JP2011027148A - Electric valve - Google Patents

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JP2011027148A
JP2011027148A JP2009171927A JP2009171927A JP2011027148A JP 2011027148 A JP2011027148 A JP 2011027148A JP 2009171927 A JP2009171927 A JP 2009171927A JP 2009171927 A JP2009171927 A JP 2009171927A JP 2011027148 A JP2011027148 A JP 2011027148A
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valve
spacer
motor
valve body
guide bush
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JP5342951B2 (en
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Shoji Yamashita
将司 山下
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Fujikoki Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To effectively reduce refrigerant passing noise, by increasing a capacity of a valve chamber, without increase in size of a valve body or a guide bush. <P>SOLUTION: A straight hole 10 is formed to the valve body 2 of an electric valve A, and the guide bush 4 guiding a valve rod 3 is fixed to the valve body 2 through a tubular spacer 15 press-fitted in an opening part 12 side of the hole 10. A stopper 19 is formed to an inner peripheral flange part 18 disposed on a tip side of the spacer 15, and an end part 24a connected to the valve body 2 of a fluid inlet pipe 24 abuts on the stopper 19 and is restricted. The valve chamber 21 is formed to have a width so that a whole edge of the end part 24a of the fluid inlet pipe 24 enters therein at a position deeper in the hole 10 than the spacer 15. Since a flow of refrigerant from the fluid inlet pipe 24 spreads into the valve chamber 21 with enlarged capacity and stably passes around a valve element 31, the refrigerant passing noise is reduced. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

この発明は、冷凍サイクルにおいて膨張弁として組み込まれる電動弁に関する。   The present invention relates to an electric valve incorporated as an expansion valve in a refrigeration cycle.

従来、空気調和機、冷凍機等の冷凍サイクル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、弁室及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ものである。   Conventionally, an electric valve used by being incorporated in a refrigeration cycle such as an air conditioner or a refrigerator is a device that adjusts the flow rate of a fluid such as a refrigerant, and usually includes a valve body including 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.

そうした電動弁の一例として、特許文献１に開示されているものがある。特許文献１に開示されている流量制御弁は、冷媒の流通過程において、断面積の変化を少なくすることにより、冷媒等の流体の乱流等による渦の発生を抑え、冷媒の剥離等に基づく圧力変動を生じ難くして、冷房時に起こる高周波の耳障りな騒音を低減することを図っている。   One example of such an electric valve is disclosed in Patent Document 1. The flow control valve disclosed in Patent Document 1 is based on the separation of the refrigerant and the like by suppressing the generation of vortices due to the turbulent flow of the fluid such as the refrigerant by reducing the change in the cross-sectional area in the refrigerant circulation process. It is intended to make it difficult for pressure fluctuations to occur and to reduce high-frequency harsh noise that occurs during cooling.

図３は、従来の電動弁Ｂを、ステッピングモータのステータ（励磁コイル装置）を取り除いた状態で示した縦断面図である。電動弁Ｂにおいて、弁本体２の内部には弁室２１が形成されているとともに、弁本体２はガイドブッシュ固定部２２と、キャン受板２３とを備えている。弁本体２には、弁室２１に繋がって冷媒等の流体が出入する流体流入管２４及び流体流出管２５が接続されている。弁室２１には、弁軸３の先端に形成されたニードル弁状の弁体３１が接離する弁座２６が設けられている。ステッピングモータのステータ（図示せず）の駆動によって、後述するねじ送り機構を介して弁軸３が昇降されることにより、弁体３１の弁座２６に対する開度に応じて、流体流入管２４と流体流出管２５とを通じる冷媒の流量が制御される。   FIG. 3 is a longitudinal sectional view showing a conventional motor-operated valve B with the stator (excitation coil device) of the stepping motor removed. In the motor-operated valve B, a valve chamber 21 is formed inside the valve main body 2, and the valve main body 2 includes a guide bush fixing portion 22 and a can receiving plate 23. Connected to the valve body 2 are a fluid inflow pipe 24 and a fluid outflow pipe 25 through which a fluid such as a refrigerant enters and exits, connected to the valve chamber 21. The valve chamber 21 is provided with a valve seat 26 to which a needle valve-like valve body 31 formed at the tip of the valve shaft 3 contacts and separates. By driving a stator (not shown) of a stepping motor, the valve shaft 3 is moved up and down via a screw feed mechanism, which will be described later. The flow rate of the refrigerant through the fluid outflow pipe 25 is controlled.

ガイドブッシュ固定部２２は弁室２１の上方に位置しており、ガイドブッシュ４は、ガイドブッシュ固定部２２に圧入されることにより弁本体２に固定されている。ガイドブッシュ４の外周には雄ねじ部４１が形成され、雄ねじ部４１には弁軸ホルダ５の内周に形成された雌ねじ部５１が螺合されている。雄ねじ部４１と雌ねじ部５１とにより、ねじ送り機構が構成されている。弁軸ホルダ５内には、下端部に弁体３１を形成している弁軸３が摺動可能に嵌挿されている。弁軸３は、弁軸ホルダ内５に縮装された圧縮コイルばね３２によって常時下方に付勢されている。   The guide bush fixing portion 22 is located above the valve chamber 21, and the guide bush 4 is fixed to the valve body 2 by being press-fitted into the guide bush fixing portion 22. A male screw portion 41 is formed on the outer periphery of the guide bush 4, and a female screw portion 51 formed on the inner periphery of the valve shaft holder 5 is screwed to the male screw portion 41. The male screw portion 41 and the female screw portion 51 constitute a screw feeding mechanism. In the valve shaft holder 5, the valve shaft 3 which forms the valve body 31 in the lower end part is slidably fitted. The valve shaft 3 is always urged downward by a compression coil spring 32 that is mounted in the valve shaft holder 5.

キャン受板２３は、弁本体２の上端に対して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ている。キャン１は、その下端部がキャン受板２３の外周部に溶接されることにより、弁本体２に固定されている。弁軸３とロータ７とは、支持リング６を介して結合されている。支持リング６は、ロータ７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。支持リング６の内周孔部に弁軸ホルダ５の上部突部が嵌合し、この突部をかしめ固定することによって、ロータ７、支持シング６及び弁軸ホルダ５が結合されている。弁軸３の上端にはプッシュナット３３が圧入固定されており、プッシュナット３３の外周には、円筒状の圧縮コイルばね３４が緩く嵌合又は外周に弾接して取り付けられている。圧縮コイルばね３４は、ガイドブッシュ４の雄ねじ部４１と弁軸ホルダ５の雌ねじ部５１との螺合が外れた場合に、その螺合に復帰させる力を与える。また、弁軸３及びロータ７の上方移動の最上限は、ロータ７の上部に設けられているばね３４とキャン１の内面との接触によって与えられる。弁軸ホルダ５に固定される上ストッパ体８とガイドブッシュ４に固定される下ストッパ体９とにより、弁軸３の上下方向の行程を制限するストッパ機構が構成されている。   The can receiving plate 23 is composed of a ring-shaped metal plate whose inner peripheral surface is caulked and fixed to the upper end of the valve body 2 and whose lower end surface is joined by welding. The can 1 is fixed to the valve body 2 by welding the lower end of the can 1 to the outer periphery of the can receiving plate 23. The valve shaft 3 and the rotor 7 are coupled via a support ring 6. The support ring 6 is composed of a brass metal ring inserted when the rotor 7 is molded. The upper protrusion of the valve shaft holder 5 is fitted into the inner peripheral hole portion of the support ring 6, and the protrusion 7 is caulked and fixed, whereby the rotor 7, the support shim 6 and the valve shaft holder 5 are coupled. A push nut 33 is press-fitted and fixed to the upper end of the valve shaft 3, and a cylindrical compression coil spring 34 is loosely fitted or elastically attached to the outer periphery of the push nut 33. The compression coil spring 34 provides a force for returning to the screwing when the male screw part 41 of the guide bush 4 and the female screw part 51 of the valve shaft holder 5 are unscrewed. Further, the upper limit of the upward movement of the valve shaft 3 and the rotor 7 is given by the contact between the spring 34 provided on the upper portion of the rotor 7 and the inner surface of the can 1. The upper stopper body 8 fixed to the valve shaft holder 5 and the lower stopper body 9 fixed to the guide bush 4 constitute a stopper mechanism for limiting the vertical stroke of the valve shaft 3.

キャン１の内部にはロータ７が内蔵され、キャン１の外部には図示しないステータ（励磁コイル装置）が外嵌されている。ステータの内部に格納されているステータコイルに通電することにより、同じくステータの内部に格納されているヨーク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軸ホルダ５と弁軸３を相対移動させることにより、弁体３１を開閉作動させて冷媒の流量の調整が行われる。
弁軸３の先端に設けられている弁体３１によって弁本体２に形成された弁座２６を開閉する（開口面積を変化させる）ことにより流量を制御する。 A rotor 7 is built in the can 1, and a stator (excitation coil device) (not shown) is fitted on the outside of the can 1. By energizing the stator coil stored in the stator, the yoke similarly stored in the stator is excited to rotate the rotor 7, and the valve shaft holder 5 and the valve shaft 3 are relatively moved by the screw feed mechanism. By moving it, the valve body 31 is opened and closed to adjust the flow rate of the refrigerant.
The flow rate is controlled by opening and closing (changing the opening area) the valve seat 26 formed in the valve body 2 by the valve body 31 provided at the tip of the valve shaft 3.

ところで、前記した従来の電動弁Ｂにおいては、ねじ送り機構を構成する雄ねじ部４１を有するガイドブッシュ４が弁本体２のガイドブッシュ固定部２２に直接に圧入されている。そのため、ガイドブッシュ固定部２２は段部構造となっており、弁室２１は当該段部構造に続く小さな内径の筒状空間として形成せざるを得ず、弁室２１の容積が狭いものとなっている。   By the way, in the above-described conventional motor-operated valve B, the guide bush 4 having the male screw portion 41 constituting the screw feeding mechanism is directly press-fitted into the guide bush fixing portion 22 of the valve body 2. Therefore, the guide bush fixing portion 22 has a stepped structure, and the valve chamber 21 has to be formed as a cylindrical space having a small inner diameter following the stepped structure, and the volume of the valve chamber 21 is narrow. ing.

特開平１１−３７３０６号公報JP-A-11-37306

弁室の容積が狭いと、例えば、冷媒が流体流入管から弁室に向かって横方向から流入し、流れの向きを下方に向けて流体流出管から流出する場合、弁室に流入した冷媒は弁室内で十分に広がることができない。その結果、流体流入管から弁室に流入する際の横方向の速度成分が弁体と弁座との間に形成されているオリフィスを通過する流れに影響し、当該オリフィスを通過する流れに偏りが生じ、そうした偏りのある流れが変動して安定しない。かかる不安定な冷媒の流れに起因して、電動弁には耳障りな冷媒通過音が発生する。   When the volume of the valve chamber is small, for example, when the refrigerant flows in from the fluid inflow pipe toward the valve chamber from the lateral direction and flows out of the fluid outflow pipe with the flow direction downward, the refrigerant flowing into the valve chamber It cannot spread sufficiently in the valve chamber. As a result, the lateral velocity component when flowing into the valve chamber from the fluid inflow pipe affects the flow passing through the orifice formed between the valve body and the valve seat, and is biased to the flow passing through the orifice. And this biased flow fluctuates and is not stable. Due to the unstable refrigerant flow, an unpleasant refrigerant passing sound is generated in the motor-operated valve.

弁本体の側方から接続される流体流入管の弁本体の側壁に突き当てる構造を維持するために弁本体の側壁を十分確保する必要があるところ、従来構造のまま弁室容積を単純に拡大するのでは、弁本体が大型化せざるを得ず、また、送りねじ機構に備わるガイドブッシュも大径化し、弁本体の切削やリセス加工が困難になり、ガイドブッシュの容易な圧入構造、即ち、電動弁の容易な組立構造が得られなくなる。   In order to maintain a structure that abuts against the side wall of the valve body of the fluid inflow pipe connected from the side of the valve body, it is necessary to sufficiently secure the side wall of the valve body. Therefore, the valve body has to be enlarged, and the guide bush provided in the feed screw mechanism is also increased in diameter, making it difficult to cut and recess the valve body. Thus, an easy assembly structure of the motor-operated valve cannot be obtained.

そこで、弁本体やガイドブッシュを大型化することなく、弁室の大容積化を可能にする点に解決すべき課題がある。
この発明の目的は、上記課題を解決することであり、弁装置外形を大きくすることなく弁室の大容積化を図って冷媒通過音を効果的に低減させることができる電動弁を提供することである。 Therefore, there is a problem to be solved in that the volume of the valve chamber can be increased without increasing the size of the valve body and the guide bush.
An object of the present invention is to solve the above-described problem, and to provide an electric valve capable of effectively reducing refrigerant passage noise by increasing the volume of a valve chamber without increasing the outer shape of the valve device. It is.

上記の課題を解決するため、この発明による電動弁は、冷媒が導入される弁室及び弁座を有する弁本体と、前記弁座に対向する弁棒と、駆動モータの回転運動を直線運動に変換して前記弁棒に伝達する送りねじ機構とを備え、前記送りねじ機構は、前記弁本体に固定されているとともに前記弁棒の移動を案内し且つねじ送りを行うねじ部を有するガイドブッシュと、前記弁棒と連結され前記モータによって回転され前記ねじ部と螺合するねじ部を有するロータとを備える電動弁であって、前記ガイドブッシュを、当該ガイドブッシュを取り囲むスペーサを介して前記弁本体に固定することにより、前記弁室の容積を拡大したことを特徴としている。   In order to solve the above problems, an electric valve according to the present invention has a valve body having a valve chamber and a valve seat into which a refrigerant is introduced, a valve rod facing the valve seat, and a rotational movement of a drive motor in a linear motion. A feed screw mechanism for converting and transmitting to the valve stem, the feed screw mechanism being fixed to the valve body and having a screw portion for guiding the movement of the valve stem and performing screw feed And a rotor having a threaded portion connected to the valve stem and rotated by the motor and screwed with the threaded portion, wherein the guide bush is connected to the valve via a spacer surrounding the guide bush. The volume of the valve chamber is increased by fixing to the main body.

本電動弁によれば、弁室の容積が従来品と比較して拡大されているので、流体流入管から弁室に流入した冷媒は、拡大された弁室に広がり、流体流入管からの流入横方向の速度成分が緩和される。したがって、弁棒の先端に設けられている弁体と弁室の底部に設けられている弁座との間を流れる冷媒の流れは、弁体の周りにおいて偏りなく且つ安定した流れになる。   According to this motor-operated valve, since the volume of the valve chamber is enlarged compared to the conventional product, the refrigerant flowing into the valve chamber from the fluid inlet pipe spreads into the enlarged valve chamber and flows into the valve inlet from the fluid inlet pipe. The lateral velocity component is relaxed. Therefore, the flow of the refrigerant flowing between the valve body provided at the tip of the valve stem and the valve seat provided at the bottom of the valve chamber is a non-uniform and stable flow around the valve body.

本発明による電動弁は、上記のように構成されているので、弁棒の先端に設けられている弁体と弁室の底部に設けられている弁座との間を流れる冷媒の流れは、弁体の周りにおいて偏りなく且つ安定した流れになり、弁体と弁座との間を流れる冷媒に通過音が発生し難くなり、電動弁の外形を大型化することなく静音化することができる。   Since the motor-operated valve according to the present invention is configured as described above, the flow of refrigerant flowing between the valve body provided at the tip of the valve stem and the valve seat provided at the bottom of the valve chamber is: There is no unevenness and a stable flow around the valve body, and it is difficult for passage sound to occur in the refrigerant flowing between the valve body and the valve seat, and it is possible to reduce the noise without increasing the size of the motor-operated valve. .

本発明による電動弁の一実施例を示す縦断面図である。It is a longitudinal cross-sectional view which shows one Example of the motor operated valve by this invention. 本発明による電動弁の冷媒通過音の周波数特性を、従来品の場合と比較して示すグラフである。It is a graph which shows the frequency characteristic of the refrigerant passing sound of the electric valve by this invention compared with the case of a conventional product. 従来の電動弁の一例を示す縦断面図である。It is a longitudinal cross-sectional view which shows an example of the conventional motor operated valve.

以下、添付した図面に基づいて、この発明による電動弁の実施例を説明する。図１に本発明による電動弁の一実施例を示す。なお、図１に示す電動弁の各構成要素及び部位のうち、図３に示した電動弁の対応する要素及び部位については、それらに付された符号と同じ符号を付すことで、再度の説明を省略する。   Hereinafter, embodiments of a motor-operated valve according to the present invention will be described with reference to the accompanying drawings. FIG. 1 shows an embodiment of a motor-operated valve according to the present invention. Of the components and parts of the motor-operated valve shown in FIG. 1, the corresponding elements and parts of the motor-operated valve shown in FIG. Is omitted.

図１に示す電動弁Ａにおいて、弁本体２には、上下方向に延びる軸線を中心として一定の内径を有する筒状スペースを有するストレートな穴１０が形成されている。穴１０の底部１１には、弁軸３の先端部に設けられる弁体３１によって開閉（開度）が制御される弁座２６が形成されている。弁本体２の上端には穴１０が開口端１２として開いている。穴１０の開口側にはスペーサ１５が装着される。   In the motor-operated valve A shown in FIG. 1, the valve body 2 is formed with a straight hole 10 having a cylindrical space having a constant inner diameter with an axis extending in the vertical direction as the center. A valve seat 26 whose opening / closing (opening degree) is controlled by a valve body 31 provided at the tip of the valve shaft 3 is formed at the bottom 11 of the hole 10. A hole 10 is opened as an open end 12 at the upper end of the valve body 2. A spacer 15 is attached to the opening side of the hole 10.

弁軸３を弁体３１の開閉方向に案内するガイドブッシュ４は、弁本体２に対して、筒状のスペーサ１５を介して固定される。スペーサ１５は、ガイドブッシュ４が嵌合する筒状本体１６を備えた筒状スペーサである。筒状本体１６の外側端部には穴１０の開口部１２に突き当たる外周フランジ部１７を有しており、外周フランジ部１７が開口部１２に突き当たることで、スペーサ１５の弁本体２（穴１０）への装着位置が決められる。また、筒状本体１６の底部１１側の端部には、ガイドブッシュ４の端部が突き当たる内周フランジ部１８を有している。ガイドブッシュ４に案内される弁軸３は、内周フランジ部１８の中央孔を貫通して延びている。穴１０において、スペーサ１５の内周フランジ部１８よりも底部１１側には、弁室２０が形成されている。   The guide bush 4 that guides the valve shaft 3 in the opening / closing direction of the valve body 31 is fixed to the valve body 2 via a cylindrical spacer 15. The spacer 15 is a cylindrical spacer provided with a cylindrical main body 16 into which the guide bush 4 is fitted. An outer peripheral flange portion 17 that abuts against the opening 12 of the hole 10 is provided at the outer end portion of the cylindrical main body 16, and the outer peripheral flange portion 17 abuts against the opening 12, so that the valve body 2 (hole 10 ) Position is determined. Further, an inner peripheral flange portion 18 against which an end portion of the guide bush 4 abuts is provided at an end portion on the bottom portion 11 side of the cylindrical main body 16. The valve shaft 3 guided by the guide bush 4 extends through the central hole of the inner peripheral flange portion 18. In the hole 10, a valve chamber 20 is formed on the bottom 11 side of the inner peripheral flange portion 18 of the spacer 15.

ガイドブッシュ４を、当該ガイドブッシュ４を取り囲むスペーサ１５を介して弁本体２に固定することにより、弁室２０の容積を拡大することができる。即ち、弁軸３やガイドブッシュ４は従来部品を踏襲しつつ、スペーサ１５を介して弁本体２に固定することにより、弁本体２の外径を大きくすることなく弁本体２の周囲壁の薄肉化を図り、その分、弁室２０の容積を大きくすることができる。スペーサ１５は、弁本体２に圧入にて固定され、ガイドブッシュ４はスペーサ１５に対して圧入により固定される。なお、弁本体２における弁室２０については、製作精度上、鍛造ではなく切削によって形成される。しかしながら、壁部が十分均肉化しているので、精密プレス作業で製作するのも可能であり、その場合には量産性を高めることができる。   By fixing the guide bush 4 to the valve body 2 via the spacer 15 surrounding the guide bush 4, the volume of the valve chamber 20 can be increased. That is, the valve shaft 3 and the guide bush 4 follow the conventional parts and are fixed to the valve main body 2 via the spacer 15, so that the peripheral wall of the valve main body 2 is thin without increasing the outer diameter of the valve main body 2. The volume of the valve chamber 20 can be increased accordingly. The spacer 15 is fixed to the valve body 2 by press-fitting, and the guide bush 4 is fixed to the spacer 15 by press-fitting. The valve chamber 20 in the valve body 2 is formed by cutting instead of forging in terms of manufacturing accuracy. However, since the wall portion is sufficiently flattened, it can be manufactured by precision press work, and in this case, mass productivity can be improved.

弁本体２には、弁室２０に繋がって冷媒等の流体が出入する流体流入管２４と流体流出管２５とが接続されている。スペーサ１５の内周フランジ部１８の先端部は流体流入管２４のためのストッパ１９として兼用されているので、流体流入管２４を弁本体２に接続するときに、流体流入管２４の端部２４ａがストッパ１９に突き当たって位置決めされる。従来は、流体流入管２４の端部２４ａが弁本体２に接続部として形成された段部に突き当たることで流体流入管２４の位置決めを行っていたので、弁本体２に当該段部を位置精度良く形成する手間が必要であった。本実施例では、弁本体２に流体流入管２４を差し込む（その後、溶接される）ために、弁室２０に達する貫通孔１３を形成するだけで良く、スペーサ１５によって流体流入管２４の位置決めを行うことができる。   Connected to the valve body 2 are a fluid inflow pipe 24 and a fluid outflow pipe 25, which are connected to the valve chamber 20 and into which a fluid such as a refrigerant enters and exits. Since the distal end portion of the inner peripheral flange portion 18 of the spacer 15 is also used as a stopper 19 for the fluid inflow tube 24, when connecting the fluid inflow tube 24 to the valve body 2, the end 24 a of the fluid inflow tube 24 is used. Is abutted against the stopper 19 and positioned. Conventionally, since the fluid inflow pipe 24 is positioned by the end 24a of the fluid inflow pipe 24 abutting against a step formed as a connection portion on the valve body 2, the stepped portion is positioned on the valve body 2. It took time and effort to form well. In the present embodiment, in order to insert the fluid inflow pipe 24 into the valve body 2 (after that, it is welded), it is only necessary to form the through hole 13 reaching the valve chamber 20, and the spacer 15 positions the fluid inflow pipe 24. It can be carried out.

弁室２０の容積を少しでも大きく確保するために、底部１１の位置を従来のものよりも下げて、弁体３１が着座する弁座２６の位置を少し下げている。弁室２０に達する貫通孔１３を形成することに対応して、弁室２０においては流体流入管２４の端部２４ａの端縁全体が入り込んで開口しており、その分、弁室２０の容積が増大されている。   In order to ensure the capacity of the valve chamber 20 as large as possible, the position of the bottom 11 is lowered from the conventional one, and the position of the valve seat 26 on which the valve body 31 is seated is slightly lowered. Corresponding to the formation of the through hole 13 reaching the valve chamber 20, the entire edge of the end 24 a of the fluid inflow pipe 24 enters and opens in the valve chamber 20, and the volume of the valve chamber 20 is correspondingly increased. Has been increased.

流れ解析等によれば、従来の電動弁Ｂのように弁室２１の容積が小さいと、弁棒３の周りで冷媒流れの流速に偏りが生じて速度分布がいびつになる。即ち、弁棒３の周りで流速が速い領域と遅い領域が生じて、流れの速度に偏りが生じる。こうした速度分布の乱れは渦の発生、即ち、通過音の発生の原因となる。これに対して、本実施例のように、弁室２０の容積を大きくした場合には、流体流入管２４から弁室２０内に流入する冷媒流れは弁室２０内で十分に広がって、弁室２０内へ流入する際の冷媒流れの速度成分が弁体３１と弁座２６との間に形成されるオリフィスを通過する冷媒流れに及ぼす影響は少なくなる。したがって、弁棒３の周りにおいて冷媒流れに偏りがなく、また時間的にも変動が少なく安定する。流体流出管２５を通じて冷媒が流れ出る出口側での速度分布についても、軸対称となって且つ十分安定していることが判明している。その結果、冷媒通過音を低減させることができる。   According to the flow analysis or the like, when the volume of the valve chamber 21 is small as in the conventional motor-operated valve B, the flow velocity of the refrigerant flow is biased around the valve rod 3 and the speed distribution becomes distorted. That is, a region where the flow velocity is fast and a region where the flow velocity is fast are generated around the valve stem 3, and the flow velocity is biased. Such disturbance of the velocity distribution causes the generation of vortices, that is, the generation of passing sounds. On the other hand, when the volume of the valve chamber 20 is increased as in the present embodiment, the refrigerant flow flowing into the valve chamber 20 from the fluid inflow pipe 24 sufficiently spreads within the valve chamber 20, The influence of the velocity component of the refrigerant flow when flowing into the chamber 20 on the refrigerant flow passing through the orifice formed between the valve body 31 and the valve seat 26 is reduced. Therefore, there is no bias in the refrigerant flow around the valve stem 3, and there is little fluctuation over time and it is stable. It has been found that the velocity distribution on the outlet side from which the refrigerant flows out through the fluid outlet pipe 25 is also axisymmetric and sufficiently stable. As a result, the refrigerant passing sound can be reduced.

本発明による電動弁の冷媒通過音の周波数特性を示すグラフ（実線）が、従来品の場合（破線）と比較して、図２に示されている。特に、高周波域（２．５〜５ｋＨｚの周波数領域であって、エアコンの使用状態としては通常の冷房運転時に現れる周波数領域）で、従来品と比較して、冷媒通過音が効果的に低減されていることが、図２から理解される。
このように、本発明によれば、電動弁の外形サイズを大型化することなく弁室２０の容積を拡大することが図れ、冷媒通過音の軽減を図ることができる。 A graph (solid line) showing the frequency characteristics of refrigerant passing sound of the motor-operated valve according to the present invention is shown in FIG. 2 in comparison with the conventional product (broken line). In particular, in the high frequency range (frequency range of 2.5 to 5 kHz, and the frequency range that appears during normal cooling operation as the air conditioner use state), the refrigerant passing sound is effectively reduced compared to the conventional product. It can be understood from FIG.
Thus, according to the present invention, the volume of the valve chamber 20 can be increased without increasing the outer size of the motor-operated valve, and the refrigerant passing sound can be reduced.

１ 電動弁 ２ 弁本体
３ 弁軸 ４ ガイドブッシュ
１０ 穴 １１ 底部
１２ 開口端 １３ 貫通孔
１５ スペーサ １６ 筒状本体
１７ 外周フランジ部 １８ 内周フランジ部
１９ ストッパ ２０ 弁室
２４ 流体流入管 ２４ａ 端部
２５ 流体流出管 ２６ 弁座
３１ 弁体 DESCRIPTION OF SYMBOLS 1 Motorized valve 2 Valve body 3 Valve shaft 4 Guide bush 10 Hole 11 Bottom part 12 Open end 13 Through-hole 15 Spacer 16 Cylindrical main body 17 Outer peripheral flange part 18 Inner peripheral flange part 19 Stopper 20 Valve chamber 24 Fluid inflow pipe 24a End part 25 Fluid outflow pipe 26 Valve seat 31 Valve body

Claims (5)

冷媒が導入される弁室及び弁座を有する弁本体と、前記弁座に対向する弁棒と、駆動モータの回転運動を直線運動に変換して前記弁棒に伝達する送りねじ機構とを備え、前記送りねじ機構は、前記弁本体に固定されているとともに前記弁棒の移動を案内し且つねじ送りを行うねじ部を有するガイドブッシュと、前記弁棒と連結され前記モータによって回転され前記ねじ部と螺合するねじ部を有するロータとを備える電動弁において、
前記ガイドブッシュを、当該ガイドブッシュを取り囲むスペーサを介して前記弁本体に固定することにより、前記弁室の容積を拡大したことを特徴とする電動弁。 A valve body having a valve chamber and a valve seat into which refrigerant is introduced; a valve rod facing the valve seat; and a feed screw mechanism that converts the rotational motion of the drive motor into a linear motion and transmits the linear motion to the valve rod. The feed screw mechanism is fixed to the valve body and guides the movement of the valve stem and has a threaded portion for screw feed, and is connected to the valve stem and rotated by the motor to rotate the screw. In a motor-operated valve comprising a rotor having a threaded portion that is screwed with the portion
The motor-operated valve, wherein the volume of the valve chamber is expanded by fixing the guide bush to the valve body via a spacer surrounding the guide bush. 前記弁本体には、一定の内径を有し且つ開口側で前記スペーサが装着されるストレートな穴が形成されており、前記穴の前記スペーサよりも底部側に前記弁室が形成されていることを特徴とする請求項１記載の電動弁。   The valve body has a constant inner diameter and is formed with a straight hole in which the spacer is mounted on the opening side, and the valve chamber is formed on the bottom side of the spacer with respect to the spacer. The motor-operated valve according to claim 1. 前記スペーサは前記ガイドブッシュが嵌合する筒状本体を備えた筒状スペーサであり、前記筒状本体の外側端部には前記穴の開口部に突き当たる外周フランジ部を有するとともに、前記筒状本体の前記弁室側端部には前記ガイドブッシュの端部が突き当たる内周フランジ部を有していることを特徴とする請求項２記載の電動弁。   The said spacer is a cylindrical spacer provided with the cylindrical main body with which the said guide bush fits, and while the outer side edge part of the said cylindrical main body has an outer peripheral flange part which contact | abuts the opening part of the said hole, the said cylindrical main body The motor-operated valve according to claim 2, further comprising an inner circumferential flange portion against which an end portion of the guide bush abuts at an end portion of the valve chamber. 前記弁本体には、前記弁室に繋がって冷媒等の流体が出入する流体流入管と流体流出管とが接続されており、
前記スペーサは、前記弁本体に接続される前記流体流入管の端部が突き当たるストッパを兼ねていることを特徴とする請求項１〜３のいずれか一項記載の電動弁。 The valve body is connected to a fluid inflow pipe and a fluid outflow pipe through which fluid such as a refrigerant enters and exits, connected to the valve chamber,
The motor operated valve according to any one of claims 1 to 3, wherein the spacer also serves as a stopper against which an end of the fluid inflow pipe connected to the valve main body abuts. 前記弁室は、前記流体流入管の前記端部の端縁全体が入り込んで開口する広さに形成されていることを特徴とする請求項４記載の電動弁。   The motor-operated valve according to claim 4, wherein the valve chamber is formed to have a width in which an entire edge of the end portion of the fluid inflow pipe enters and opens.
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