60 made of a non-magnetic material.

ステッピングモータ１０は、ロータ軸１と、密閉ケース６０の内部に回転可能に配設されたマグネットロータ２と、密閉ケース６０の外周においてマグネットロータ２に対して対向配置されたステータユニット３とで構成されている。後述するように、ロータ軸１はマグネットロータ２の中心に取り付けられ、このロータ軸１は弁機構部５０側に延設されている。ステータユニット３は、樹脂製のボビン３１と、ボビン３１に巻装された上下一対のテータコイル３２と、磁性体からなる継鉄（ヨーク）３３を備えている。そして、継鉄３３の外周端部は円筒ガイカン３４内に嵌合され、継鉄３３と円筒ガイカン３４は樹脂モールド３５によって密閉されている。 The stepping motor 10 includes a rotor shaft 1, a magnet rotor 2 rotatably arranged inside the sealed case 60, and a stator unit 3 arranged to face the magnet rotor 2 on the outer circumference of the sealed case 60. Has been done. As will be described later, the rotor shaft 1 is attached to the center of the magnet rotor 2, and the rotor shaft 1 extends to the valve mechanism portion 50 side. The stator unit 3 includes a bobbin 31 made of resin, a pair of upper and lower theta coils 32 wound around the bobbin 31, and a joint iron (yoke) 33 made of a magnetic material. Then, the outer peripheral end portion of the joint iron 33 is fitted in the cylindrical guy can 34, and the joint iron 33 and the cylindrical guy can 34 are sealed by the resin mold 35.

弁ハウジング４０はステンレス等で略円筒形状に形成されており、その内側に弁室４０Ｒを有している。弁ハウジング４０の外周片側には弁室４０Ｒに導通される第１継手管４１が接続されるとともに、下端から下方に延びる筒状部に第２継手管４２が接続されている。また、第２継手管４２の弁室４０Ｒ側には弁座リング４３が嵌合されている。弁座リング４３の上端内側は弁ポート４３ａとなっており、第２継手管４２は弁ポート４３ａを介して弁室４０Ｒに導通される。なお、第１継手管４１、第２継手管４２及び弁座リング４３は、弁ハウジング４０に対してろう付け等により固着されている。 The valve housing 40 is made of stainless steel or the like and has a substantially cylindrical shape, and has a valve chamber 40R inside. A first joint pipe 41 conductive to the valve chamber 40R is connected to one side of the outer circumference of the valve housing 40, and a second joint pipe 42 is connected to a tubular portion extending downward from the lower end. A valve seat ring 43 is fitted on the valve chamber 40R side of the second joint pipe 42. The inside of the upper end of the valve seat ring 43 is a valve port 43a, and the second joint pipe 42 is conducted to the valve chamber 40R via the valve port 43a. The first joint pipe 41, the second joint pipe 42, and the valve seat ring 43 are fixed to the valve housing 40 by brazing or the like.

弁機構部５０は、支持部材５１と、弁ホルダ５２と、「弁部材」としてのニードル弁５３とを有している。支持部材５１は例えば合成樹脂製で略円柱形状に形成されており、その外周にはインサート成形により一体に設けられたステンレス製のフランジ部５１１を介して弁ハウジング４０の上端部に溶接等により固定されている。支持部材５１の中心には、ロータ軸１の軸線Ｌと同軸の雌ねじ部５１ａとそのねじ孔が形成されるとともに、雌ねじ部５１ａのねじ孔よりも径の大きな円筒状のガイド孔５１ｂが形成されている。 The valve mechanism portion 50 includes a support member 51, a valve holder 52, and a needle valve 53 as a “valve member”. The support member 51 is made of synthetic resin, for example, and is formed in a substantially cylindrical shape, and is fixed to the upper end of the valve housing 40 by welding or the like via a stainless steel flange portion 511 integrally provided on the outer periphery thereof by insert molding. Has been done. At the center of the support member 51, a female screw portion 51a coaxial with the axis L of the rotor shaft 1 and a screw hole thereof are formed, and a cylindrical guide hole 51b having a diameter larger than that of the screw hole of the female screw portion 51a is formed. ing.

弁ホルダ５２は円筒状の部材であり、ガイド孔５１ｂ内に嵌合されて軸線Ｌ方向に摺動可能に配設されている。そして、弁ホルダ５２の下端部にニードル弁５３が固着されている。弁ホルダ５２内には、バネ受け５２ａが軸線Ｌ方向に移動可能に設けられ、バネ受け５２ａとニードル弁５３との間に圧縮コイルバネ５２ｂが所定の荷重を与えられた状態で取り付けられている。 The valve holder 52 is a cylindrical member, which is fitted in the guide hole 51b and slidably arranged in the axis L direction. The needle valve 53 is fixed to the lower end of the valve holder 52. A spring receiver 52a is provided in the valve holder 52 so as to be movable in the axis L direction, and a compression coil spring 52b is attached between the spring receiver 52a and the needle valve 53 in a state where a predetermined load is applied.

ロータ軸１の支持部材５１側の外周には雄ねじ部１ａが形成されており、この雄ねじ部１ａが支持部材５１の雌ねじ部５１ａに螺合されている。そして、支持部材５１のガイド孔５１ｂ内で、弁ホルダ５２の上端部がロータ軸１の下端部に係合され、弁ホルダ５２及びニードル弁５３はロータ軸１によって回転可能に吊り下げた状態で支持されている。 A male screw portion 1a is formed on the outer circumference of the rotor shaft 1 on the support member 51 side, and the male screw portion 1a is screwed into the female screw portion 51a of the support member 51. Then, in the guide hole 51b of the support member 51, the upper end portion of the valve holder 52 is engaged with the lower end portion of the rotor shaft 1, and the valve holder 52 and the needle valve 53 are rotatably suspended by the rotor shaft 1. It is supported.

密閉ケース６０は、上端部が塞がれた略円筒形状に形成されており、弁ハウジング４０の上端に溶接等によって気密に固定されている。また、密閉ケース６０内の上部には、ガイド保持筒６１が嵌合され、このガイド保持筒６１の中央の円筒部６１ａ内にガイド６２が嵌め込まれている。ガイド６２は中央にガイド孔６２ａを有しており、このガイド孔６２ａ内にロータ軸１の上端部が回動自在に嵌め込まれている。円筒部６１ａの外周には、螺旋ガイド線体６３が装着されるとともに螺旋ガイド線体６３に螺合した可動ストッパ部材６４が設けられている。 The sealed case 60 is formed in a substantially cylindrical shape with the upper end closed, and is airtightly fixed to the upper end of the valve housing 40 by welding or the like. A guide holding cylinder 61 is fitted in the upper part of the sealed case 60, and the guide 62 is fitted in the cylindrical portion 61a at the center of the guide holding cylinder 61. The guide 62 has a guide hole 62a in the center, and the upper end portion of the rotor shaft 1 is rotatably fitted in the guide hole 62a. A spiral guide wire 63 is mounted on the outer periphery of the cylindrical portion 61a, and a movable stopper member 64 screwed into the spiral guide 63 is provided.

以上の構成により、ステッピングモータ１０の駆動により、マグネットロータ２及びロータ軸１が回転し、ロータ軸１の雄ねじ部１ａと支持部材５１の雌ねじ部５１ａとのねじ送り機構により、ロータ軸１が軸線Ｌ方向に移動する。そして、ニードル弁５３が軸線Ｌ方向に移動して弁座リング４３に対して近接又は離間する。これにより、弁ポート４３ａが開閉され、第１継手管４１から第２継手管４２へ、あるいは第２継手管４２から第１継手管４１へ流れる冷媒の流量が制御される。 With the above configuration, the magnet rotor 2 and the rotor shaft 1 are rotated by driving the stepping motor 10, and the rotor shaft 1 is aligned with the screw feed mechanism between the male screw portion 1a of the rotor shaft 1 and the female screw portion 51a of the support member 51. Move in the L direction. Then, the needle valve 53 moves in the axis L direction and approaches or separates from the valve seat ring 43. As a result, the valve port 43a is opened and closed, and the flow rate of the refrigerant flowing from the first joint pipe 41 to the second joint pipe 42 or from the second joint pipe 42 to the first joint pipe 41 is controlled.

また、マグネットロータ２には突起部２４が形成されており、マグネットロータ２の回転に伴って突起部２４が可動ストッパ部材６４を蹴り回すことにより、可動ストッパ部材６４が螺旋ガイド線体６３との螺合によって旋回しながら上下動する。そして、可動ストッパ部材６４が、螺旋ガイド線体６３の下端ストッパ６３ａに当接することによって、ロータ軸１の最下端位置での回転ストッパ作用が得られる。また、可動ストッパ部材６４が、ガイド保持筒６１の上端ストッパ６１ｂに当接することによって、ロータ軸１の最上端位置での回転ストッパ作用が得られる。 Further, a protrusion 24 is formed on the magnet rotor 2, and the protrusion 24 kicks the movable stopper member 64 as the magnet rotor 2 rotates, so that the movable stopper member 64 and the spiral guide wire 63 are formed. It moves up and down while turning by screwing. Then, when the movable stopper member 64 comes into contact with the lower end stopper 63a of the spiral guide wire 63, the rotation stopper action at the lowermost end position of the rotor shaft 1 can be obtained. Further, when the movable stopper member 64 comes into contact with the upper end stopper 61b of the guide holding cylinder 61, a rotation stopper action at the uppermost end position of the rotor shaft 1 can be obtained.

このように電動弁１００は、ステッピングモータ１０（モータ部）がマグネットロータ２及び金属製のロータ軸１を回転させるとともに、ロータ軸１の回転に伴うニードル弁５３の進退移動によって弁ポート４３ａを開閉させる電動弁である。 In this way, in the electric valve 100, the stepping motor 10 (motor portion) rotates the magnet rotor 2 and the metal rotor shaft 1, and the valve port 43a is opened and closed by the advance / retreat movement of the needle valve 53 accompanying the rotation of the rotor shaft 1. It is an electric valve to make it.

ロータ軸１はステンレス製のロッド部材を加工して形成されており、支持部材５１よりも上方に位置する第１軸部１１と、この第１軸部１１よりも径が大きい第２軸部１２とを有している。なお、第２軸部１２の支持部材５１に挿通される部分には前記雄ねじ部１ａが形成されている。また、第１軸部１１と第２軸部１２との径の違いにより、第１軸部１１と第２軸部１２との境界部には、前記ロータ軸１の軸線Ｌ側から第２軸部１２の外径方向に延びてロータ軸１の軸線Ｌに対して直角な面となる段差面部１３を有している。 The rotor shaft 1 is formed by processing a rod member made of stainless steel, and has a first shaft portion 11 located above the support member 51 and a second shaft portion 12 having a diameter larger than that of the first shaft portion 11. And have. The male screw portion 1a is formed in a portion of the second shaft portion 12 that is inserted into the support member 51. Further, due to the difference in diameter between the first shaft portion 11 and the second shaft portion 12, the boundary portion between the first shaft portion 11 and the second shaft portion 12 is a second shaft from the axis L side of the rotor shaft 1. It has a stepped surface portion 13 that extends in the outer diameter direction of the portion 12 and is a surface perpendicular to the axis L of the rotor shaft 1.

マグネットロータ２は、外周部を多極に着磁された円筒状のマグネット部２１と、その内部の軸線Ｌ方向の略中央部に延在する円盤部２２と、円盤部２２の中央のボス部２２ａ内に設けられたハブの機能を果たす固定部材２３と、前記の突起部２４とを有している。マグネット部２１と円盤部２２と突起部２４とはＰＰＳ等からなる一体成形部材として「マグネット本体」を構成しており、そのマグネット部２１はＰＰＳ等を母材として磁性粉を混入して成形されている。また、固定部材２３はロータ軸１と同材質のステンレス製であり、この固定部材２３はマグネット部２１及び円盤部２２（そのボス部２２ａ）と共に、インサート成形により一体に成形されている。 The magnet rotor 2 includes a cylindrical magnet portion 21 whose outer peripheral portion is magnetized in multiple poles, a disk portion 22 extending therein substantially in the central portion in the axis L direction, and a boss portion in the center of the disk portion 22. It has a fixing member 23 that functions as a hub provided in 22a, and the above-mentioned protrusion 24. The magnet portion 21, the disk portion 22, and the protrusion 24 form an integrally molded member made of PPS or the like, and the magnet portion 21 is formed by mixing magnetic powder with PPS or the like as a base material. ing. The fixing member 23 is made of stainless steel made of the same material as the rotor shaft 1, and the fixing member 23 is integrally molded together with the magnet portion 21 and the disk portion 22 (the boss portion 22a thereof) by insert molding.

マグネットロータ２の一部である固定部材２３は、円柱形状の固定部材本体部２３１と、固定部材本体部２３１より小径で円筒形状の円筒部２３２とを有して形成され、この固定部材本体部２３１と円筒部２３２とは軸線Ｌが中心軸となるように同軸になっている。また、固定部材２３は、固定部材本体部２３１と円筒部２３２とを軸線Ｌ方向に貫通する円柱状の挿通孔２３ａを有している。さらに、固定部材２３は、支持部材５１側の面が、挿通孔２３ａの内周面よりも軸線Ｌから外方に延びる面となっており、この面は、ロータ
軸１の段差面部１３と当接可能な当接面部２３ｂとなっている。 The fixing member 23, which is a part of the magnet rotor 2, is formed by having a cylindrical fixing member main body portion 231 and a cylindrical portion 232 having a diameter smaller than that of the fixing member main body portion 231 and having a cylindrical shape. The 231 and the cylindrical portion 232 are coaxial so that the axis L is the central axis. Further, the fixing member 23 has a columnar insertion hole 23a that penetrates the fixing member main body portion 231 and the cylindrical portion 232 in the axis L direction. Further, the surface of the fixing member 23 on the support member 51 side is a surface extending outward from the axis L with respect to the inner peripheral surface of the insertion hole 23a, and this surface is in contact with the stepped surface portion 13 of the rotor shaft 1. It is a contact surface portion 23b that can be contacted.

マグネットロータ２は、固定部材２３の挿通孔２３ａ内にロータ軸１（第１軸部１１）を挿通し、固定部材２３の当接面部２３ｂをロータ軸１の段差面部１３に当接させた状態となっている。これにより、ロータ軸１に対するマグネットロータ２の軸線Ｌ方向の位置出しがなされている。そして、固定部材２３における挿通孔２３ａの円筒部２３２側の開口端部の周囲Ａ（図２の二点鎖線）において、その２箇所（一部）にてロータ軸１と円筒部２３２とが溶接により固定され、この溶接による２つの溶融凝固部４，４が形成されている。また、図３に示すように、この溶融凝固部４，４は、それぞれが軸線Ｌ回りの４５°〜９０°の範囲内に形成されている。上記の溶接方法は、例えばレーザ溶接によるもので、レーザのスポットを挿通孔２３ａの開口端部とロータ軸１との境界の部分に照射する。このとき、溶融凝固部４の深さが、ロータ軸１と固定部材２３とを確実に固定できる深さとなるように、レーザの出力（強度）を調整する。 The magnet rotor 2 is in a state in which the rotor shaft 1 (first shaft portion 11) is inserted into the insertion hole 23a of the fixing member 23, and the contact surface portion 23b of the fixing member 23 is brought into contact with the stepped surface portion 13 of the rotor shaft 1. It has become. As a result, the position of the magnet rotor 2 with respect to the rotor shaft 1 in the axis L direction is made. Then, at the periphery A (two-dot chain line in FIG. 2) of the insertion hole 23a of the fixing member 23 on the cylindrical portion 232 side, the rotor shaft 1 and the cylindrical portion 232 are welded at the two locations (part). Two melt-solidified portions 4 and 4 are formed by this welding. Further, as shown in FIG. 3, each of the melt-solidified portions 4 and 4 is formed within a range of 45 ° to 90 ° around the axis L. The above welding method is, for example, laser welding, in which a laser spot is applied to the boundary between the open end of the insertion hole 23a and the rotor shaft 1. At this time, the laser output (intensity) is adjusted so that the depth of the melt-solidified portion 4 is such that the rotor shaft 1 and the fixing member 23 can be reliably fixed.

このように、固定部材２３は、インサート成形による一体成形にてマグネット部２１及び円盤部２２（マグネット本体）に結合された固定部材本体部２３１を有している。また。固定部材本体部２３１の外径より小径で、かつ、固定部材本体部２３１の体積より体積の小さな円筒状の円筒部２３２を有している。そして、ロータ軸１が挿通孔２３ａに挿通され、円筒部２３２とロータ軸１とが、挿通孔２３ａの開口端部の周囲Ａの一部にて溶接により固定されている。すなわち、固定部材本体部２３１の外径より小径で体積が小さく熱容量の小さい円筒部２３２にて全周溶接ではなく部分的に溶接されている。したがって、溶接時に過大な溶接熱の発生を抑えるように溶接できる。これにより、溶接熱によるロータ軸１の変形のない範囲で溶け込み量を増やせる。したがって、溶融凝固部４，４による部分的強度が全体の接合強度の向上として作用し、マグネットロータ２（固定部材２３）がロータ軸１から外れなくなる。なお、固定部材本体部２３１の方が、溶接で接合される円筒部２３２よりも外径が大きいので、マグネットロータ２の回転時にマグネット本体のトルクを固定部材本体部２３１に無理なく伝達することができ、マグネット本体から固定部材２３が外れなくなる。 As described above, the fixing member 23 has the fixing member main body portion 231 coupled to the magnet portion 21 and the disk portion 22 (magnet main body) by integral molding by insert molding. Also. It has a cylindrical cylindrical portion 232 having a diameter smaller than the outer diameter of the fixing member main body portion 231 and a volume smaller than the volume of the fixing member main body portion 231. Then, the rotor shaft 1 is inserted into the insertion hole 23a, and the cylindrical portion 232 and the rotor shaft 1 are fixed by welding at a part of the periphery A of the opening end portion of the insertion hole 23a. That is, the cylindrical portion 232 having a diameter smaller than the outer diameter of the fixing member main body portion 231 and having a small volume and a small heat capacity is partially welded instead of being welded all around. Therefore, welding can be performed so as to suppress the generation of excessive welding heat during welding. As a result, the amount of penetration can be increased within a range in which the rotor shaft 1 is not deformed by welding heat. Therefore, the partial strength of the melt-solidified portions 4 and 4 acts as an improvement in the overall joint strength, and the magnet rotor 2 (fixing member 23) does not come off from the rotor shaft 1. Since the fixed member main body 231 has a larger outer diameter than the cylindrical portion 232 joined by welding, the torque of the magnet main body can be reasonably transmitted to the fixed member main body 231 when the magnet rotor 2 rotates. The fixing member 23 cannot be removed from the magnet body.

また、ロータ軸１の軸線Ｌ回りの対向する２箇所において挿通孔２３ａの開口端部とロータ軸１とが溶接されており、溶接による各溶融凝固部４，４が、軸線Ｌ回りの４５°〜９０°の範囲内に形成されている。したがって、溶接時に過大な溶接熱の発生を抑えるように溶接できる。 Further, the open end portion of the insertion hole 23a and the rotor shaft 1 are welded at two opposite positions around the axis L of the rotor shaft 1, and the molten and solidified portions 4 and 4 by welding are 45 ° around the axis L. It is formed within the range of ~ 90 °. Therefore, welding can be performed so as to suppress the generation of excessive welding heat during welding.

また、図４の一点鎖線の円で示す一部拡大図に示すように、円筒部２３２の上端の挿通孔２３ａのロータ軸１側の内径角部がＣ０．１以下の糸面取り形状となっている。したがって、固定部材２３の円筒部２３２の端部において、ロータ軸１との隙間が小さくなり、部品ばらつきや溶接ばらつきに対しても、固定部材２３とロータ軸１との溶接性が向上し、固定強度がさらに向上する。なお、挿通孔２３ａのロータ軸１側の内径角部はエッジ形状でもよい。 Further, as shown in the partially enlarged view shown by the alternate long and short dash line circle in FIG. 4, the inner diameter angle portion of the insertion hole 23a at the upper end of the cylindrical portion 232 on the rotor shaft 1 side has a thread chamfered shape of C0.1 or less. There is. Therefore, at the end of the cylindrical portion 232 of the fixing member 23, the gap between the fixing member 23 and the rotor shaft 1 is reduced, and the weldability between the fixing member 23 and the rotor shaft 1 is improved and fixed even with respect to component variation and welding variation. The strength is further improved. The inner diameter corner of the insertion hole 23a on the rotor shaft 1 side may have an edge shape.

また、ロータ軸１と固定部材２３とがともにステンレス製で同材質となっているので、熱伝導率が同じであり、ロータ軸１と固定部材２３とが均等に溶融し、さらに固定強度が向上する。 Further, since the rotor shaft 1 and the fixing member 23 are both made of stainless steel and made of the same material, the thermal conductivity is the same, the rotor shaft 1 and the fixing member 23 are evenly melted, and the fixing strength is further improved. To do.

また、固定部材本体部２３１が円柱形状であり、固定部材本体部２３１の軸線Ｌ方向の寸法が、円筒部２３２の軸線Ｌ方向の寸法より大である。したがって、固定部材本体部２３１の熱容量を十分に確保でき、マグネット部２１と円盤部２２とを一体にした「マグネット本体」に対する溶接熱の影響を抑制できる。 Further, the fixing member main body 231 has a cylindrical shape, and the dimension of the fixing member main body 231 in the axis L direction is larger than the dimension of the cylindrical portion 232 in the axis L direction. Therefore, the heat capacity of the fixing member main body 231 can be sufficiently secured, and the influence of welding heat on the "magnet main body" in which the magnet portion 21 and the disk portion 22 are integrated can be suppressed.

また、図２に示すように、ロータ軸１の第１軸部１１の径をＤ、円筒部２３２の径方向の肉厚をｔ、円筒部２３２の軸線Ｌ方向の寸法（高さ）をＨ、としたとき、
ｔ＜Ｄ／２，Ｈ／ｔ≧１
となっている。これにより、円筒部２３２の熱容量が、ロータ軸１の熱容量に対して溶接に適したものとなり、溶接性が向上し、固定強度が向上する。 Further, as shown in FIG. 2, the diameter of the first shaft portion 11 of the rotor shaft 1 is D, the radial wall thickness of the cylindrical portion 232 is t, and the dimension (height) of the cylindrical portion 232 in the axis L direction is H. When,
t <D / 2, H / t ≧ 1
It has become. As a result, the heat capacity of the cylindrical portion 232 becomes suitable for welding with respect to the heat capacity of the rotor shaft 1, the weldability is improved, and the fixing strength is improved.

図５は固定部材の変形例１を示す図である。なお、以下の変形例１乃至３に対応する図５乃至図７において、（Ａ）図は固定部材の平面図、（Ｂ）図は固定部材の縦断面図、（Ｃ）図は固定部材の側面図である。また、マグネットロータ２は図示を省略して縦断面図にてボス部２２ａだけを一点鎖線で示してある。この変形例１の固定部材２５は、ロータ軸１と同材質のステンレス製であり、前記マグネット部２１及び円盤部２２（そのボス部２２ａ）と共に、インサート成形により一体に成形される。また、この変形例１の固定部材２５は、円柱形状の固定部材本体部２５１と、固定部材本体部２５１より小径で円筒形状の円筒部２５２とを有して形成されるとともに、ロータ軸１を挿通する円柱状の挿通孔２５ａを有している。この変形例１の固定部材本体部２５１は前記固定部材本体部２３１と同形状であるが、円筒部２５２は、前記円筒部２３２より小径となっている。 FIG. 5 is a diagram showing a modified example 1 of the fixing member. In FIGS. 5 to 7 corresponding to the following modified examples 1 to 3, FIG. 5A is a plan view of the fixing member, FIG. 3B is a vertical sectional view of the fixing member, and FIG. It is a side view. Further, the magnet rotor 2 is not shown, and only the boss portion 22a is shown by a alternate long and short dash line in a vertical cross-sectional view. The fixing member 25 of the modified example 1 is made of stainless steel of the same material as the rotor shaft 1, and is integrally molded together with the magnet portion 21 and the disk portion 22 (the boss portion 22a thereof) by insert molding. Further, the fixing member 25 of the modified example 1 is formed by having a cylindrical fixing member main body portion 251 and a cylindrical portion 252 having a smaller diameter than the fixing member main body portion 251 and having a cylindrical shape, and the rotor shaft 1 is formed. It has a cylindrical insertion hole 25a to be inserted. The fixing member main body 251 of the modified example 1 has the same shape as the fixing member main body 231 but the cylindrical portion 252 has a smaller diameter than the cylindrical portion 232.

図６は固定部材の変形例２を示す図である。この変形例２の固定部材２６は、ロータ軸１と同材質のステンレス製であり、前記マグネット部２１及び円盤部２２（そのボス部２２ａ）と共に、インサート成形により一体に成形される。また、この変形例２の固定部材２６は、略円柱形状の固定部材本体部２６１と、固定部材本体部２６１より小径で円筒形状の円筒部２６２とを有して形成されるとともに、ロータ軸１を挿通する円柱状の挿通孔２６ａを有している。この変形例２の固定部材本体部２６１は前記固定部材本体部２３１と同径であるが、外周の４箇所に凹溝２６１ａを有している。なお、円筒部２６２は変形例１の円筒部２５２と同形状である。凹溝２６１ａの大きさ、形状は、図の大きさとは限らず、小も大も考えられ、凹溝箇所も４箇所ではなく、４箇所以上でも、４箇所以下でもよい。 FIG. 6 is a diagram showing a modified example 2 of the fixing member. The fixing member 26 of the modified example 2 is made of stainless steel made of the same material as the rotor shaft 1, and is integrally molded together with the magnet portion 21 and the disk portion 22 (the boss portion 22a thereof) by insert molding. Further, the fixing member 26 of the modified example 2 is formed by having a substantially cylindrical fixing member main body portion 261 and a cylindrical portion 262 having a diameter smaller than that of the fixing member main body portion 261 and having a cylindrical shape, and the rotor shaft 1 It has a columnar insertion hole 26a through which the above is inserted. The fixing member main body 261 of the modified example 2 has the same diameter as the fixing member main body 231 but has concave grooves 261a at four locations on the outer circumference. The cylindrical portion 262 has the same shape as the cylindrical portion 252 of the first modification. The size and shape of the concave groove 261a are not limited to the size shown in the figure, and may be small or large, and the concave groove portion may be four or more or four or less, instead of four.

図７は固定部材の変形例３を示す図である。この変形例３の固定部材２７は、ロータ軸１と同材質のステンレス製であり、前記マグネット部２１及び円盤部２２（そのボス部２２ａ）と共に、インサート成形により一体に成形される。また、この変形例３の固定部材２７は、四角柱形状の固定部材本体部２７１と、固定部材本体部２７１より小径で円筒形状の円筒部２７２とを有して形成されるとともに、ロータ軸１を挿通する円柱状の挿通孔２７ａを有している。この変形例３の固定部材本体部２７１の最大径部は前記固定部材本体部２３１と同径である。なお、円筒部２７２は変形例１の円筒部２５２と同形状である。 FIG. 7 is a diagram showing a modified example 3 of the fixing member. The fixing member 27 of the modified example 3 is made of stainless steel of the same material as the rotor shaft 1, and is integrally molded together with the magnet portion 21 and the disk portion 22 (the boss portion 22a thereof) by insert molding. Further, the fixing member 27 of the modified example 3 is formed by having a quadrangular prism-shaped fixing member main body 271 and a cylindrical portion 272 having a smaller diameter than the fixing member main body 271 and having a cylindrical shape, and the rotor shaft 1 It has a columnar insertion hole 27a through which the The maximum diameter portion of the fixing member main body 271 of the modification 3 is the same diameter as the fixing member main body 231. The cylindrical portion 272 has the same shape as the cylindrical portion 252 of the first modification.

図５（Ｂ）、図６（Ｂ）、図７（Ｂ）に示すように、これらの変形例１乃至３においても、ロータ軸１の軸線Ｌ回りの対向する２箇所において溶接による各溶融凝固部４，４がそれぞれ形成されている。また、これらの変形例１乃至３において固定部材本体部２５１，２６１，２７１の断面形状は同じであり、その最大外径は同じである。しかし、固定部材本体部２５１，２６１，２７１の体積はそれぞれ異なっている。 As shown in FIGS. 5 (B), 6 (B), and 7 (B), also in these modified examples 1 to 3, each melt-solidification by welding is performed at two opposite locations around the axis L of the rotor shaft 1. Parts 4 and 4 are formed, respectively. Further, in these modified examples 1 to 3, the cross-sectional shapes of the fixing member main bodies 251,261,271 are the same, and the maximum outer diameter thereof is the same. However, the volumes of the fixing member main bodies 251, 26, 271 are different from each other.

なお、以上の実施形態及び変形例１乃至３における固定部材本体部２３１，２５１，２６１，２７１の体積は、円筒部２３２，２５２，２６２，２７２の体積のそれぞれ３倍以上であるのが好適である。また、固定部材本体部の形状はその他の形状、例えば三角形や五角形、それ以外の角柱形状でもよい。 It is preferable that the volumes of the fixing member main bodies 231,251 and 261,271 in the above embodiments and modifications 1 to 3 are three times or more the volumes of the cylindrical portions 232,252,262,272, respectively. is there. Further, the shape of the fixing member main body may be another shape, for example, a triangle, a pentagon, or another prism shape.

また、実施形態及び各変形例では、ロータ軸１の軸線Ｌ回りの対向する２箇所に溶接を施した例について説明したが、溶接箇所は軸線Ｌ回りに１箇所であってもよい。この場合
、軸線周りの１５０°〜２７０°の範囲に溶融凝固部が形成されていることが好ましい。また、軸線Ｌ周りの対向する２箇所、軸線Ｌ周りの１箇所に限らず、溶接箇所は軸線Ｌ回りの複数箇所（例：３箇所以上）であってもよい。この場合、溶接箇所は軸線Ｌ回りの回転対称な位置に施すのが好適であり、軸線周りの各溶融凝固部が形成されている角度は４５°未満でもよい。 Further, in the embodiment and each modification, an example in which welding is performed at two opposing locations around the axis L of the rotor shaft 1 has been described, but there may be one welding location around the axis L. In this case, it is preferable that the melt-solidified portion is formed in the range of 150 ° to 270 ° around the axis. Further, the welding points are not limited to two opposing points around the axis L and one place around the axis L, and may be a plurality of welded points (eg, three or more points) around the axis L. In this case, it is preferable that the welded portion is provided at a rotationally symmetric position around the axis L, and the angle at which each melt-solidified portion around the axis is formed may be less than 45 °.

図８は実施形態の冷凍サイクルシステムを示す図である。図において、符号１００は「膨張弁」を構成する本発明の実施形態の電動弁、２００は室外ユニットに搭載された室外熱交換器、３００は室内ユニットに搭載された室内熱交換器、４００は四方弁を構成する流路切換弁、５００は圧縮機である。電動弁１００、室外熱交換器２００、室内熱交換器３００、流路切換弁４００、及び圧縮機５００は、それぞれ導管によって図示のように接続され、ヒートポンプ式の冷凍サイクルシステムを構成している。なお、アキュムレータ、圧力センサ、温度センサ等は図示を省略してある。 FIG. 8 is a diagram showing a refrigeration cycle system of the embodiment. In the figure, reference numeral 100 is an electric valve according to an embodiment of the present invention constituting an "expansion valve", 200 is an outdoor heat exchanger mounted on an outdoor unit, 300 is an indoor heat exchanger mounted on an indoor unit, and 400 is an indoor heat exchanger. The flow path switching valve 500 constituting the four-way valve is a compressor. The motor-operated valve 100, the outdoor heat exchanger 200, the indoor heat exchanger 300, the flow path switching valve 400, and the compressor 500 are each connected as shown by a conduit to form a heat pump type refrigeration cycle system. The accumulator, pressure sensor, temperature sensor, etc. are not shown.

冷凍サイクルの流路は、流路切換弁４００により冷房運転時の流路と暖房運転時の流路の２通りに切換えられる。冷房運転時には、図に実線の矢印で示したように、圧縮機５００で圧縮された冷媒は流路切換弁４００から室外熱交換器２００に流入され、この室外熱交換器２００は凝縮器として機能し、室外熱交換器２００から流出された液冷媒は電動弁１００を介して室内熱交換器３００に流入され、この室内熱交換器３００は蒸発器として機能する。 The flow path of the refrigeration cycle is switched between the flow path during the cooling operation and the flow path during the heating operation by the flow path switching valve 400. During the cooling operation, as shown by the solid line arrow in the figure, the refrigerant compressed by the compressor 500 flows into the outdoor heat exchanger 200 from the flow path switching valve 400, and the outdoor heat exchanger 200 functions as a condenser. Then, the liquid refrigerant flowing out from the outdoor heat exchanger 200 flows into the indoor heat exchanger 300 via the electric valve 100, and the indoor heat exchanger 300 functions as an evaporator.

一方、暖房運転時には、図に破線の矢印で示したように、圧縮機５００で圧縮された冷媒は流路切換弁４００から室内熱交換器３００、電動弁１００、室外熱交換器２００、流路切換弁４００、そして、圧縮機５００の順に循環され、室内熱交換器３００が凝縮器として機能し、室外熱交換器２００が蒸発器として機能する。電動弁１００は、冷房運転時に室外熱交換器２００から流入する液冷媒、または暖房運転時に室内熱交換器３００から流入する液冷媒を、それぞれ減圧膨張し、さらにその冷媒の流量を制御する。 On the other hand, during the heating operation, as shown by the broken arrow in the figure, the refrigerant compressed by the compressor 500 is transferred from the flow path switching valve 400 to the indoor heat exchanger 300, the electric valve 100, the outdoor heat exchanger 200, and the flow path. The switching valve 400 and the compressor 500 are circulated in this order, the indoor heat exchanger 300 functions as a condenser, and the outdoor heat exchanger 200 functions as an evaporator. The electric valve 100 decompresses and expands the liquid refrigerant flowing from the outdoor heat exchanger 200 during the cooling operation and the liquid refrigerant flowing from the indoor heat exchanger 300 during the heating operation, and further controls the flow rate of the refrigerant.

以上、本発明の実施の形態について図面を参照して詳述してきたが、具体的な構成はこれらの実施の形態に限られるものではなく、本発明の要旨を逸脱しない範囲の設計の変更等があっても本発明に含まれる。 Although the embodiments of the present invention have been described in detail with reference to the drawings, the specific configuration is not limited to these embodiments, and the design changes, etc. within the range not deviating from the gist of the present invention, etc. Even if there is, it is included in the present invention.

１ロータ軸
１ａ雄ねじ部
２マグネットロータ
２１マグネット部（マグネット本体）
２２円盤部（マグネット本体）
２２ａボス部
２３固定部材
２３ａ挿通孔
２３１固定部材本体部
２３２円筒部
２５固定部材
２５１固定部材本体部
２５２円筒部
２５ａ挿通孔
２６固定部材
２６１固定部材本体部
２６２円筒部
２６ａ挿通孔
２７固定部材
２７１固定部材本体部
２７２円筒部
２７ａ挿通孔
３ステータユニット
４溶融凝固部
１０ステッピングモータ（モータ部）
４０弁ハウジング
４１第１継手管
４２第２継手管
４３弁座リング
４３ａ弁ポート
５０弁機構部
５１支持部材
５２弁ホルダ
５３ニードル弁（弁部材）
５１ａ雌ねじ部
１００電動弁（膨張弁）
２００室外熱交換器
３００室内熱交換器
４００流路切換弁
５００圧縮機
Ｌ軸線 1 Rotor shaft 1a Male thread part 2 Magnet rotor 21 Magnet part (magnet body)
22 Disc (magnet body)
22a Boss part 23 Fixing member 23a Insertion hole 231 Fixing member body part 232 Cylindrical part 25 Fixing member 251 Fixing member body part 252 Cylindrical part 25a Insertion hole 26 Fixing member 261 Fixing member body part 262 Cylindrical part 26a Insertion hole 27 Fixing member 271 Member body part 272 Cylindrical part 27a Insertion hole 3 Stator unit 4 Melt solidification part 10 Stepping motor (motor part)
40 Valve housing 41 1st joint pipe 42 2nd joint pipe 43 Valve seat ring 43a Valve port 50 Valve mechanism 51 Support member 52 Valve holder 53 Needle valve (valve member)
51a Female thread 100 Electric valve (expansion valve)
200 Outdoor heat exchanger 300 Indoor heat exchanger 400 Flow path switching valve 500 Compressor L axis

Claims

In an electric valve in which a motor unit rotates a magnet rotor and a metal rotor shaft, and opens and closes a valve port by moving the valve member forward and backward with the rotation of the rotor shaft.
The magnet rotor has a magnet main body having magnetism and a metal fixing member integrally molded with the magnet main body in the center of the magnet main body.
The fixing member has a cylindrical shape having a diameter smaller than the outer diameter of the fixing member main body and the fixing member main body connected to the magnet body by the integral molding and a volume smaller than the volume of the fixing member main body. Is formed, and an insertion hole is provided so as to penetrate the fixing member main body portion and the cylindrical portion in the axial direction of the rotor shaft.
The rotor shaft is inserted into the insertion hole, and the cylindrical portion and the rotor shaft are fixed by welding at a part around the opening end portion of the insertion hole.
The open end portion of the insertion hole of the cylindrical portion and the rotor shaft are welded at a plurality of rotationally symmetric points around the axis of the rotor shaft, and each melt-solidified portion by the welding is 90 around the axis. An electric valve characterized in that it is formed over an angle range of ° or less.

The opening end of the insertion hole of the cylindrical portion and the rotor shaft are welded to each other at two opposite positions around the axis of the rotor shaft.
The motorized valve according to claim 1, wherein each melt-solidified portion formed by welding is formed within a range of 45 ° to 90 ° around the axis.

The first or second claim is characterized in that the shape of the inner diameter corner portion of the opening end portion of the cylindrical portion is an edge shape in contact with the outer circumference of the rotor shaft or a thread chamfer shape having a C0.1 or less. The described motorized valve.

The motorized valve according to any one of claims 1 to 3, wherein the rotor shaft and the fixing member are made of the same material.

Any of claims 1 to 4, wherein the fixing member main body portion has a cylindrical shape, and the axial dimension of the fixing member main body portion is larger than the axial dimension of the cylindrical portion. The motorized valve described in item 1.

When the diameter of the rotor shaft is D, the radial wall thickness of the cylindrical portion is t, and the axial dimension of the cylindrical portion is H.
t <D / 2, H / t ≧ 1
The motorized valve according to any one of claims 1 to 5, wherein the motorized valve is characterized by the above.

The rotor shaft is located adjacent to the first shaft portion located on the opposite side of the valve member and the end portion of the first shaft portion on the valve member side, and is equal to or less than the length of the first shaft portion. It has a second shaft portion having a length of the above and a diameter larger than that of the first shaft portion.
The cylindrical portion and the rotor shaft are fixed so that the surface of the fixing member on the valve member side is located at the boundary between the first shaft portion and the second shaft portion. The electric valve according to any one of claims 1 to 6.

The magnet body includes a cylindrical magnet portion and a disk portion that extends to a substantially central portion inside the magnet portion in the axial direction and has a boss portion protruding toward the valve member in the center. Have and
The fixing member main body is coupled to the disk portion so as to extend in the axial direction from the surface of the disk portion opposite to the valve member to the end portion of the boss portion on the valve member side. The electric valve according to any one of claims 1 to 7, wherein the motorized valve is characterized in that.

A refrigeration cycle system including a compressor, a condenser, an expansion valve, and an evaporator, wherein the electric valve according to any one of claims 1 to 8 is used as the expansion valve. A refrigeration cycle system characterized by that.