JP2008292003A

JP2008292003A - Motor-operated selector valve

Info

Publication number: JP2008292003A
Application number: JP2008200482A
Authority: JP
Inventors: Shinichi Nemoto; 伸一根本; Kaoru Koyaizu; 薫小柳津; Tetsuya Aoki; 哲也青木
Original assignee: Fujikoki Corp
Current assignee: Fujikoki Corp
Priority date: 2008-08-04
Filing date: 2008-08-04
Publication date: 2008-12-04

Abstract

<P>PROBLEM TO BE SOLVED: To set the flow rate of a refrigerant flowing through a motor-operated valve constant in both forward and backward flow directions. <P>SOLUTION: This motor-operated valve 10 is provided with: a valve body 12 regulating a passage flow rate of a fluid by a valve element in a valve chest; a can 16 fixed to the valve body 12, and having a rotor 17 operating the valve element 13 incorporated therein; and a stator 18 externally fitted to the can 16 and rotationally driving the rotor 17. The motor-operated valve is structured such that the valve element 13 is made rotatable, and the flow rate of a fluid is set nearly constant in both the forward and backward flow directions of the fluid. Therefor, the outer surface of the valve element 13 is formed into a cylindrical shape, and the valve element is rotated by using the center line of the cylinder as an axis, and an orifice 13a and a cutout part 13b for running the refrigerant between passages 2a and 2b are formed on the valve element 13. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、空気調和機等に組み込まれて使用される電動弁に係り、特に、電動弁を流れる流体が、流れ方向が正逆に拘わらず、同一流量とすることができる電動弁に関する。 The present invention relates to a motor-operated valve that is used by being incorporated in an air conditioner or the like, and more particularly, to a motor-operated valve that allows a fluid flowing through the motor-operated valve to have the same flow rate regardless of the flow direction.

従来、この種の空気調和機、冷凍機等に組み込まれて使用される電動弁は、冷媒等の流体の流量を調整する機器であり、通常、弁室および弁座を備えた弁本体と、鍔状部を介して前記弁本体の上部に固着された有底円筒状のキャンとを備えており、該キャンの内側にはロータが内蔵され、前記キャンの外部には中央部に挿通孔を有するステータが外嵌されている。図１５は、前記したような従来の電動弁１の縦断面図を示しており、弁本体２は弁室２ｃと、ガイドブッシュ固定部２ｄと、キャン固着部２ｅとを備え、弁室２ｃには冷媒等の流体が出入する流体入出管２ａ、２ｂが設けられるとともに、その内部には弁軸３の先端に形成された弁体３ａであるニードル弁が接離する弁座２ｆが配設されている。 Conventionally, an electric valve used by being incorporated in this type of air conditioner, refrigerator, etc. is a device that adjusts the flow rate of a fluid such as a refrigerant, and usually includes a valve body having a valve chamber and a valve seat, A cylindrical can with a bottom fixed to the upper part of the valve body through a hook-shaped portion, and a rotor is built inside the can, and an insertion hole is formed in the center portion outside the can. The stator which has is externally fitted. FIG. 15 is a longitudinal sectional view of the conventional motor-operated valve 1 as described above. The valve body 2 includes a valve chamber 2c, a guide bush fixing portion 2d, and a can fixing portion 2e. Are provided with fluid inlet / outlet pipes 2a and 2b through which a fluid such as a refrigerant enters and exits, and a valve seat 2f to which a needle valve, which is a valve body 3a formed at the tip of the valve shaft 3, is contacted and separated. ing.

前記ガイドブッシュ固定部２ｄは、弁室の上方に位置し、弁本体２とガイドブッシュ４とを固定する。該ガイドブッシュ４の内周には雌ねじ部４ａが形成され、該雌ねじ部４ａには弁体ホルダ５の外周に形成された雄ねじ部５ａが螺合され、雌ねじ部と雄ねじ部とによりねじ送り機構が構成されている。そして、この弁体ホルダ５内には、下端部に弁体３ａを形成している弁軸３が摺動可能に嵌挿されており、該弁軸３は弁体ホルダ内５に縮装された圧縮コイルばね３ｂによって常時下方に付勢されている。 The guide bush fixing portion 2d is located above the valve chamber, and fixes the valve body 2 and the guide bush 4. A female screw portion 4a is formed on the inner periphery of the guide bush 4, and a male screw portion 5a formed on the outer periphery of the valve element holder 5 is screwed into the female screw portion 4a. Is configured. And in this valve body holder 5, the valve shaft 3 which forms the valve body 3a in the lower end part is slidably fitted, and this valve shaft 3 is shrunk in the valve body holder 5 inside. It is always urged downward by the compression coil spring 3b.

キャン固着部２ｅは弁本体２の上端に位置し、内周面をかしめ固定されるとともに下端面を溶接により接合されているリング状金属板で構成され、その外周部にてキャン６の鍔状部と溶接され弁本体２にキャン６を固定している。弁軸３とロータ７との結合は、弁軸３に弁体ホルダ５と雄ねじ部５ａを外嵌させるとともに、これを永久磁石付きのロータ７に内嵌させることによって行われている。弁軸３の上端にはプッシュナット３ｃが圧入固定され、その鍔部が弁軸３に若干の上下動を許容してロータ７に結合している。弁体ホルダ５に固定される下ストッパ４ｂとスリーブに形成される上ストッパ５ｂとによりストッパ機構が構成される。 The can fixing portion 2e is located at the upper end of the valve body 2 and is composed of a ring-shaped metal plate whose inner peripheral surface is fixed by caulking and whose lower end surface is joined by welding. The can 6 is fixed to the valve body 2 by welding to the valve body. The valve shaft 3 and the rotor 7 are coupled to each other by fitting the valve body holder 5 and the male screw portion 5a to the valve shaft 3 and fitting the valve shaft holder 5 to the rotor 7 with a permanent magnet. A push nut 3 c is press-fitted and fixed to the upper end of the valve shaft 3, and its flange portion is coupled to the rotor 7 while allowing the valve shaft 3 to move slightly up and down. The lower stopper 4b fixed to the valve body holder 5 and the upper stopper 5b formed on the sleeve constitute a stopper mechanism.

キャン６の内部にはロータ７が内蔵され、キャン６の外部にはステータ８が外嵌されている。ステータ８の内部には上下にステータコイル８ａおよびヨーク８ｂが格納されており、ステータコイル８ａはリード線８ｃおよびステータ８の外周に設けられたコネクタ８ｄを通じて通電される。ステータコイル８ａの通電によりヨーク８ｂが励磁されてロータ７を回転させ、ねじ送り機構により弁体ホルダ５と弁軸３を摺動させることによりを開閉作動させて冷媒の流量の調整を行っている。ステータ８にはコネクタのカバー８ｅが溶着されている。 A rotor 7 is built in the can 6, and a stator 8 is fitted on the outside of the can 6. A stator coil 8 a and a yoke 8 b are stored in the stator 8 in the vertical direction, and the stator coil 8 a is energized through a lead wire 8 c and a connector 8 d provided on the outer periphery of the stator 8. The yoke 8b is excited by energization of the stator coil 8a to rotate the rotor 7, and the valve body holder 5 and the valve shaft 3 are slid by a screw feed mechanism to open and close to adjust the refrigerant flow rate. . A connector cover 8e is welded to the stator 8.

ところで、上記の従来技術においては、冷媒の正・逆の流れの方向により、弁体３ａに対する冷媒圧に差が出てきて、結果として、冷媒の流れの方向により流量に差が出てくるという不具合がある。即ち、図１５において、冷媒が、流体入出管２ａから流体入出管２ｂに流れる場合には、弁体３ａに対して冷媒圧は下方向に作用するため、ねじ送り機構のバックラッシュによって常に下方向の位置にあるので、弁本体２との隙間が小さい。これに対して、流体入出管２ｂから流体入出管２ａに流れる場合には、弁体３ａに対して冷媒圧は上方向に作用するため、ねじ送り機構のバックラッシュによって常に上方向の位置となるため、弁本体２との隙間が大きくなって、その分流量を大きくしてしまうという不具合がある。 By the way, in said prior art, the difference in the refrigerant | coolant pressure with respect to the valve body 3a comes out according to the direction of the normal / reverse flow of a refrigerant | coolant, As a result, the difference in the flow volume comes out according to the direction of the refrigerant | coolant flow. There is a bug. That is, in FIG. 15, when the refrigerant flows from the fluid inlet / outlet pipe 2a to the fluid inlet / outlet pipe 2b, the refrigerant pressure acts downward with respect to the valve body 3a. Therefore, the gap with the valve body 2 is small. On the other hand, when the fluid flows from the fluid inlet / outlet pipe 2b to the fluid inlet / outlet pipe 2a, the refrigerant pressure acts upward with respect to the valve body 3a. Therefore, there is a problem that the gap with the valve body 2 becomes large and the flow rate is increased accordingly.

本発明は、このような不具合に鑑みてなされたものであって、その課題とするところは、電動弁を流れる冷媒等の流体が、正逆の流れ方向に拘わらず、同一流量とすることができる電動弁を提供することにある。 The present invention has been made in view of such problems, and the problem is that the fluid such as refrigerant flowing through the motor-operated valve has the same flow rate regardless of the forward and reverse flow directions. An object is to provide an electric valve that can be used.

前記課題を達成すべく本発明に係る電動弁は、下記の手段からなるものである。
請求項１記載の電動弁は、弁室内の弁体により流体の通過流量を調整する弁本体と、該弁本体に固着され前記弁体を作動させるロータを内蔵するキャンと、該キャンに外嵌され前記ロータを回転駆動するステータとを備えた電動弁において、前記弁体は、回転可能とし、流体の流れ方向が正逆いずれに拘わらず、流量が略同一となるように構成することを特徴とする。 In order to achieve the above object, the motor-operated valve according to the present invention comprises the following means.
The motor-operated valve according to claim 1 includes a valve body that adjusts a flow rate of fluid through a valve body in a valve chamber, a can that is fixed to the valve body and that has a built-in rotor that operates the valve body, and an outer fit to the can. In the motor-operated valve comprising the stator for rotating the rotor, the valve body is configured to be rotatable and configured to have substantially the same flow rate regardless of whether the fluid flow direction is normal or reverse. And

請求項２記載の電動弁は、弁本体と、該弁本体に固着されるキャンと、該キャンに嵌合されるロータとを備えた電動弁において、前記弁本体の弁室内にはロータに連動して回転する弁体を設け、流体の流れ方向が正逆いずれに拘わらず、流体の圧力に伴って形成される弁本体と弁体との隙間の大きさが略同一となるように構成することを特徴とする。 The motor-operated valve according to claim 2, wherein the motor-operated valve includes a valve body, a can fixed to the valve body, and a rotor fitted to the can, and the valve body of the valve body is interlocked with the rotor. The rotating valve body is provided so that the size of the gap between the valve body formed by the fluid pressure and the valve body is substantially the same regardless of whether the fluid flow direction is normal or reverse. It is characterized by that.

請求項３記載の電動弁は、上記いずれかの手段において、弁体は、外面円筒形状でこの円筒の中心線を軸として回転するようにし、弁体には流体を流路間で連通させる弁体流路を形成することを特徴とする。
請求項４記載の電動弁は、請求項３記載の手段において、弁体流路を複数設け、それぞれの弁体流路の断面積が相違するように形成することを特徴とする。
請求項５記載の電動弁は、請求項１〜４記載のいずれかの手段において、弁本体は、弁本体に連結される第１流路と第２流路とが直角に配置されるように形成することを特徴とする。 According to a third aspect of the present invention, there is provided the motor-operated valve according to any one of the above-mentioned means, wherein the valve body has an outer cylindrical shape and rotates around the center line of the cylinder, and the valve body allows fluid to communicate between the flow paths. A body flow path is formed.
According to a fourth aspect of the present invention, there is provided the motor-operated valve according to the third aspect, wherein a plurality of valve body passages are provided and the cross-sectional areas of the respective valve body passages are different.
According to a fifth aspect of the present invention, there is provided the motor-operated valve according to any one of the first to fourth aspects, wherein the first and second flow paths connected to the valve main body are arranged at right angles. It is characterized by forming.

請求項６記載の電動弁は、請求項３又は４記載の手段において、弁本体は、弁本体に連結される第１流路と第２流路とが円筒部側部で並行して配置されるように形成することを特徴とする。
請求項７記載の電動弁は、請求項３又は４記載の手段において、弁本体は、弁本体に連結される第１流路と第２流路とが略直線状に配置され、且つ、弁体流路は弁体を貫通するように形成することを特徴とする。
請求項８記載の電動弁は、請求項３又は４記載の電動弁の手段において、弁本体は、弁本体に連結される第１流路と第２流路とが円筒部の軸線延長部の側部に略並行して配置されるように形成することを特徴とする。 According to a sixth aspect of the present invention, there is provided the motor-operated valve according to the third or fourth aspect, wherein the first main flow path and the second flow path connected to the valve main body are arranged in parallel on the side of the cylindrical portion. It is characterized by forming so that it may form.
The motor-operated valve according to claim 7 is the means according to claim 3 or 4, wherein the valve main body has a first flow path and a second flow path connected to the valve main body arranged substantially linearly, and The body flow path is formed so as to penetrate the valve body.
The motor-operated valve according to claim 8 is the motor-operated valve means according to claim 3 or 4, wherein the valve main body includes a first flow path and a second flow path connected to the valve main body of the axial extension portion of the cylindrical portion. It is formed so that it may be arrange | positioned substantially parallel to a side part.

請求項９記載の電動弁は、請求項８記載の手段において、弁本体は円盤状部材からなり、該円盤状部材の中心部周辺に第１連通孔と第２連通孔とが穿設されると共に、円盤状部材のキャン側に、回転して第１連通孔と第２連通孔とを選択的に閉止する位置、及び、第１連通孔と第２連通孔の両方とも閉止しない位置とに移動可能に弁体が配置され、更に、円盤状部材の弁体を配置した側とは反対側の各連通孔に、第１流路と第２流路とを装着させることを特徴とする。
請求項１０記載の電動弁は、請求項９記載の手段において、第１流路と第２流路とは、円筒部の軸線延長部側部で且つ軸線を中心に一定の角度を有する位置に配置されることを特徴とする。
請求項１１記載の電動弁は、請求項９記載の手段において、弁体の弁体流路の上流側に多孔質部材を配置せしめたことを特徴とする。
請求項１２記載の電動弁は、請求項１１記載の手段において、上記弁体は、孔及びこの孔内にオリフィスを形成したオリフィス形成板を具備すると共に、上記多孔質部材は、上記オリフィス形成板における流体流入側に配置されていることを特徴とする。
請求項１３記載の電動弁は、請求項１２記載の手段において、上記孔に支持段部を形成し、この支持段部に多孔質部材とオリフィス形成板をこの順に固定する固定部材を設けたことを特徴とする。 According to a ninth aspect of the present invention, in the motor valve according to the eighth aspect, the valve body is formed of a disk-shaped member, and the first communication hole and the second communication hole are formed around the center of the disk-shaped member. And a position where the first communication hole and the second communication hole are selectively closed by rotating toward the can side of the disk-shaped member, and a position where both the first communication hole and the second communication hole are not closed. The valve body is movably disposed, and the first flow path and the second flow path are attached to each communication hole on the side opposite to the side on which the valve body of the disk-shaped member is disposed.
According to a tenth aspect of the present invention, there is provided the motor-operated valve according to the ninth aspect, wherein the first flow path and the second flow path are located on the side of the axial extension portion of the cylindrical portion and at a certain angle around the axis. It is characterized by being arranged.
The motor-driven valve according to claim 11 is characterized in that, in the means according to claim 9, a porous member is arranged on the upstream side of the valve body flow path of the valve body.
The motor-driven valve according to claim 12 is the means according to claim 11, wherein the valve body includes a hole and an orifice forming plate in which an orifice is formed in the hole, and the porous member is the orifice forming plate. It is arrange | positioned at the fluid inflow side in.
According to a thirteenth aspect of the present invention, in the means according to the twelfth aspect, a support step is formed in the hole, and a fixing member for fixing the porous member and the orifice forming plate in this order is provided in the support step. It is characterized by.

そして、このように構成された電動弁は、冷媒等の流体の流れが正・逆いずれの方向であっても漏れ量が略同一となるため、冷媒の流路を切り換える空調機等において正確な流量制御の実現が可能となる。また、上記機能に加えて流体の流れが正・逆いずれの方向であっても、流体圧が弁体を弁本体に押圧するようにしているから、弁室から流路への流体の漏れが僅少となる。また、電動弁から、流体の流動に伴う騒音が低減される。 The motor-operated valve configured as described above is accurate in an air conditioner or the like that switches the refrigerant flow path because the leakage amount is substantially the same regardless of whether the flow of fluid such as the refrigerant is in the forward or reverse direction. Flow rate control can be realized. In addition to the above functions, the fluid pressure presses the valve body against the valve body regardless of whether the fluid flow is forward or reverse, so that the fluid leaks from the valve chamber to the flow path. Become scarce. Moreover, the noise accompanying the flow of fluid is reduced from the motor-operated valve.

以上の説明から理解できるように、このように構成された本発明の電動弁は、冷媒等の流体の流れが正・逆いずれの方向であっても漏れ量が略同一となるため、流路を切り換える空調機等において正確な流量制御の実現が可能となる。また、上記機能に加えて流体の流れが正・逆いずれの方向であっても、流体圧が弁体を弁本体に押圧するようにしているから、弁室から流路への流体の漏れを僅少とする。更に、多孔質部材を弁体に具備せしめることにより、冷媒通過時の騒音を低減することができる。 As can be understood from the above description, the motor-operated valve of the present invention configured as described above has substantially the same amount of leakage regardless of whether the flow of fluid such as refrigerant is in the forward or reverse direction. It is possible to realize accurate flow control in an air conditioner or the like that switches between. In addition to the above function, the fluid pressure presses the valve body against the valve body regardless of whether the fluid flow is in the forward or reverse direction. Slightly. Furthermore, by providing the valve member with the porous member, it is possible to reduce noise when the refrigerant passes.

以下、実施例１に係る電動弁１０の一実施形態を図面に基づき詳細に説明する。図１は、本発明の実施例１に係る電動弁の最小流量時の状態を示す縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）であり、図２は、同実施例１に係る電動弁の最大流量時の状態を示す縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）である。電動弁１０は、弁室１２ａ内の弁体１３により冷媒の通過流量を調整する弁本体１２と、弁本体１２と一体で弁体１３を回転させるロータ１７を内蔵するキャン１６と、キャン１６に外嵌されロータ１７を回転駆動するステータ１８とを備えている。ロータ１７とステータ１８によりステッピングモータを構成している。 Hereinafter, an embodiment of a motor-operated valve 10 according to Example 1 will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view (A) showing a state at the minimum flow rate of the motor-operated valve according to Embodiment 1 of the present invention, and a bb sectional view (B) of FIG. They are a longitudinal cross-sectional view (A) which shows the state at the time of the maximum flow volume of the motor operated valve which concerns on the Example 1, and bb sectional drawing (B) of the same figure (A). The motor-operated valve 10 includes a valve body 12 that adjusts the flow rate of refrigerant through the valve body 13 in the valve chamber 12a, a can 16 that incorporates a rotor 17 that rotates the valve body 13 integrally with the valve body 12, and a can 16 And a stator 18 that is externally fitted and rotationally drives the rotor 17. The rotor 17 and the stator 18 constitute a stepping motor.

弁本体１２は本発明の基幹をなすものであり、黄銅等の金属から構成され、図１に示すように、上下に一定長の長さを有し、筒状形状でその筒状内部は弁室１２ｃを形成しており、その側部には弁室１２ｃに連通する第１連通孔１２ａを有し、該第１連通孔１２ａには第１流路２ａが連結されている。また、弁室の下部には弁室に連通する第２連通孔１２ｂを有し、該第２連通孔１２ｂには第２流路２ｂが連結されている。弁本体１０の上部外周肩部の段差部には、リング状の鍔状板１２ｄが固定される。そして、この鍔状板１２ｄに後述のキャン１６の下端部を突き合わせ溶接することにより固定される。 The valve body 12 forms the backbone of the present invention, and is made of a metal such as brass. As shown in FIG. 1, the valve body 12 has a certain length in the vertical direction, and has a cylindrical shape. A chamber 12c is formed, and a side portion thereof has a first communication hole 12a communicating with the valve chamber 12c, and the first flow path 2a is connected to the first communication hole 12a. The lower part of the valve chamber has a second communication hole 12b communicating with the valve chamber, and the second flow path 2b is connected to the second communication hole 12b. A ring-shaped bowl-shaped plate 12 d is fixed to the stepped portion of the upper outer peripheral shoulder of the valve body 10. And it fixes by butt-welding the lower end part of the below-mentioned can 16 to this saddle-like board 12d.

また、図１に示すように、鍔状板１２ｄの上面における中心点から一定角度、例えば１８０度離れた位置の２箇所にはストッパ１２ｅ，１２ｅが立設される。このストッパ１２ｅ，１２ｅは、弁体１３の回転を一定角度、例えば１８０度で規制し、弁本体１２の第１流路２ａ及び第２流路２ｂと位置決め可能に組付けられる。また、ストッパ１２ｅ，１２ｅは鍔状板１２ｄと同時にろう付け固定される。弁室１２ｃはその水平断面が円形で略円筒状に形成され、上面が開放され、下面が第２連通部１２ｂに連通し、内部に弁体１３が配置される。 Further, as shown in FIG. 1, stoppers 12e and 12e are erected at two positions at a certain angle, for example, 180 degrees apart from the center point on the upper surface of the bowl-shaped plate 12d. The stoppers 12e and 12e are assembled so that the rotation of the valve body 13 is regulated at a constant angle, for example, 180 degrees, and can be positioned with respect to the first flow path 2a and the second flow path 2b of the valve body 12. The stoppers 12e and 12e are brazed and fixed simultaneously with the saddle plate 12d. The valve chamber 12c is formed in a substantially cylindrical shape with a circular horizontal cross section, an upper surface is opened, a lower surface communicates with the second communication portion 12b, and a valve body 13 is disposed therein.

弁体１３は黄銅を素材として構成され、一定の厚みを有する筒体からなり、その下部には、弁室１２ｃに内接する外面円筒形状で、この円筒の中心線を軸として回転可能であり、冷媒を第１流路２ａと第２流路２ｂとの間で連通させる弁体流路１３が形成されている。実施例１の場合、弁体流路１３は、切欠き部１３ｂとオリフィス１３ａとからなる。切欠き部１３ｂは、図１，２に示すように、弁体１３下部の一定高さにわたって、略半円形分が欠けた状態で形成され、更に、弁体１３下部の残存部分の上記一定高さの中間位置にオリフィス１３ａが穿設される。そして、弁体１３は回転し、図１に示すように、上記残存部分が第１流路２ａを閉止し、オリフィス１３ａが対向している状態、及び、図２に示すように、上記切欠き部１３ｂが第１流路２ａと第２流路２ｂとを連通させる状態のいずれかに切り換え可能となっている。 The valve body 13 is made of brass and is made of a cylindrical body having a constant thickness. The lower part of the valve body 13 has an outer cylindrical shape inscribed in the valve chamber 12c, and is rotatable around the center line of the cylinder. A valve body flow path 13 is formed to allow the refrigerant to communicate between the first flow path 2a and the second flow path 2b. In the case of Example 1, the valve body flow path 13 consists of the notch part 13b and the orifice 13a. As shown in FIGS. 1 and 2, the notch 13 b is formed in a state in which a substantially semicircular portion is missing over a certain height of the lower part of the valve body 13, and further, the above-mentioned constant height of the remaining part of the lower part of the valve body 13 An orifice 13a is formed at an intermediate position. Then, the valve body 13 is rotated, and as shown in FIG. 1, the remaining portion closes the first flow path 2a and the orifice 13a is opposed, and as shown in FIG. The part 13b can be switched to any state in which the first flow path 2a and the second flow path 2b are communicated.

そのために、弁体１３は１８０度の範囲で回転駆動される。弁体１３上部は筒状の弁体キー部１３ｃが形成され、この弁体キー部１３ｃは、後述の弁体ホルダ１５に回転のみ連動可能に連結される。そのために、弁体キー部１３ｃの下部外周部は凹凸状に形成され弁体ホルダ１５の下部と係合されるようになっている。また、弁体１３の上下方向中間位置には段部１３ｄが形成され、弁本体１３の上面に当接するように形成され、更に、段部１３ｄの一部には上記ストッパ１２ｅ，１２ｅに当接可能な突起部１３ｅが形成されている。 Therefore, the valve body 13 is rotationally driven within a range of 180 degrees. A cylindrical valve body key portion 13c is formed on the upper portion of the valve body 13, and this valve body key portion 13c is connected to a later-described valve body holder 15 so that only rotation is possible. Therefore, the lower outer peripheral portion of the valve body key portion 13c is formed in an uneven shape and is engaged with the lower portion of the valve body holder 15. Further, a step portion 13d is formed at an intermediate position in the vertical direction of the valve body 13, and is formed so as to contact the upper surface of the valve body 13. Further, a part of the step portion 13d contacts the stoppers 12e, 12e. Possible projections 13e are formed.

上記弁体キー部１３ｃは、その上部の筒状の弁体ホルダ１５に嵌合される。この弁体ホルダ１５はロータ１７によって駆動される。弁体ホルダ１５はその上面にばね受け部が形成される。また、弁体ホルダ１５とロータ１７とは支持リング１７ａを介して結合されており、支持リング１７はロータ１７の成形時にインサートされた黄銅製の金属リングで構成されている。また、支持リング１７の内周孔部に弁体ホルダ１５の上部突部が嵌合し、上部突部の外周をかしめ固定して、ロータ１７、支持リング１７ａおよび弁体ホルダ１５を結合している。弁本体１２、弁体ホルダ１５、及び、支持リング１７ａは、全て黄銅より構成している。 The said valve body key part 13c is fitted by the cylindrical valve body holder 15 of the upper part. This valve element holder 15 is driven by a rotor 17. The valve body holder 15 has a spring receiving portion formed on the upper surface thereof. Further, the valve body holder 15 and the rotor 17 are coupled via a support ring 17 a, and the support ring 17 is composed of a brass metal ring inserted when the rotor 17 is molded. Further, the upper protrusion of the valve element holder 15 is fitted into the inner peripheral hole portion of the support ring 17, and the outer periphery of the upper protrusion is caulked and fixed to couple the rotor 17, the support ring 17 a and the valve element holder 15. The valve body 12, the valve body holder 15, and the support ring 17a are all made of brass.

ロータ１７は、後述のキャン１６に内装されるように外周面が円筒状であり、弁体ホルダ１５に軸支される。また、キャン１６の内面上底部と、弁体ホルダ１５の上面のばね受けとの間にばね１５ａが圧装される。この構成により、弁体ホルダ１５とロータ１７とは下方向において弁体１３側に押圧されているが、弁体１３に過大な荷重がかかった場合は、弁体ホルダ１５と弁体１３とが非係合となるようにすることも可能で、安全装置の役割を果たさせることができる。 The rotor 17 has a cylindrical outer peripheral surface so as to be housed in a can 16 described later, and is supported by the valve body holder 15. Further, a spring 15 a is press-fitted between the upper bottom of the inner surface of the can 16 and the spring receiver on the upper surface of the valve element holder 15. With this configuration, the valve element holder 15 and the rotor 17 are pressed toward the valve element 13 in the downward direction, but when an excessive load is applied to the valve element 13, the valve element holder 15 and the valve element 13 are It is also possible to be disengaged, and the role of a safety device can be fulfilled.

キャン１６は、ステンレス等の非磁性の金属から形成される有底円筒状をしており、弁本体１２の上部に固着されたステンレス製の鍔状板１２ｄに溶接等により固着され、内部は気密状態に保たれている。 The can 16 has a bottomed cylindrical shape made of a non-magnetic metal such as stainless steel, and is fixed to a stainless steel saddle plate 12d fixed to the upper portion of the valve body 12 by welding or the like, and the inside is airtight. It is kept in a state.

ステータ１８は、磁性材より構成されるヨーク１９と、このヨーク１９にボビン１９ａを介して巻回される上下のステータコイル１９ｂ，１９ｂとから構成され、キャン１６に外嵌する嵌合穴１８ａが形成されている。ステータ１８には、リード端子１９ｃが配設され、該リード端子１９ｃに接続されるコネクタ１９ｄを覆うカバー１９ｅが形成されている。ステータ１８から、ステータコイル１９ｂ，１９ｂに接続されたリード端子１９ｃが突出しており、このリード端子１９ｃに複数のリード線１９ｆが接続されたコネクタ１９ｄが連結されている。そして、コネクタ１９ｄを覆うカバー１９ｅがステータ１８に溶着され、カバー１９ｅ内はエポキシ樹脂等の充填材１９ｇで充填されている。ステータ１８は中心に下面開口の嵌合穴１８ａを有し、この嵌合穴１８ａにキャン１６が嵌合し、ステータ１８の下面に溶着された回り止め部材１８ｂにより弁本体１２およびキャン１６に固定される。 The stator 18 includes a yoke 19 made of a magnetic material, and upper and lower stator coils 19b and 19b wound around the yoke 19 via a bobbin 19a. Is formed. The stator 18 is provided with a lead terminal 19c, and a cover 19e is formed to cover the connector 19d connected to the lead terminal 19c. A lead terminal 19c connected to the stator coils 19b and 19b protrudes from the stator 18, and a connector 19d to which a plurality of lead wires 19f are connected is connected to the lead terminal 19c. A cover 19e covering the connector 19d is welded to the stator 18, and the inside of the cover 19e is filled with a filler 19g such as an epoxy resin. The stator 18 has a fitting hole 18a having a lower surface opening at the center. The can 16 is fitted into the fitting hole 18a, and is fixed to the valve body 12 and the can 16 by a rotation preventing member 18b welded to the lower surface of the stator 18. Is done.

実施例１は、上記構成により、第１，２の両流路２ａ，２ｂ間で冷媒を流す場合に、弁体１３を、図１に示す位置にすれば、小容量の冷媒を流すことができ、弁体１３を、図２に示す位置にすれば、大容量の冷媒を流すことができる。この場合、実施例１では，第１流路２ａから第２流路２ｂへ冷媒が流れると、冷媒圧力によって弁体１３が右方に押されるため，隙間からの漏れ量が大きく、逆に第２流路２ｂから第１流路２ａへ冷媒が流れると、圧力によって左方向に押されるために隙間からの漏れ量が小さくなる。したがって、オリフィス１３ａを流れる流量にこの漏れ量がプラスされるために、完全に、第１→第２の流量＝第２→第１の流量とになるわけではないが、従来技術のように、触媒の流れの方向により、弁体に対して開閉方向における順方向又は逆方向に冷媒圧が作用しないため、比較的両方向の流れが同一に近いものとなる。また、この実施例１では、電動弁１０を構成する部品点数が少ないことから、故障が少なく、また、冷媒の弁体１３に対する圧力を、弁本体１２が直接的に受けることになるから構造的・応力的に無理がなく、材料的にも節約することができる。 In the first embodiment, when the refrigerant is caused to flow between the first and second flow paths 2a and 2b, the valve body 13 is set to the position shown in FIG. If the valve body 13 is in the position shown in FIG. 2, a large volume of refrigerant can be flowed. In this case, in the first embodiment, when the refrigerant flows from the first flow path 2a to the second flow path 2b, the valve body 13 is pushed rightward by the refrigerant pressure, so that the amount of leakage from the gap is large. When the refrigerant flows from the second flow path 2b to the first flow path 2a, the amount of leakage from the gap is reduced because the refrigerant is pushed leftward by the pressure. Therefore, since this leakage amount is added to the flow rate flowing through the orifice 13a, it is not completely the first → second flow rate = second → first flow rate. Depending on the flow direction of the catalyst, the refrigerant pressure does not act in the forward or reverse direction in the opening / closing direction on the valve body, so the flows in both directions are relatively close to each other. Further, in the first embodiment, since the number of parts constituting the motor-operated valve 10 is small, there are few failures, and the valve body 12 directly receives the pressure of the refrigerant on the valve body 13.・ There is no unreasonable stress, and material can be saved.

この実施例２の電動弁２０では、第１流路２ａと第２流路２ｂを上下に平行に並べて、両流路２ａ，２ｂから受ける冷媒からの圧力によって、常に右方向（図３）に押圧される構造として、第１→第２≒第２→第１を実現するものである。実施例２は、図３，４に示し、図３は小容量の状態を、図４は大容量の状態を、それぞれ示している。
実施例２が実施例１と基本的に相違する点は、第１流路２ａの下部に平行させて第２流路２ｂを設けた点、及び、弁体２３の第１流路２ａ及び第２流路２ｂに対応する弁体２３に切欠き部２３ｂを形成すると共に、その残存部分の上下に且つ第１流路２ａ及び第２流路２ｂに対応する位置に、それぞれオリフィス２３ａ，２３ａを穿設した点である。また、弁本体２３の下面は閉止されている。 In the motor-operated valve 20 of the second embodiment, the first flow path 2a and the second flow path 2b are arranged in parallel in the vertical direction, and always in the right direction (FIG. 3) due to the pressure from the refrigerant received from both flow paths 2a and 2b. As a structure to be pressed, the first → second≈second → first is realized. The second embodiment is shown in FIGS. 3 and 4, FIG. 3 shows a small capacity state, and FIG. 4 shows a large capacity state.
The second embodiment is basically different from the first embodiment in that the second flow path 2b is provided in parallel with the lower portion of the first flow path 2a, and the first flow path 2a and the first flow path of the valve body 23 are the same. The notch 23b is formed in the valve body 23 corresponding to the two flow paths 2b, and the orifices 23a and 23a are respectively provided above and below the remaining portion and at positions corresponding to the first flow path 2a and the second flow path 2b. This is the point where it was drilled. Further, the lower surface of the valve body 23 is closed.

即ち、実施例２の場合も、弁体流路は、切欠き部２３ｂとオリフィス２３ａ，２３ａとからなる。切欠き部２３ｂは、図３，４に示すように弁体２３下部の一定高さにわたって、略半円形分が欠けた状態で形成され、更に、弁体２３下部の残存部分の上記一定高さの位置の２箇所にオリフィス２３ａ，２３ａが穿設される。なお、弁体２３の最下端部は、弁体２３の円滑な回転及び支持のために、切り欠かず、平面視正円部分を残すことで、弁本体２２に案内させるように形成している。また、この平面視正円部分の中心部分は、中心部に孔を形成したリング状となっている。これは冷媒圧がこの弁体２３の下方にかからず、弁本体２２の弁室底部に作用させて弁体２３の回転の障害とならないようにするためである。 That is, also in the second embodiment, the valve body flow path includes the notch portion 23b and the orifices 23a and 23a. As shown in FIGS. 3 and 4, the notch 23 b is formed in a state in which a substantially semicircular portion is missing over a certain height of the lower part of the valve body 23, and further, the above-mentioned constant height of the remaining part of the lower part of the valve body 23. Orifices 23a, 23a are drilled at two locations. The lowermost end of the valve body 23 is formed so as to be guided to the valve main body 22 by leaving a circular portion in a plan view without leaving a notch for smooth rotation and support of the valve body 23. . Moreover, the center part of this planar view regular-circle part becomes a ring shape which formed the hole in the center part. This is to prevent the refrigerant pressure from being applied below the valve body 23 and acting on the bottom of the valve chamber of the valve body 22 to obstruct the rotation of the valve body 23.

そして、弁体２３は回転し、図３に示すように、上記残存部分が第１流路２ａ及び第１流路２ｂを閉止し、それぞれのオリフィス２３ａ，２３ａが第１，２流路２ａ，２ｂに対向している状態、及び、図４に示すように、上記切欠き部２３ｂが第１流路２ａと第２流路２ｂとを連通させる状態のいずれかに切り換え可能となっている。
上記構成において、弁体２３は１８０度の範囲で回転駆動される。弁体２３上部は筒状の弁体キー部２３ｃが形成され、この弁体キー部２３ｃは、後述のロータ２７に回転のみ連動可能に連結されている点、そのために弁体キー部２３ｃの下部外周部は凹凸状に形成され弁体ホルダ２５の下部と係合されるようになっている点、及び、弁体２３の上下方向中間位置には段部２３ｄが形成され、弁本体２２の上面に当接するように形成され、更に、段部２３ｄの一部には上記ストッパ２２ｅ，２２ｅに当接可能な突起部２３ｅが形成されている点等は、実施例１と同じである。 Then, the valve body 23 rotates, and as shown in FIG. 3, the remaining portion closes the first flow path 2a and the first flow path 2b, and the respective orifices 23a and 23a are connected to the first and second flow paths 2a, 2a, As shown in FIG. 4, the cutout portion 23 b can be switched to either a state facing the 2 b or a state where the first flow path 2 a and the second flow path 2 b communicate with each other.
In the above configuration, the valve body 23 is driven to rotate within a range of 180 degrees. A cylindrical valve body key portion 23c is formed on the upper portion of the valve body 23, and this valve body key portion 23c is connected to a rotor 27, which will be described later, so that only rotation is possible, and for this reason, a lower portion of the valve body key portion 23c. A step portion 23d is formed at the middle of the valve body 23 in the vertical direction of the valve body 23 in that the outer peripheral portion is formed in an uneven shape and engaged with the lower portion of the valve body holder 25, and the upper surface of the valve body 22 Further, the second embodiment is the same as the first embodiment in that a protrusion 23e that can contact the stoppers 22e and 22e is formed on a part of the step 23d.

実施例２は、実施例１の効果に加えて、冷媒の流れがどのような方向であっても、弁体２３は第１流路２ａと第２流路２ｂから受ける圧力によって、常に右方向に押圧される構造となっていることから、冷媒の正・逆の流れ方向に拘わらず実施例１に比べて、一層、第１→第２の流量≒第２→第１の流量、を実現することができる。 In the second embodiment, in addition to the effects of the first embodiment, the valve body 23 is always in the right direction depending on the pressure received from the first flow path 2a and the second flow path 2b regardless of the direction of the flow of the refrigerant. Compared to the first embodiment, the first → second flow rate≈second → first flow rate is realized, regardless of the forward / reverse flow direction of the refrigerant. can do.

本実施例３の電動弁３０は、その基本的な課題は実施例１，２と同様とするも、その流路の位置及び弁体構造は基本的に相違する。実施例３では、弁本体３２に付設する第１流路２ａ及び第２流路２ｂは同一管径で一直線状に配置され、弁体３３の回転軸芯を挟んで弁本体３２の反対面に連結される。一方、弁体３３は全体として筒状に形成される点、及び、弁体３３がその回転軸芯部に弁体通路３３ａ，３３ｂが形成されている点などは実施例１，２と変わるところはない。 Although the basic problem of the electric valve 30 of the third embodiment is the same as that of the first and second embodiments, the position of the flow path and the valve body structure are basically different. In the third embodiment, the first flow path 2a and the second flow path 2b attached to the valve main body 32 are arranged in a straight line with the same pipe diameter, and on the opposite surface of the valve main body 32 with the rotation axis of the valve body 33 interposed therebetween. Connected. On the other hand, the point that the valve body 33 is formed in a cylindrical shape as a whole, and the point that the valve body 33 is formed with valve body passages 33a and 33b in the rotating shaft core portion are different from the first and second embodiments. There is no.

この実施例３では、第１流路２ａと第２流路２ｂから受ける冷媒の圧力によって、下流側に押圧されるものの、その形状は全く対称形状となっているために、第１→第２の流量≒第２→第１の流量を実現するものである。実施例３を、更に図５，６を用いて具体的に説明する。図５は小容量の状態を、図６は大容量の状態をそれぞれ示している。実施例３の弁体３３の特徴は、弁体流路として流路断面が小さい小オリフィス３３ａと、流路断面が大きい大オリフィス３３ｂとをクロス状に穿設した点である。また、弁本体３２の下面は閉止されている。 In the third embodiment, although it is pressed downstream by the pressure of the refrigerant received from the first flow path 2a and the second flow path 2b, the shape is completely symmetrical, so the first → second The flow rate of ≒ 2nd → 1st flow rate is realized. The third embodiment will be described in detail with reference to FIGS. FIG. 5 shows a small capacity state, and FIG. 6 shows a large capacity state. A feature of the valve element 33 of the third embodiment is that a small orifice 33a having a small flow path section and a large orifice 33b having a large flow path section are formed in a cross shape as valve body flow paths. Further, the lower surface of the valve body 32 is closed.

即ち、実施例３の場合は、弁体流路は、９０度に交差する２本の小・大のオリフィス３３ａ，３３ｂとからなる。なお、弁体３３の最下端部は、弁体３３の円滑な回転及び支持のために、切り欠かず、平面視正円部分を残すことで、弁本体に案内させるように形成している点は、実施例２と同じである。そして、弁体３３が、図５に示すように、小オリフィス３３ａが両流路２ａ，２ｂを結ぶ位置にあるときは、第１流路２ａ、第２流路２ｂ間において冷媒を流す場合に、その方向に拘わらず流量に差は発生しない。また、弁体３３をその９０度回転させて、図６に示すように、大断面のオリフィス３３ｂが両流路２ａ，２ｂを結ぶ位置にあり、第１流路２ａから第２流路２ｂに冷媒を流す場合も、その逆でも流量に差は発生しない。 That is, in the case of Example 3, the valve body flow path is composed of two small and large orifices 33a and 33b that intersect at 90 degrees. The lowermost end of the valve body 33 is formed so as to be guided to the valve main body by leaving a circular part in a plan view without leaving a notch for smooth rotation and support of the valve body 33. Is the same as in Example 2. When the valve body 33 is at a position where the small orifice 33a connects the two flow paths 2a and 2b as shown in FIG. 5, the refrigerant flows between the first flow path 2a and the second flow path 2b. Regardless of the direction, there is no difference in flow rate. Further, by rotating the valve body 33 by 90 degrees, as shown in FIG. 6, the orifice 33b having a large cross section is located at a position connecting both the flow paths 2a and 2b, and the first flow path 2a to the second flow path 2b. There is no difference in the flow rate when the refrigerant is flown or vice versa.

上記構成において、弁体３３は９０度の範囲で回転駆動される。そして、弁体３３上部は筒状の弁体キー部３３ｃが形成され、この弁体キー部３３ｃは、後述のロータ３７に回転のみ連動可能に連結されている点、そのために、弁体キー部３３ｃの下部外周部は凹凸状に形成され、ロータ３７の下部と係合されるようになっている点、及び、弁体３３の上下方向中間位置には段部３３ｄが形成され、弁本体３２の上面に当接するように形成され、更に、段部３３ｄの一部には上記ストッパ３２ｅに当接可能な突起部が形成されている点等は、実施例１，２と同じである。 In the above configuration, the valve body 33 is driven to rotate within a range of 90 degrees. A cylindrical valve body key portion 33c is formed on the upper portion of the valve body 33, and this valve body key portion 33c is connected to a rotor 37, which will be described later, so that only rotation is possible. A lower outer peripheral portion of 33c is formed in an uneven shape and is engaged with the lower portion of the rotor 37, and a step portion 33d is formed at an intermediate position in the vertical direction of the valve body 33. The second embodiment is the same as the first and second embodiments in that it is formed so as to be in contact with the upper surface of the first and second protrusions and a protrusion that can contact the stopper 32e is formed on a part of the step 33d.

実施例３は、実施例１の効果に加えて、冷媒の流れがどちらの方向であっても、弁体３３が冷媒から受ける圧力は同じであることから、大・小いずれの流量の場合でも、第１→第２の流量＝第２→第１の流量となる。 In the third embodiment, in addition to the effects of the first embodiment, the pressure that the valve body 33 receives from the refrigerant is the same regardless of the direction of the flow of the refrigerant. First → second flow rate = second → first flow rate.

この実施例４では、冷媒の入出管２ａ，２ｂを構成する２本の流路を弁体４３の回転軸芯と平行に縦に並べて、第１流路２ａと第２流路２ｂから受ける冷媒の圧力によって発生する冷媒の漏れ出しを同一にし、第１→第２の流量＝第２→第１の流量を実現するものである。 In the fourth embodiment, the two flow paths constituting the refrigerant inlet / outlet pipes 2a and 2b are arranged vertically in parallel with the rotational axis of the valve body 43, and are received from the first flow path 2a and the second flow path 2b. The leakage of the refrigerant generated by the pressure is the same, and the first → second flow rate = second → first flow rate is realized.

実施例４は図７〜９に示され、図７，９は、流量が小容量の場合を、図８は流量が大容量の場合をそれぞれ示している。具体的には、図７は、冷房（又は暖房）サイクルの除湿時の弁体位置、図８は、冷房・暖房時の弁体位置、図９は、暖冷（又は冷房）サイクルの除湿時の弁体位置を示している。実施例４が実施例１〜３と基本的に相違する点は、図７に示すように、第１流路２ａと第２流路２ｂとを左右に平行に配置し、両流路の上端部に円盤状の弁本体４２を配置し、該弁本体４２に２つの孔、即ち、第１連通孔４２ａ及び第２連通孔４２ｂを形成して上記流路を装着した点、及び、この弁本体４２の上面に１８０度だけ回転する合成樹脂等から成る弁体を設けた点にある。上記弁体４３は蓋状となっており、該蓋部分にはオリフィス４３ａ、即ち、比較的小断面の流通孔が穿設される。 Example 4 is shown in FIGS. 7 to 9, and FIGS. 7 and 9 show the case where the flow rate is a small capacity, and FIG. 8 shows the case where the flow rate is a large capacity. Specifically, FIG. 7 shows the position of the valve body during dehumidification of the cooling (or heating) cycle, FIG. 8 shows the position of the valve body during cooling and heating, and FIG. 9 shows the time of dehumidification during the heating and cooling (or cooling) cycle. The valve body position is shown. The fourth embodiment basically differs from the first to third embodiments in that, as shown in FIG. 7, the first flow path 2a and the second flow path 2b are arranged in parallel on the left and right, and the upper ends of both flow paths. A disc-shaped valve main body 42 is disposed in the portion, and two holes, that is, a first communication hole 42a and a second communication hole 42b are formed in the valve main body 42, and the flow path is mounted. The valve body made of a synthetic resin or the like that rotates by 180 degrees is provided on the upper surface of the main body 42. The valve body 43 has a lid shape, and an orifice 43a, that is, a relatively small cross-sectional flow hole is formed in the lid portion.

更に具体的に述べれば、弁本体４２は平面視円形に形成されると共にその中心部には凹部４２ｆが形成され、弁体４３の支持軸４３ｃが回転自在に挿通される。この弁体４３の外周部及び支持軸４３ｃは、弁体ホルダ３２４５の内周部に回転力が伝わるように連結されている。上記弁体ホルダ４５は、他の実施例と同様にロータ４７と一体であり、ロータ４７の回転が弁体ホルダ４５を介して弁体４３を回転させることになる。弁体４３は、左・右の第１連通孔４２ａ及び第２連通孔４２ｂを塞ぐことが可能な閉止部４３ｆと軸芯部４３ｇとからなり、該軸芯部４３ｇに支持軸４３ｃが挿通され、該支持軸４３ｃの回転により、閉止部４３ｆは、図７に示す第１連通孔４２ａを閉止する位置、図８に示す第１連通孔４２ａ及び第２連通孔４２ｂ共に閉止しない位置、及び、図９に示す第２連通孔４２ｂを閉止する位置となる。また、弁体４３が上記３つの位置以外に移動しないようにするために、２本のストッパ４２ｅ，４２ｅが弁本体４２上部で連通孔４２ａ，４２ｂの近傍に立設される。 More specifically, the valve main body 42 is formed in a circular shape in plan view, and a concave portion 42f is formed in the center thereof, and the support shaft 43c of the valve body 43 is rotatably inserted. The outer peripheral portion of the valve body 43 and the support shaft 43c are connected to the inner peripheral portion of the valve body holder 3245 so that the rotational force is transmitted. The valve body holder 45 is integrated with the rotor 47 as in the other embodiments, and the rotation of the rotor 47 rotates the valve body 43 via the valve body holder 45. The valve body 43 includes a closing portion 43f and a shaft core portion 43g capable of closing the left and right first communication holes 42a and the second communication hole 42b, and a support shaft 43c is inserted through the shaft core portion 43g. The rotation of the support shaft 43c causes the closing portion 43f to close the first communication hole 42a shown in FIG. 7, the position where both the first communication hole 42a and the second communication hole 42b shown in FIG. 8 do not close, and This is the position for closing the second communication hole 42b shown in FIG. Further, in order to prevent the valve body 43 from moving to other than the above three positions, two stoppers 42e and 42e are erected in the vicinity of the communication holes 42a and 42b on the valve main body 42.

実施例４は、実施例２，３の効果と同様に、冷媒の流れがどちらの方向であっても、弁体４３は冷媒圧により連通孔４２ａ，４２ｂに押圧される構造となっていることから、第１→第２の流量＝第２→第１の流量を実現することに加えて、弁本体４２と弁体４３との隙間が小さくなり、冷媒の漏れを僅少にすることができる。具体例においては、図７の冷房サイクル時の除湿時（冷媒は、第２流路から第１流路に流れる。）と、図９の暖房サイクル時の除湿時（冷媒は、第１流路から第２流路に流れる。）とを、略同一の冷媒流状態とすることができる。 In the fourth embodiment, similarly to the effects of the second and third embodiments, the valve body 43 is pressed against the communication holes 42a and 42b by the refrigerant pressure regardless of the direction of the refrigerant flow. Therefore, in addition to realizing the first → second flow rate = second → first flow rate, the gap between the valve main body 42 and the valve body 43 is reduced, and refrigerant leakage can be minimized. In the specific example, at the time of dehumidification during the cooling cycle of FIG. 7 (the refrigerant flows from the second flow path to the first flow path) and at the time of dehumidification during the heating cycle of FIG. 9 (the refrigerant is the first flow path). To the second flow path) can be set to substantially the same refrigerant flow state.

更に、本発明においては、実施例４に示す電動弁において、冷媒通過時に騒音が発生する場合には、その騒音を低減させることができる。即ち、図７〜９に示す電動弁の弁体４３に多孔質部材を具備せしめるのである。かかる多孔質部材を具備せしめた実施例５を図１０及び図１１に示す。 Further, in the present invention, in the motor operated valve shown in the fourth embodiment, when noise is generated when the refrigerant passes, the noise can be reduced. That is, a porous member is provided on the valve body 43 of the motor-operated valve shown in FIGS. A fifth embodiment provided with such a porous member is shown in FIGS.

以下、実施例５に係る電動弁１００の一実施形態を図面に基づき詳細に説明する。図１０は、実施例５に係る電動弁１００の最小流量時の状態を示す縦断面図であり、図１１は、図１０の矢印α方向からみた弁体位置の説明図である。電動弁１００は、弁本体９００と、弁本体９００と一体で弁体２００を回転させるロータ３００を内蔵するキャン４００と、キャン４００に外嵌されロータ３００を回転駆動するステータ５００とを備えている。ロータ３００とステータ５００によりステッピングモータを構成している。 Hereinafter, one Embodiment of the motor operated valve 100 which concerns on Example 5 is described in detail based on drawing. FIG. 10 is a longitudinal sectional view showing the state of the motor-operated valve 100 according to the fifth embodiment at the minimum flow rate, and FIG. 11 is an explanatory diagram of the valve body position as seen from the direction of the arrow α in FIG. The motor-operated valve 100 includes a valve body 900, a can 400 that incorporates a rotor 300 that rotates the valve body 200 integrally with the valve body 900, and a stator 500 that is fitted on the can 400 and rotationally drives the rotor 300. . The rotor 300 and the stator 500 constitute a stepping motor.

弁本体９００はステンレス等の金属から構成される。回転軸８００は、その上部の筒状の弁体ホルダ６００に嵌合される。この弁体ホルダ６００はロータ３００によって駆動される。弁本体９００は、その周縁にキャン４００の固着部を備えるとともに、弁本体９００を構成する円盤部側部で且つ軸線を中心に所定の角度を有する位置に２つの連通孔９１０，９２０が配置されている。また、この２つの連通孔９１０，９２０には、それぞれ流体入出管２ａ及び流体入出管２ｂが連結される。更に、弁本体９００の弁室１１０部分の中心部には、回転軸８００の下端を支持する凹部９００ａが形成される。弁体ホルダ６００には、その上面にばね受け部が形成される。また、弁体ホルダ６００とロータ３００とは支持リング７００を介して結合されており、支持リング７００はロータ３００の成形時にインサートされた金属リングで構成されている。また、支持リング７００の内周孔部に弁体ホルダ６００の上部突部が嵌合し、上部突部の外周をかしめ固定して、ロータ３００、支持リング７００および弁体ホルダ６００を結合している。 The valve body 900 is made of a metal such as stainless steel. The rotating shaft 800 is fitted into a cylindrical valve body holder 600 on the upper side thereof. The valve body holder 600 is driven by the rotor 300. The valve body 900 includes a fixing portion of the can 400 at the periphery thereof, and two communication holes 910 and 920 are arranged at positions on the side of the disk portion constituting the valve body 900 and having a predetermined angle about the axis. ing. The two communication holes 910 and 920 are connected to the fluid inlet / outlet pipe 2a and the fluid inlet / outlet pipe 2b, respectively. Furthermore, a concave portion 900 a that supports the lower end of the rotating shaft 800 is formed in the central portion of the valve chamber 110 portion of the valve body 900. The valve body holder 600 is formed with a spring receiving portion on the upper surface thereof. Further, the valve body holder 600 and the rotor 300 are coupled via a support ring 700, and the support ring 700 is configured by a metal ring inserted when the rotor 300 is molded. Further, the upper protrusion of the valve element holder 600 is fitted into the inner peripheral hole of the support ring 700, and the outer periphery of the upper protrusion is caulked and fixed to couple the rotor 300, the support ring 700, and the valve element holder 600.

ロータ３００は、後述のキャン４００に内装されるように外周面が円筒状であり、弁体ホルダ６００に軸支される。また、キャン４００の内面上底部と、弁体ホルダ６００の上面のばね受けとの間にばね８２０が縮装される。この構成により、弁体ホルダ６００とロータ３００とは弁本体９００側に押圧されている。 The rotor 300 has a cylindrical outer peripheral surface so as to be housed in a can 400 described later, and is supported by the valve body holder 600. Further, the spring 820 is mounted between the upper bottom of the inner surface of the can 400 and the spring receiver on the upper surface of the valve element holder 600. With this configuration, the valve body holder 600 and the rotor 300 are pressed toward the valve body 900.

キャン４００は、ステンレス等の非磁性の金属から形成される有底円筒状をしており、弁本体９００の上部に形成されたステンレス製の鍔状部分に溶接等により固着され、内部は気密状態に保たれている。 The can 400 has a bottomed cylindrical shape formed of a non-magnetic metal such as stainless steel, and is fixed to a stainless steel bowl-shaped portion formed on the upper portion of the valve body 900 by welding or the like, and the inside is airtight. It is kept in.

ステータ５００は、磁性材より構成されるヨーク５１０と、このヨーク５１０にボビン５２０を介して巻回される上下のステータコイル５３０，５３０とから構成され、キャン４００に外嵌する嵌合孔が形成されている。ステータ５００には、リード端子５４０が配設され、リード端子５４０に接続されるコネクタ５５０を覆うカバー５６０が形成されている。ステータ５００からは、ステータコイル５３０，５３０に接続されたリード端子５４０が突出しており、このリード端子５４０に複数のリード線５７０が接続されたコネクタ５５０が連結されている。そして、コネクタ５５０を覆うカバー５６０がステータ５００に溶着され、カバー５６０内はエポキシ樹脂等の充填材５８０で充填されている。ステータ５００は中心に下面開口の嵌合孔を有し、この嵌合孔にキャン４００が嵌合し、ステータ５００の下面に溶着された回り止め部材５００ａにより弁本体９００およびキャン４００に固定される。 The stator 500 includes a yoke 510 made of a magnetic material, and upper and lower stator coils 530 and 530 wound around the yoke 510 via a bobbin 520, and a fitting hole that fits outside the can 400 is formed. Has been. The stator 500 is provided with a lead terminal 540 and a cover 560 that covers the connector 550 connected to the lead terminal 540. A lead terminal 540 connected to the stator coils 530 and 530 protrudes from the stator 500, and a connector 550 to which a plurality of lead wires 570 are connected is connected to the lead terminal 540. A cover 560 covering the connector 550 is welded to the stator 500, and the inside of the cover 560 is filled with a filler 580 such as an epoxy resin. The stator 500 has a fitting hole having a lower surface opening at the center. The can 400 is fitted into the fitting hole, and is fixed to the valve main body 900 and the can 400 by a detent member 500a welded to the lower surface of the stator 500. .

弁体２００には、図７に示す弁体４３の弁体流路４３ａに多孔質部材を配置し、上記弁体流路４３ａと同じ流路であるオリフィス２２４が穿設されたオリフィス形成板２２５と、多孔質部材として上記オリフィス２２４の上流側に第１の多孔質部材２２６を設けている。さらに必要なら、オリフィス２２４の下流側に第２の多孔質部材を設けてもよい。
図１０では、第１及び第２の多孔質部材を配置するために、弁体２１０に孔２２１を形成し、この孔２２１に第１の多孔質部材２２６、オリフィス２２４を形成したオリフィス形成板２２５及び第２の多孔質部材２２３をこの順に配置し、これらで弁体２００の閉止部２２０を構成する。したがって、弁体２００は回転軸８００が挿入される軸芯部２１０と、閉止部２２０とで構成されることになる。即ち、弁体２００は、一定厚みを有し、所定角度離れた第１連通孔９１０及び第２連通孔９２０を塞ぐことが可能な閉止部２２０と、軸芯部２１０とが例えば合成樹脂等で一体成形されてなり、該軸芯部２１０に回転軸８００が挿通され、該弁体ホルダ６００の回転により、閉止部２２０は、第１連通孔９１０、及び第２連通孔９２０共に閉止しない位置、第２連通孔９２０を閉止する位置、及び第１連通孔９１０を閉止する位置となる。また、弁体２００が上記３つの位置以外に移動しないようにするために、ストッパ９３０が弁本体９００上部に立設される。 In the valve body 200, a porous member is disposed in the valve body flow path 43a of the valve body 43 shown in FIG. 7, and an orifice forming plate 225 in which an orifice 224 that is the same flow path as the valve body flow path 43a is formed. The first porous member 226 is provided on the upstream side of the orifice 224 as a porous member. If necessary, a second porous member may be provided on the downstream side of the orifice 224.
In FIG. 10, in order to arrange the first and second porous members, a hole 221 is formed in the valve body 210, and an orifice forming plate 225 in which a first porous member 226 and an orifice 224 are formed in the hole 221. And the 2nd porous member 223 is arrange | positioned in this order, and the closing part 220 of the valve body 200 is comprised by these. Therefore, the valve body 200 includes the shaft core portion 210 into which the rotating shaft 800 is inserted and the closing portion 220. That is, the valve body 200 has a constant thickness, and the closing portion 220 that can close the first communication hole 910 and the second communication hole 920 separated by a predetermined angle and the shaft core portion 210 are made of, for example, synthetic resin. The rotary shaft 800 is inserted into the shaft core portion 210, and the closing portion 220 does not close both the first communication hole 910 and the second communication hole 920 due to the rotation of the valve body holder 600. It becomes a position for closing the second communication hole 920 and a position for closing the first communication hole 910. Further, in order to prevent the valve body 200 from moving to other than the above three positions, a stopper 930 is erected on the upper part of the valve main body 900.

軸芯部２１０には棒状の連動杆２１１が立設され、該連動杆２１１は回転軸８００側に形成された略Ｕ形の駆動板８１０により前後から挟まれるように配置されている。なお、連動杆２１１を略Ｕ形に形成し、駆動板８１０を平板状に形成して、連動杆２１１が駆動板８１０を前後から挟むように配置しても同様の機能が得られる。 A rod-shaped interlocking rod 211 is erected on the shaft core portion 210, and the interlocking rod 211 is disposed so as to be sandwiched from the front and rear by a substantially U-shaped drive plate 810 formed on the rotating shaft 800 side. The same function can be obtained even if the interlocking rod 211 is formed in a substantially U shape, the drive plate 810 is formed in a flat plate shape, and the interlocking rod 211 is disposed so as to sandwich the drive plate 810 from the front and rear.

閉止部２２０は、その位置により、第１連通孔９１０又は第２連通孔９２０のいずれか、若しくは、両方を開とする作用を有する。（図１０，１１は、第１連通孔９１０を「閉」とし、流体が流体入出管２ｂから流体入出管２ａに流れる場合を示している。）弁体２００の閉止部２２０には孔２２１が形成され、該孔２２１には支持段部２２２が形成される。そして、この支持段部２２２上には、第２多孔質部材２２３、オリフィス２２４が穿設されたオリフィス形成板２２５、及び、第１多孔質部材２２６がこの順で嵌合され、前記各部材２２３，２２５，２２６が固定部材２２７によって孔２２１内に固定される。 The closing part 220 has an action of opening either the first communication hole 910 or the second communication hole 920 or both, depending on the position. (FIGS. 10 and 11 show the case where the first communication hole 910 is “closed” and the fluid flows from the fluid inlet / outlet pipe 2b to the fluid inlet / outlet pipe 2a.) A hole 221 is formed in the closing portion 220 of the valve body 200. The support step 222 is formed in the hole 221. On the support step 222, a second porous member 223, an orifice forming plate 225 in which an orifice 224 is formed, and a first porous member 226 are fitted in this order, and each member 223 is fitted. , 225, 226 are fixed in the hole 221 by a fixing member 227.

上流側の第１多孔質部材２２６は、ニッケル、銅などを主成分とする発泡金属或いは多孔質プラスチックを円盤状に形成し、これをオリフィス形成板２２５の上流側の孔２２１に嵌合させる。もちろん、オリフィス２２４部分のみを覆うようにしてもよい。発泡金属は気孔率が９０％以上のものが望ましい。また、第１多孔質部材２２６が層形状である場合は、２層以上の構造としても良い。 The first porous member 226 on the upstream side is formed of a foam metal or porous plastic mainly composed of nickel, copper or the like in a disc shape, and is fitted into the hole 221 on the upstream side of the orifice forming plate 225. Of course, only the orifice 224 portion may be covered. The foam metal preferably has a porosity of 90% or more. Moreover, when the 1st porous member 226 is a layer shape, it is good also as a structure of two or more layers.

下流側の第２多孔質部材２２３は、上流側の第１多孔質部材２２６と同様に、ニッケル、銅などを主成分とする発泡金属或いは多孔質プラスチックを円盤状に形成し、これをオリフィス形成板２２５の下流側の孔１２１に嵌合させる。また、第２多孔質部材２２３が層形状である場合は、２層以上の構造としても良い。更に、以上の説明においては、多孔質部材について述べたが、上記第１及び第２の多孔質部材２２６，２２３の一方又は両方をメッシュ状の金網部材に変更してもよいのは勿論である。
上記実施例５によれば、多孔質部材、例えば発泡金属の形成体又は多孔質プラスチックの成形体からなる部材が介装されているので、流体中の大きな気泡は、多孔質部材を通過する際に細分化され、その細分化された状態で、大きな気泡に成長することなく速やかに弁体と流出口との間に形成されるオリフィスに流入する。そして、流出口（オリフィス）を通過する際、その流入側と流出側に急激な圧力変動は発生せず、したがって、従来の電動弁に比して、流動音の低減効果が向上し、騒音を効果的に防止できる。なお、実施例５は、第１連通孔９１０と第２連通孔９２０とが、軸線を中心に所定角度を有する位置に配置する場合の実施例を示したが、この配置角度は、本発明の作用効果が実現する限りにおいて適宜選択される。 The second porous member 223 on the downstream side, like the first porous member 226 on the upstream side, is formed by forming a foamed metal or porous plastic mainly composed of nickel, copper, etc. into a disk shape, and forming this into an orifice. It fits in the hole 121 on the downstream side of the plate 225. Moreover, when the 2nd porous member 223 is a layer shape, it is good also as a structure of two or more layers. Furthermore, in the above description, the porous member has been described. However, it is needless to say that one or both of the first and second porous members 226 and 223 may be changed to a mesh-like wire mesh member. .
According to the fifth embodiment, since a porous member, for example, a member made of a foamed metal formed body or a porous plastic molded body is interposed, large bubbles in the fluid pass through the porous member. In the subdivided state, it quickly flows into an orifice formed between the valve body and the outlet without growing into a large bubble. And, when passing through the outlet (orifice), there is no sudden pressure fluctuation on the inflow side and outflow side, so that the effect of reducing the flow noise is improved compared to the conventional motorized valve, and the noise is reduced. It can be effectively prevented. In addition, although Example 5 showed the Example when the 1st communicating hole 910 and the 2nd communicating hole 920 arrange | position in the position which has a predetermined angle centering on an axis line, this arrangement | positioning angle shows the present invention. It is appropriately selected as long as the effect is realized.

実施例６に係る電動弁５０は、第１流路２ａと第２流路２ｂとが、弁本体５２を構成する円盤部の軸線延長部側部で且つ軸線を中心に一定の角度を有する位置に配置されることを特徴とする（図１２〜１４）。換言すれば、実施例４では、弁本体５２の中心に対して、２つの連通孔５２ａ，５２ｂを点対称の位置に、即ち、弁本体５２の中心に対して１８０度離して配置させたが、実施例６では、１３５度離して配置し、この２つの連通孔５２ａ，５２ｂに第１流路２ａと第２流路２ｂを設けるものである。 In the motor-operated valve 50 according to the sixth embodiment, the first flow path 2a and the second flow path 2b are located on the side of the axial extension portion of the disk portion constituting the valve body 52 and have a certain angle around the axis. (FIGS. 12 to 14). In other words, in the fourth embodiment, the two communication holes 52 a and 52 b are arranged at point-symmetric positions with respect to the center of the valve body 52, that is, 180 degrees apart from the center of the valve body 52. In the sixth embodiment, the first flow path 2a and the second flow path 2b are provided in the two communication holes 52a and 52b by being spaced apart by 135 degrees.

具体的に述べれば、図１２〜１４に示すように、弁本体５２は平面視円形に形成されると共に、その中心部には凹部５２ｆが形成され、弁体５３の支持軸５３ｃが回転自在に挿通される。この弁体５３は、弁体ホルダ５５に嵌合され、回転力が伝わるように連結されている。上記弁体ホルダ５５は、他の実施例と同様にロータ５７と一体であり、ロータ５７の回転が弁体ホルダ５５を介して弁体５３を回転させることになる。なお、キャン５６はキャン支持枠５２ｄを介して弁体５２に支持・固定されている。弁体５３は、１３５度離れた第１連通孔５２ａ、及び第２連通孔５２ｂを塞ぐことが可能な閉止部５３ｆと軸芯部５３ｇとからなり、該軸芯部５３ｇに支持軸５３ｃが挿通され、該弁体ホルダ５５の回転により、閉止部５３ｆは、図１２に示す第１連通孔５２ａ、及び第２連通孔５２ｂ共に閉止しない位置、図１３に示す第２連通孔５２ｂを閉止する位置、及び図１４に示す第１連通孔５２ａを閉止する位置となる。また、弁体５３が上記３つの位置以外に移動しないようにするために、１本のストッパ５２ｅが弁本体５２上部に立設される。 Specifically, as shown in FIGS. 12 to 14, the valve body 52 is formed in a circular shape in plan view, and a recess 52 f is formed at the center thereof, so that the support shaft 53 c of the valve body 53 is rotatable. It is inserted. The valve body 53 is fitted to the valve body holder 55 and connected so that rotational force is transmitted. The valve body holder 55 is integral with the rotor 57 as in the other embodiments, and the rotation of the rotor 57 rotates the valve body 53 via the valve body holder 55. The can 56 is supported and fixed to the valve body 52 via a can support frame 52d. The valve body 53 includes a closing portion 53f and a shaft core portion 53g capable of closing the first communication hole 52a and the second communication hole 52b separated by 135 degrees, and the support shaft 53c is inserted into the shaft core portion 53g. Then, by the rotation of the valve body holder 55, the closing portion 53f does not close both the first communication hole 52a and the second communication hole 52b shown in FIG. 12, and closes the second communication hole 52b shown in FIG. And it becomes a position which closes the 1st communicating hole 52a shown in FIG. Further, in order to prevent the valve body 53 from moving to other than the above three positions, one stopper 52e is erected on the valve main body 52.

実施例６は、実施例４，５の効果と同様に、冷媒の流れがどちらの方向であっても、弁体５３は冷媒圧により、第１連通孔５２ａ又は第２連通孔５２ｂに押圧される構造となっていることから、第１→第２の流量＝第２→第１の流量を実現することに加えて、弁本体と弁体との隙間が小さくなり、冷媒の漏れを僅少にすることができる。特に、本実施例６は、図１２の状態では、双方向で全開、図１３の状態では、第１流路→第２流路の方向で全閉、図１４の状態では、第２流路→第１流路の方向で全閉となる。 In the sixth embodiment, similar to the effects of the fourth and fifth embodiments, the valve body 53 is pressed against the first communication hole 52a or the second communication hole 52b by the refrigerant pressure regardless of which direction the refrigerant flows. Therefore, in addition to realizing the first → second flow rate = second → first flow rate, the gap between the valve body and the valve body is reduced, and refrigerant leakage is reduced. can do. In particular, the sixth embodiment is fully open in both directions in the state of FIG. 12, fully closed in the direction of the first flow path → second flow path in the state of FIG. 13, and the second flow path in the state of FIG. → Fully closed in the direction of the first flow path.

具体例には、図１３の冷房サイクル時の除湿時（冷媒は、第１流路２ａから第２流路２ｂに流れる。）と、図１４の暖房サイクル時の除湿時（冷媒は、第２流路２ｂから第１流路２ａに流れる。）とを、略同一の冷媒流状態とすることができる。更に、実施例６では、第１流路２ａと第２流路２ｂとを近接して設けることができ、外形がコンパクトになるとともに、弁室５２ｃ内における冷媒の移動が少なく、抵抗も少ないから、弁室５２ｃ内における冷媒の移動エネルギの損失も少なくて済むという効果もある。 Specific examples include dehumidification during the cooling cycle of FIG. 13 (the refrigerant flows from the first flow path 2a to the second flow path 2b) and dehumidification during the heating cycle of FIG. The flow from the flow path 2b to the first flow path 2a) can be substantially the same refrigerant flow state. Further, in the sixth embodiment, the first flow path 2a and the second flow path 2b can be provided close to each other, the outer shape becomes compact, the movement of the refrigerant in the valve chamber 52c is small, and the resistance is also small. There is also an effect that the loss of the moving energy of the refrigerant in the valve chamber 52c can be reduced.

なお、上記各実施例においては、小容量の流量を流すために、弁体流路として、オリフィスを形成したが、実施例５のように、弁体にオリフィスを形成しなければ流量を限りなくゼロに近い値となる。 In each of the above-described embodiments, an orifice is formed as a valve body flow path in order to flow a small volume flow rate. However, as in the fifth embodiment, the flow rate is not limited unless an orifice is formed in the valve body. The value is close to zero.

本発明の実施例１に係る電動弁の最小流量時の状態を示す縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The longitudinal cross-sectional view (A) which shows the state at the time of the minimum flow volume of the motor operated valve which concerns on Example 1 of this invention, and bb sectional drawing (B) of the same figure (A). 同実施例１に係る電動弁の最大流量時の状態を示す縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The longitudinal cross-sectional view (A) which shows the state at the time of the maximum flow volume of the motor operated valve which concerns on the Example 1, and bb sectional drawing (B) of the same figure (A). 本発明の実施例２に係る電動弁の最小流量時の状態を示す要部縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The principal part longitudinal cross-sectional view (A) which shows the state at the time of the minimum flow volume of the motor operated valve which concerns on Example 2 of this invention, and bb sectional drawing (B) of the same figure (A). 同実施例２に係る電動弁の最大流量時の状態を示す要部縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The principal part longitudinal cross-sectional view (A) which shows the state at the time of the maximum flow volume of the motor operated valve which concerns on the Example 2, and bb sectional drawing (B) of the same figure (A). 本発明の実施例３に係る電動弁の最小流量時の状態を示す要部縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The principal part longitudinal cross-sectional view (A) which shows the state at the time of the minimum flow volume of the motor operated valve which concerns on Example 3 of this invention, and bb sectional drawing (B) of the same figure (A). 同実施例３に係る電動弁の最大流量時の状態を示す要部縦断面図（Ａ）と、同図（Ａ）のｂ−ｂ断面図（Ｂ）。The principal part longitudinal cross-sectional view (A) which shows the state at the time of the maximum flow volume of the motor operated valve which concerns on the Example 3, and bb sectional drawing (B) of the same figure (A). 本発明の実施例４に係る電動弁の正方向の最小流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。The principal part longitudinal cross-sectional view at the time of the minimum flow rate of the positive direction of the motor operated valve which concerns on Example 4 of this invention (A), and valve body position explanatory drawing (B). 同実施例４に係る電動弁の最大流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。The principal part longitudinal cross-sectional view (A) at the time of the maximum flow volume of the motor operated valve which concerns on the same Example 4, and valve body position explanatory drawing (B). 同実施例４に係る電動弁の逆方向の最小流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。The principal part longitudinal cross-sectional view (A) at the time of the minimum flow rate of the reverse direction of the electrically operated valve which concerns on the Example 4 and valve body position explanatory drawing (B). 本発明の実施例５に係る電動弁の最小流量時の状態を示す縦断面図。The longitudinal cross-sectional view which shows the state at the time of the minimum flow volume of the motor operated valve which concerns on Example 5 of this invention. 図１０の矢印α方向からみた弁体位置の説明図。Explanatory drawing of the valve body position seen from the arrow (alpha) direction of FIG. 本発明の実施例６に係る電動弁の最大流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。なお、図（Ａ）は、図（Ｂ）のＤ−Ｄ断面。The principal part longitudinal cross-sectional view (A) at the time of the maximum flow volume of the motor operated valve which concerns on Example 6 of this invention, and valve body position explanatory drawing (B). In addition, FIG. (A) is a DD cross section of FIG. (B). 同実施例６に係る電動弁の逆方向の最小流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。なお、図（Ａ）は、図（Ｂ）のＤ−Ｄ断面。The principal part longitudinal cross-sectional view (A) at the time of the minimum flow rate of the reverse direction of the motor operated valve which concerns on the Example 6 and valve body position explanatory drawing (B). In addition, FIG. (A) is a DD cross section of FIG. (B). 同実施例６に係る電動弁の正方向の最小流量時の要部縦断面図（Ａ）と弁体位置説明図（Ｂ）。なお、図（Ａ）は、図（Ｂ）のＤ−Ｄ断面。The principal part longitudinal cross-sectional view (A) at the time of the minimum flow rate of the positive direction of the motor operated valve which concerns on the Example 6 and valve body position explanatory drawing (B). In addition, FIG. (A) is a DD cross section of FIG. (B). 従来技術に係る電動弁の縦断面図。The longitudinal cross-sectional view of the motor operated valve which concerns on a prior art.

Explanation of symbols

１・・・電動弁（従来技術），２・・・弁本体
２ａ・・・流体入出管[第１流路]，２ｂ・・・流体入出管[第２流路]
２ｃ・・・弁室，２ｄ・・・ガイドブッシュ固定部
２ｅ・・・キャン固着部，２ｆ・・・弁座
３・・・弁軸，３ａ・・・弁体
３ｂ・・・圧縮コイルばね，３ｃ・・・プッシュナット
４・・・ガイドブッシュ
４ａ・・・雌ねじ部，４ｂ・・・下ストッパ
５・・・弁体ホルダ
５ａ・・・雄ねじ部，５ｂ・・・上ストッパ
６・・・キャン，７・・・ロータ
８・・・ステータ，８ａ・・・ステータコイル
８ｂ・・・ヨーク，８ｃ・・・リード線
８ｄ・・・コネクタ，８ｅ・・・カバー
１０・・電動弁（実施例１）
１２・・弁本体，１２ａ・・第１連通孔
１２ｂ・・第２連通孔，１２ｃ・・弁室
１２ｄ・・鍔状板，１２ｅ・・ストッパ
１３・・・・弁体，１３ａ・・弁体流路［オリフィス］
１３ｂ・・弁体流路［切欠き部］，１３ｃ・・弁体キー部
１３ｄ・・段部，１３ｅ・・突起部
１５・・弁体ホルダ，１５ａ・・ばね
１６・・キャン
１７・・ロータ，１７ａ・・支持リンク
１８・・ステータ，１８ａ・・嵌合穴
１８ｂ・・回り止め部材
１９・・ヨーク，１９ａ・・ボビン
１９ｂ・・ステータコイル，１９ｃ・・リード端子
１９ｄ・・コネクタ，１９ｅ・・カバー
１９ｆ・・リード線，１９ｇ・・充填材
２０・・電動弁（実施例２）
２２・・弁本体，２２ａ・・第１連通孔
２２ｂ・・第２連通孔，２２ｃ・・弁室
２２ｄ・・鍔状板，２２ｅ・・ストッパ
２３・・・・弁体，２３ａ・・弁体流路［オリフィス］
２３ｂ・・弁体流路［切欠き部］，２３ｃ・・弁体キー部
２３ｄ・・段部，２３ｅ・・突起部
２５・・弁体ホルダ，２５ａ・・ばね
２６・・キャン
２７・・ロータ，２７ａ・・支持リンク，３０・・電動弁（実施例３）
３２・・弁本体，３２ａ・・第１連通孔
３２ｂ・・第２連通孔，３２ｃ・・弁室
３２ｄ・・鍔状板，３２ｅ・・ストッパ
３３・・・・弁体，３３ａ・・弁体流路［小オリフィス］
３３ｂ・・弁体流路［大オリフィス］，３３ｃ・・弁体キー部
３３ｄ・・段部，３３ｅ・・突起部
３５・・弁体ホルダ，３５ａ・・ばね
３６・・キャン
３７・・ロータ，３７ａ・・支持リンク
４０・・電動弁（実施例４）
４２・・弁本体，４２ａ・・第１連通孔
４２ｂ・・第２連通孔，４２ｃ・・弁室
４２ｅ・・ストッパ，４２ｆ・・凹部
４３・・・・弁体，４３ａ・・弁体流路［オリフィス］
４３ｃ・・支持軸，４３ｄ・・段部
４３ｆ・・閉止部，４３ｇ・・軸芯部
４５・・弁体ホルダ，４５ａ・・ばね
４６・・キャン
４７・・ロータ，４７ａ・・支持リンク
５０・・電動弁（実施例６）
５２・・弁本体，５２ａ・・第１連通孔
５２ｂ・・第２連通孔，５２ｃ・・弁室
５２ｄ・・キャン支持枠，５２ｅ・・ストッパ
５２ｆ・・凹部，５３・・・・弁体，５３ｃ・・支持軸
５３ｅ・・突起部，５３ｆ・・閉止部，５３ｇ・・軸芯部
５５・・弁体ホルダ，５５ａ・・ばね，５６・・キャン
５７・・ロータ，５７ａ・・支持リンク
１００・・電動弁（実施例５），１１０・・弁室
２００・・弁体，２１０・・軸芯部
２１１・・連動杆，２２０・・閉止部
２２１・・孔，２２２・・支持段部
２２３・・第２多孔質部材，２２４・・オリフィス
２２５・・オリフィス形成板，２２６・・第１多孔質部材
２２７・・固定部材，３００・・ロータ
４００・・キャン，５００・・ステータ，５００ａ・・回り止め部材
５１０・・ヨーク，５２０・・ボビン
５３０・・ステータコイル，５４０・・リード端子
５５０・・コネクタ，５６０・・カバー
５７０・・リード線，５８０・・充填材
６００・・弁体ホルダ，７００・・支持リング
８００・・回転軸，８１０・・・駆動板
８２０・・ばね，９００・・・弁本体
９１０・・・第１連通孔，９２０・・・第２連通孔
９３０・・・ストッパ DESCRIPTION OF SYMBOLS 1 ... Electric valve (prior art), 2 ... Valve main body 2a ... Fluid inlet / outlet pipe [1st flow path], 2b ... Fluid inlet / outlet pipe [2nd flow path]
2c: Valve chamber, 2d: Guide bush fixing portion 2e: Can fixing portion, 2f: Valve seat 3: Valve shaft, 3a: Valve body 3b: Compression coil spring, 3c ... Push nut 4 ... Guide bush 4a ... Female thread part, 4b ... Lower stopper 5 ... Valve element holder 5a ... Male thread part, 5b ... Upper stopper 6 ... Can 7 ... rotor 8 ... stator, 8a ... stator coil 8b ... yoke, 8c ... lead wire 8d ... connector, 8e ... cover 10,. )
12 .. Valve body, 12a ... First communication hole 12b ... Second communication hole, 12c ... Valve chamber 12d, saddle plate, 12e ... Stopper 13 ... Valve body, 13a ... Valve body Flow path [orifice]
13b ... Valve flow path [notch], 13c ... Valve key part 13d ... Step part 13e ... Projection part 15 ... Valve holder 15a ... Spring 16 ... Can 17 ... Rotor , 17a ··· Support link 18 ··· Stator 18a · · Fitting hole 18b · · Anti-rotation member 19 · · yoke 19a · bobbin 19b · stator coil 19c · · lead terminal 19d · connector · 19e · · Cover 19f · · Lead wire 19g · · Filler 20 · · Electric valve (Example 2)
··· Valve body, 22a ··· First communication hole 22b · ··· Second communication hole, 22c · · Valve chamber 22d · · · Plate, 22e · · · Stopper 23 · · · Valve body, 23a · · · valve body Flow path [orifice]
23b ... Valve flow path [notch part] 23c ... Valve key part 23d ... Step part 23e ... Protrusion 25 ... Valve holder 25a ... Spring 26 ... Can 27 ... Rotor 27a ... Support link, 30 ... Electric valve (Example 3)
32 ... Valve body, 32a ... First communication hole 32b ... Second communication hole, 32c ... Valve chamber 32d ... Saddle plate, 32e ... Stopper 33 ... Valve, 33a ... Valve Flow path [small orifice]
33b ... Valve flow path [Large orifice] 33c ... Valve key part 33d ... Step part 33e ... Protrusion 35 ... Valve holder 35a ... Spring 36 ... Can 37 ... Rotor 37a .. Support link 40 .. Motorized valve (Example 4)
42 ... Valve body 42a ... First communication hole 42b ... Second communication hole 42c ... Valve chamber 42e ... Stopper 42f ... Recess 43 ... Valve, 43a ... Valve flow path [Orifice]
43c ··· Support shaft, 43d · · Step portion 43f · · Closing portion, 43g · · Shaft core portion 45 · · Valve body holder, 45a · · · Spring 46 · · · Can 47 · · · Rotor, 47a · · · Support link 50 · ·・ Electric valve (Example 6)
52 ... Valve body 52a ... First communication hole 52b ... Second communication hole 52c ... Valve chamber 52d ... Can support frame 52e ... Stopper 52f ... Recess part 53 ... Valve 53c ... Support shaft 53e ... Projection part 53f ... Closure part 53g ... Shaft core 55 ... Valve body holder 55a ... Spring 56 ... Can 57 ... Rotor 57a ... Support link 100 ..Motorized valve (Embodiment 5), 110 ..Valve chamber 200 ..Valve body 210 ..Axis core part 211 ..Interlocking rod 220 ..Closed part 221 ..Hole 222 ..Supporting step part 223 .. second porous member 224 .. orifice 225 .. orifice forming plate 226 .. first porous member 227 .. fixing member 300 .. rotor 400 .. can 500 .. stator 500a. Non-rotating member 510 ・・ Yoke, 520 ・Bobbin 530 ··· Stator coil 540 · · Lead terminal 550 · · Connector 560 · · Cover 570 · · Lead wire 580 · · Filler 600 · · Valve body holder 700 · · Support ring 800 · · Rotating shaft 810 ... Drive plate 820 ... Spring, 900 ... Valve body 910 ... First communication hole, 920 ... Second communication hole 930 ... Stopper

Claims

A valve body that adjusts the flow rate of fluid by a valve body in the valve chamber; a can that is fixed to the valve body and that houses a rotor that operates the valve body; and a stator that is externally fitted to the can and rotationally drives the rotor. The motor-operated valve is characterized in that the valve body is configured to be rotatable so that the flow rate is substantially the same regardless of whether the fluid flow direction is normal or reverse.

In a motor-operated valve comprising a valve body, a can fixed to the valve body, and a rotor fitted to the can, a valve body that rotates in conjunction with the rotor is provided in the valve chamber of the valve body, What is claimed is: 1. A motor-operated valve configured to have substantially the same size of a gap between a valve body and a valve body formed in accordance with fluid pressure, regardless of whether the fluid flow direction is normal or reverse.

2. The valve body according to claim 1, wherein the valve body has an outer cylindrical shape and is rotated about the center line of the cylinder, and the valve body is formed with a valve body flow path that allows fluid to communicate between both flow paths. 2. The electric valve according to 2.

4. The motor-operated valve according to claim 3, wherein a plurality of valve body flow paths are provided in the valve body, and the cross-sectional areas of the valve body flow paths are different from each other.

5. The motor-operated valve according to claim 1, wherein the valve main body is formed such that the first flow path and the second flow path connected to the valve main body are arranged at right angles.

The valve body is formed so that the first flow path and the second flow path connected to the valve main body are arranged in parallel on the side of the cylindrical portion. A motorized valve.

The valve body is characterized in that the first flow path and the second flow path connected to the valve main body are arranged substantially linearly, and the valve body flow path is formed so as to penetrate the valve body. Item 5. The motor-operated valve according to any one of items 3 and 4.

The valve main body is formed so that the first flow path and the second flow path connected to the valve main body are arranged substantially in parallel with the side portion of the axial extension portion of the cylindrical portion. Or the motor operated valve of 4.

The valve body is made of a disk-shaped member, and a first communication hole and a second communication hole are formed around the center of the disk-shaped member, and the first communication hole is rotated to the can side of the disk-shaped member. And the second communication hole are selectively closed, and the valve body is arranged to be movable to a position where both the first communication hole and the second communication hole are not closed. The motor-operated valve according to claim 8, wherein the first flow path and the second flow path are attached to each of the communication holes on the side opposite to the side where the valve is disposed.

The motor-operated valve according to claim 9, wherein the first communication hole and the second communication hole are arranged on the side of the axial extension portion of the cylindrical portion and at a position having a predetermined angle about the axis.

10. The motor-operated valve according to claim 9, wherein a porous member is disposed upstream of the valve body flow path of the valve body.

12. The valve body includes a hole and an orifice forming plate in which an orifice is formed in the hole, and the porous member is disposed on a fluid inflow side of the orifice forming plate. The motorized valve described.

The motor-operated valve according to claim 12, wherein a support step portion is formed in the hole, and a fixing member for fixing the porous member and the orifice forming plate in this order is provided in the support step portion.