JP2017096360A

JP2017096360A - Electric valve

Info

Publication number: JP2017096360A
Application number: JP2015227557A
Authority: JP
Inventors: 輝聖見津; Terumasa Mizu; 治高見; Osamu Takami
Original assignee: Pacific Industrial Co Ltd; Taiheiyo Kogyo KK
Current assignee: Pacific Industrial Co Ltd; Taiheiyo Kogyo KK
Priority date: 2015-11-20
Filing date: 2015-11-20
Publication date: 2017-06-01
Anticipated expiration: 2035-11-20
Also published as: JP6545088B2

Abstract

PROBLEM TO BE SOLVED: To provide an electric valve capable of downsizing a driving source.SOLUTION: In an electric valve 10, a second valve port 24 is formed at a tip end of a cylindrical first valve body 20 opening/closing a first valve port 13, and a second valve body 37 in the first valve body 20 opens/closes the second valve port 24. The first valve body 20 is equipped with an orifice 20D penetrating from a side part to the inside and outside, and while the first and second valve ports 13 and 24 are closed, fluid pressure on an upstream side of the first valve port 13 reaches the inside of a back surface room 18 of the first valve body 20 through the orifice 20D. Since an opening area of the second valve port 24 is larger than an opening area of the orifice 20D, while the first valve port 13 is closed and the second valve port 24 is opened, the inside of the back surface room 18 becomes generally the same as fluid pressure on a downstream side of the first valve port 13. Therefore, the first valve body 20 can be moved in a valve opening direction with small power, and a motor 40 as a power source can be downsized.SELECTED DRAWING: Figure 1

Description

本発明は、第１弁口を開平する第１弁体に第２弁口が形成され、その第２弁口を第２弁体で開閉する電動弁に関する。 The present invention relates to a motor-operated valve in which a second valve port is formed in a first valve body that opens the first valve port, and the second valve port is opened and closed by the second valve body.

従来、この種の電動弁として、第１弁体が一端に底壁を有する筒状をなし、その第１弁体を側方から内外に貫通する連通孔を備えると共に、第１弁体の底壁に第２弁口が貫通形成されているものが知られている。また、この電動弁では、第２弁体が駆動源から動力を受けて第１弁体内で直動し、第２弁口を開閉すると共に、第２弁体が第２弁口から離間する方向に移動する過程で、第１弁体に備えた当接部に当接して、第１弁体を開弁方向に移動する（例えば、特許文献１参照）。 Conventionally, as this type of electric valve, the first valve body has a cylindrical shape having a bottom wall at one end, and has a communication hole that penetrates the first valve body from the side to the inside and outside, and the bottom of the first valve body. There is known a wall in which a second valve port is formed so as to penetrate therethrough. In this motor-operated valve, the second valve body receives power from the drive source and moves directly in the first valve body to open and close the second valve port, and the second valve body is separated from the second valve port. In the process of moving to the first position, the first valve body is moved in the valve opening direction by contacting the contact portion provided in the first valve body (see, for example, Patent Document 1).

特開平８−２１５５４号公報（図１）JP-A-8-21554 (FIG. 1)

しかしながら、上記した従来の電動弁では、第１弁口が第１弁体によって閉じられかつ第２弁口が開いている状態で、その閉弁状態の第１弁体を開弁側に移動する際に、大きな動力を要するため、駆動源が大きくなるという問題があった。 However, in the conventional motor-operated valve described above, the first valve body in the closed state is moved to the valve opening side in a state where the first valve port is closed by the first valve body and the second valve port is open. However, since a large amount of power is required, there is a problem that the drive source becomes large.

本発明は、上記事情に鑑みてなされたもので、駆動源を従来より小さくすることが可能な電動弁の提供を目的とする。 The present invention has been made in view of the above circumstances, and an object thereof is to provide a motor-operated valve capable of making the drive source smaller than the conventional one.

上記目的を達成するためになされた請求項１の発明は、屈曲した流路（１６）を有するベース部材（１１Ｓ）と、前記流路（１６）の屈曲部（１６Ａ）の下流側を絞ってなる第１弁口（１３）と、前記屈曲部（１６Ａ）を挟んで前記第１弁口（１３）に対向した支持凹部（１７）と、一端に底壁（２０Ａ）を有する筒状をなして、前記支持凹部（１７）に直動可能に嵌合し、前記底壁（２０Ａ）側の端部で前記第１弁口（１３）を開閉する第１弁体（２０，２０Ｖ）と、前記第１弁体（２０，２０Ｖ）を閉弁側に付勢する弾性部材（２５）と、前記支持凹部（１７）の内部と前記第１弁体（２０，２０Ｖ）の内部とに跨がって形成された背面部屋（１８）と、前記第１弁体（２０，２０Ｖ）を側方から内外に貫通し、前記第１弁口（１３）より上流部分と前記背面部屋（１８）とを連通するオリフィス（２０Ｄ）と、前記第１弁体（２０，２０Ｖ）の前記底壁（２０Ａ）を貫通し、前記オリフィス（２０Ｄ）より開口面積が広い第２弁口（２４）と、前記第１弁体（２０，２０Ｖ）の内部で直動して、前記第２弁口（２４）を開閉する第２弁体（３７）と、前記第２弁体（３７）を任意の直動位置に保持可能な駆動源（４０）と、前記第１弁体（２０，２０Ｖ）と前記第２弁体（３７）とに形成され、前記第２弁口（２４）が開弁してさらに前記第２弁体（３７）が前記第２弁口（２４）から離れる側に移動する途中で互いに当接し、前記第１弁体（２０，２０Ｖ）を開弁させる動力を前記第２弁体（３７）から前記第１弁体（２０，２０Ｖ）へと伝達する弁体当接部（３８Ａ，３８Ｂ）と、を備える電動弁（１０，１０Ｖ）である。 In order to achieve the above object, the invention of claim 1 squeezes the base member (11S) having the bent flow path (16) and the downstream side of the bent portion (16A) of the flow path (16). A first valve port (13), a supporting recess (17) facing the first valve port (13) across the bent portion (16A), and a cylindrical shape having a bottom wall (20A) at one end. A first valve body (20, 20V) that fits in the support recess (17) so as to be capable of linear movement and opens and closes the first valve port (13) at the end on the bottom wall (20A) side, The elastic member (25) that biases the first valve body (20, 20V) toward the valve closing side, the inside of the support recess (17), and the inside of the first valve body (20, 20V) straddle. Through the back chamber (18) and the first valve body (20, 20V) formed from the side to the inside and outside and through the first valve port (13). An orifice (20D) communicating with the upstream portion and the back chamber (18) and the bottom wall (20A) of the first valve body (20, 20V) pass through and have an opening area larger than that of the orifice (20D). A second valve port (24), a second valve body (37) that opens and closes the second valve port (24) by directly moving inside the first valve body (20, 20V), and the second The second valve body is formed by a drive source (40) capable of holding the valve body (37) in an arbitrary linear motion position, the first valve body (20, 20V) and the second valve body (37). When the opening (24) is opened and the second valve body (37) further moves away from the second valve opening (24), the first valve body (20, 20V) is brought into contact with each other. Valve body abutting portions (38A, 3) for transmitting the power for opening the valve from the second valve body (37) to the first valve body (20, 20V) And B), it is an electric valve with a (10,10V).

請求項２の発明は、前記支持凹部（１７）の内側面と前記第１弁体（２０，２０Ｖ）の外側面の一方に設けられて他方に摺接する摺動シール（２３）が備えられている請求項１に記載の電動弁（１０，１０Ｖ）である。 The invention of claim 2 is provided with a sliding seal (23) provided on one of the inner side surface of the support recess (17) and the outer side surface of the first valve body (20, 20V) and in sliding contact with the other. The motor-operated valve (10, 10V) according to claim 1.

請求項３の発明は、前記支持凹部（１７）の内側面と前記第１弁口（１３）の内側面とが、同心かつ略同一径の円形をなし、前記第１弁体（２０）の先端部には、前記第１弁口（１３）の突入しかつ前記第１弁口（１３）の開口縁に当接するテーパ面（２０Ｔ）が備えられている請求項１又は２に記載の電動弁（１０）である。 According to a third aspect of the present invention, the inner side surface of the support recess (17) and the inner side surface of the first valve port (13) form a concentric circular shape having substantially the same diameter, and the first valve body (20) 3. The electric motor according to claim 1, wherein the distal end portion is provided with a tapered surface (20 T) that enters the first valve port (13) and contacts the opening edge of the first valve port (13). Valve (10).

請求項４の発明は、前記第１弁口（１３）の開口縁には、前記第１弁体（２０Ｖ）の直動方向に対して垂直に配された平面状の弁座（１３Ｖ）が設けられ、前記第１弁体（２０Ｖ）には、前記弁座（１３Ｖ）に当接するパッキン（３９）が備えられている請求項１又は２に記載の電動弁（１０Ｖ）である。 According to a fourth aspect of the present invention, a planar valve seat (13V) arranged perpendicular to the linear motion direction of the first valve body (20V) is provided at the opening edge of the first valve port (13). The motor-operated valve (10V) according to claim 1 or 2, wherein the first valve body (20V) is provided with a packing (39) that contacts the valve seat (13V).

［請求項１の発明］
請求項１の電動弁（１０，１０Ｖ）では、第１弁口（１３）及び第２弁口（２４）が共に閉弁した状態で、第１弁体（２０，２０Ｖ）の背面側の背面部屋（１８）と、流路（１６）における第１弁口（１３）の上流側部分とがオリフィス（２０Ｄ）を通して連通して同じ圧力になる。これにより、閉弁状態の第１弁口（１３）の上流側と下流側との間の比較的大きな差圧により、第１弁体（２０）が比較的強い力で閉弁状態に保持されることになる。これに対し、第１弁口（１３）が閉弁した状態で第２弁口（２４）がオリフィス（２０Ｄ）より大きく開くと、背面部屋（１８）の内圧が第１弁口（１３）の下流側の内圧に近づくように下がる。これにより、第１弁口（１３）が閉弁しかつ第２弁口（２４）が開弁した状態では、第１弁体（２０）が比較的弱い力で閉弁状態に保持されることになり、駆動源（４０）にて第１弁体（２０）を開弁側に移動するために必要な駆動力が小さくなる。即ち、本発明によれば、駆動源（４０）を小さくすることができる。 [Invention of Claim 1]
In the motor-operated valve (10, 10V) according to claim 1, the back surface on the back side of the first valve body (20, 20V) with both the first valve port (13) and the second valve port (24) closed. The chamber (18) and the upstream portion of the first valve port (13) in the flow path (16) communicate with each other through the orifice (20D) and have the same pressure. As a result, the first valve body (20) is held in the closed state with a relatively strong force due to the relatively large differential pressure between the upstream side and the downstream side of the closed first valve port (13). Will be. On the other hand, when the second valve port (24) opens larger than the orifice (20D) with the first valve port (13) closed, the internal pressure of the back chamber (18) is increased in the first valve port (13). Lower to approach the internal pressure on the downstream side. Thereby, in a state where the first valve port (13) is closed and the second valve port (24) is opened, the first valve body (20) is held in the closed state with a relatively weak force. Thus, the driving force required to move the first valve body (20) to the valve opening side by the driving source (40) is reduced. That is, according to the present invention, the drive source (40) can be reduced.

［請求項２の発明］
請求項２の電動弁（１０，１０Ｖ）では、支持凹部（１７）の内側面と第１弁体（２０，２０Ｖ）の外側面との間に備えた摺動シール（２３）により、オリフィス（２０Ｄ）以外から流路（１６）の流体が背面部屋（１８）に流れこむことを防ぐことができる。 [Invention of claim 2]
In the motor-operated valve (10, 10V) according to claim 2, an orifice (by a sliding seal (23) provided between the inner surface of the support recess (17) and the outer surface of the first valve body (20, 20V) is provided. 20D), it is possible to prevent the fluid in the flow path (16) from flowing into the back room (18).

［請求項３の発明］
請求項３の構成によれば、第１弁口（１３）が閉弁しかつ第２弁口（２４）が開弁した状態で、第１弁体（２０）のうち背面部屋（１８）側の受圧面を第１弁体（２０）の直動方向と直交する架空の面（以下、「軸直交面」という）に投影させた場合の投影面積と、第１弁体（２０）のうち第１弁口（１３）より下流側の受圧面の投影面積とが略同一になる。これにより、流体圧力により第１弁体（２０）が受ける軸力を小さくすることができる。 [Invention of claim 3]
According to the configuration of the third aspect, the back valve (18) side of the first valve body (20) with the first valve port (13) closed and the second valve port (24) opened. Of the first pressure element (20), and the projected area when the pressure-receiving surface of the first pressure element (20) is projected onto an imaginary surface orthogonal to the linear motion direction of the first valve element (20) The projected area of the pressure receiving surface downstream of the first valve port (13) is substantially the same. Thereby, the axial force which a 1st valve body (20) receives by fluid pressure can be made small.

［請求項４の発明］
請求項４の構成によれば、第１弁体（２０Ｖ）に備えたパッキン（３９）により第１弁体（２０Ｖ）と弁座（１３Ｖ）との衝突音を抑えることができる。また、第１弁口（１３）を急峻に閉弁状態と開弁状態とに切り替えることができる。 [Invention of claim 4]
According to the configuration of the fourth aspect, the collision sound between the first valve body (20V) and the valve seat (13V) can be suppressed by the packing (39) provided in the first valve body (20V). Further, the first valve port (13) can be sharply switched between the valve closing state and the valve opening state.

本発明の第１実施形態に係る電動弁の側断面図1 is a side sectional view of a motor operated valve according to a first embodiment of the present invention. 第１弁口及び第２弁口が閉弁した電動弁の一部拡大側断面図Partially enlarged side sectional view of a motor-operated valve with the first valve port and the second valve port closed 第１弁口が閉弁し、第２弁口が開弁した電動弁の一部拡大側断面図Partially enlarged side sectional view of a motor-operated valve with the first valve port closed and the second valve port opened 第１弁口が閉弁し、第２弁口が開弁した電動弁の一部拡大側断面図Partially enlarged side sectional view of a motor-operated valve with the first valve port closed and the second valve port opened 第１弁口及び第２弁口が開弁した電動弁の一部拡大側断面図Partially enlarged side sectional view of the motor operated valve with the first valve port and the second valve port opened 電動弁を通過する流体の流量とモータの回転量との関係を示したグラフA graph showing the relationship between the flow rate of fluid passing through the motorized valve and the amount of rotation of the motor 第２実施形態に係る電動弁の一部拡大側断面図Partially enlarged side sectional view of an electric valve according to a second embodiment

［第１実施形態］
以下、本発明の第１実施形態の電動弁１０を図１〜図６に基づいて説明する。なお、電動弁１０は、重力方向に対して任意の姿勢で使用可能であるが、以下の説明では、図１〜図６の上下方向を電動弁１０の上下方向として説明する。 [First Embodiment]
Hereinafter, the motor-operated valve 10 of 1st Embodiment of this invention is demonstrated based on FIGS. The motor-operated valve 10 can be used in any posture with respect to the direction of gravity, but in the following description, the up-and-down direction of FIGS.

図１に示すように、本実施形態の電動弁１０は、直方体状のバルブボディ１１を備えている。バルブボディ１１には、上面中央から下端寄り位置まで延びたセンター孔１２が備えられ、センター孔１２の下端寄り位置の内径が絞られて本発明に係る第１弁口１３が形成されている。また、第１弁口１３の上側開口縁が僅かに面取りされて弁座１３Ｚが形成されている。 As shown in FIG. 1, the motor-operated valve 10 of this embodiment includes a rectangular parallelepiped valve body 11. The valve body 11 is provided with a center hole 12 extending from the center of the upper surface to a position near the lower end, and an inner diameter of the position near the lower end of the center hole 12 is reduced to form the first valve port 13 according to the present invention. Further, the upper opening edge of the first valve port 13 is slightly chamfered to form a valve seat 13Z.

センター孔１２のうち第１弁口１３の上側近傍位置には、バルブボディ１１の一側面から穿孔された第１横孔１４が連絡されると共に、センター孔１２の下端部には、バルブボディ１１の他の側面から穿孔された第２横孔１５が連絡されている。そして、これら第１と第２の横孔１４，１５とセンター孔１２の一部とからクランク状に屈曲した流路１６が形成されている。なお、本実施形態では、流路１６においてクランク状となった２つの屈曲部のうち上側の屈曲部１６Ａが本発明に係る「流路の屈曲部」に相当する。 A first lateral hole 14 pierced from one side surface of the valve body 11 is connected to a position near the upper side of the first valve port 13 in the center hole 12, and a valve body 11 is connected to a lower end portion of the center hole 12. The 2nd horizontal hole 15 drilled from the other side is connected. A flow path 16 bent in a crank shape is formed from the first and second lateral holes 14 and 15 and a part of the center hole 12. In the present embodiment, of the two bent portions having a crank shape in the flow channel 16, the upper bent portion 16A corresponds to the “bent portion of the flow channel” according to the present invention.

センター孔１２の上端部には筒形ベース３０が挿入され、その筒形ベース３０の螺子部３０Ｎと、センター孔１２の上部の螺子部１２Ｎとが螺合されている。そして、バルブボディ１１と筒形ベース３０と後述するモータ４０の筒形ケース４０Ｈとから本発明に係るベース部材１１Ｓが構成されている。 A cylindrical base 30 is inserted into the upper end portion of the center hole 12, and a screw portion 30 N of the cylindrical base 30 and a screw portion 12 N at the upper portion of the center hole 12 are screwed together. And the base member 11S which concerns on this invention is comprised from the valve body 11, the cylindrical base 30, and the cylindrical case 40H of the motor 40 mentioned later.

筒形ベース３０の外周面には、Ｏリング溝３０Ａが形成され、そこに取り付けられたＯリング３０Ｌによって筒形ベース３０の外周面とセンター孔１２の内周面との間がシールされている。また、筒形ベース３０の内部には、その軸方向の中間位置に仕切蓋３１が嵌合固定され、仕切蓋３１の中心部には、異形孔３１Ａが貫通形成されている。異形孔３１Ａは、丸孔の内周面の一部を内側に張り出させて平坦面にした形状をなしている。 An O-ring groove 30A is formed on the outer peripheral surface of the cylindrical base 30, and the space between the outer peripheral surface of the cylindrical base 30 and the inner peripheral surface of the center hole 12 is sealed by an O-ring 30L attached thereto. . A partition lid 31 is fitted and fixed inside the cylindrical base 30 at an intermediate position in the axial direction, and a deformed hole 31 A is formed through the center of the partition lid 31. The odd-shaped hole 31A has a shape in which a part of the inner peripheral surface of the round hole protrudes inward to form a flat surface.

筒形ベース３０の下端面は、センター孔１２のうち第１横孔１４との連通部分より上方に位置し、筒形ベース３０の内側部分のうち仕切蓋３１より第１弁口１３側が、本発明に係る支持凹部１７になっている。その支持凹部１７の内側面は、第１弁口１３の内側面と同軸かつ同一内径の円筒面になっている。そして、支持凹部１７に、筒形の第１弁体２０が直動可能に嵌合されている。 The lower end surface of the cylindrical base 30 is positioned above the communication portion with the first lateral hole 14 in the center hole 12, and the first valve port 13 side of the inner portion of the cylindrical base 30 is closer to the first valve port 13 side. It is the support recessed part 17 which concerns on invention. The inner surface of the support recess 17 is a cylindrical surface that is coaxial with the inner surface of the first valve port 13 and has the same inner diameter. And the cylindrical 1st valve body 20 is fitted by the support recessed part 17 so that linear movement is possible.

図２に示すように、第１弁体２０は、下端有底の筒部２１の上端側に閉塞盤２２を装着してなる。筒部２１の下端部には、全体に比べて外径が大きくなった下端大径部２０Ｂが備えられ、その下端大径部２０Ｂの下端部にはテーパ面２０Ｔが形成され、上端部には段差面２０Ｓが形成されている。 As shown in FIG. 2, the 1st valve body 20 equips the upper end side of the cylinder part 21 with a lower end bottom, and mounts the obstruction board 22 in it. The lower end portion of the cylindrical portion 21 is provided with a lower end large diameter portion 20B whose outer diameter is larger than the whole, a tapered surface 20T is formed at the lower end portion of the lower end large diameter portion 20B, and the upper end portion is formed at the upper end portion. A step surface 20S is formed.

筒部２１のうち段差面２０Ｓの上側に隣接する位置には、本発明に係るオリフィス２０Ｄが軸方向と直交する方向に貫通形成されている。そのオリフィス２０Ｄは、例えば、内径均一の円形孔になっている。また、筒部２１における底壁２０Ａの中心部には、本発明に係る第２弁口２４が軸方向に貫通形成されている。第２弁口２４の下端部は、下方に向かって内径が２倍程度に拡径したテーパ部２４Ｘになっている。また、第２弁口２４の上端部には、開口縁を僅かに面取りしてなる弁座２４Ｚが形成されている。そして、第２弁口２４のうち弁座２４Ｚとテーパ部２４Ｘとの間には、均一内径の円筒部２４Ｙになっている。 An orifice 20D according to the present invention is formed through the cylindrical portion 21 at a position adjacent to the upper side of the stepped surface 20S in a direction orthogonal to the axial direction. The orifice 20D is, for example, a circular hole with a uniform inner diameter. Moreover, the 2nd valve port 24 which concerns on this invention is penetrated and formed by the axial part in the center part of 20 A of bottom walls in the cylinder part 21. As shown in FIG. The lower end portion of the second valve port 24 is a tapered portion 24X having an inner diameter that is about twice as large as the downward direction. Further, a valve seat 24Z having a slightly chamfered opening edge is formed at the upper end portion of the second valve port 24. A cylindrical portion 24Y having a uniform inner diameter is formed between the valve seat 24Z and the tapered portion 24X in the second valve port 24.

第２弁口２４の開口面積は、オリフィス２０Ｄの開口面積より広くなっている。ここで、開口面積とは、流体が通過する孔のうち流体の通過断面積が最も狭くなった部分の断面積であり、本実施形態の場合、第２弁口２４の開口面積は、円筒部２４Ｙの断面積でもある。そして、その第２弁口２４の円筒部２４Ｙの断面積は、オリフィス２０Ｄの断面積より広くなっている。 The opening area of the second valve port 24 is larger than the opening area of the orifice 20D. Here, the opening area is the cross-sectional area of the portion of the hole through which the fluid passes where the passage cross-sectional area of the fluid is the narrowest. In the present embodiment, the opening area of the second valve port 24 is the cylindrical portion. It is also the cross-sectional area of 24Y. The cross-sectional area of the cylindrical portion 24Y of the second valve port 24 is wider than the cross-sectional area of the orifice 20D.

筒部２１の上端部の内側には、内径を段付き状に拡径した内側大径部２１Ｄが形成されている。これに対し、閉塞盤２２は、円柱部２２Ｄの上端からフランジ部２２Ｅが側方に張り出した構造をなし、その円柱部２２Ｄが、外側小径部２１Ｅに圧入されて、閉塞盤２２が筒部２１に固定されている。そして、フランジ部２２Ｅの外周面が、筒部２１の下端大径部２０Ｂより上側部分の外周面と面一に配置されている。そして、筒部２１のうち下端大径部２０Ｂより上側部分と閉塞盤２２とが支持凹部１７に嵌合して第１弁体２０が筒形ベース３０に直動可能に支持されるている。また、閉塞盤２２と仕切蓋３１との間に、本発明の「弾性部材」として圧縮コイルバネ２５が収容され、その圧縮コイルバネ２５によって、第１弁体２０が直動範囲の下端側に付勢されている。そして、第１弁体２０が直動範囲の下端側に配置されて、テーパ面２０Ｔが第１弁口１３の弁座１３Ｚに当接することで第１弁口１３が閉弁状態になる。 On the inner side of the upper end portion of the cylindrical portion 21, an inner large-diameter portion 21 D whose inner diameter is increased in a stepped shape is formed. On the other hand, the closing plate 22 has a structure in which the flange portion 22E protrudes laterally from the upper end of the cylindrical portion 22D. The cylindrical portion 22D is press-fitted into the outer small-diameter portion 21E, and the closing plate 22 is the cylindrical portion 21. It is fixed to. And the outer peripheral surface of the flange part 22E is arrange | positioned flush with the outer peripheral surface of an upper part part from the lower end large diameter part 20B of the cylinder part 21. As shown in FIG. Then, the upper portion of the cylindrical portion 21 above the lower end large diameter portion 20 B and the closing plate 22 are fitted into the support recess 17, and the first valve body 20 is supported by the cylindrical base 30 so as to be capable of linear movement. In addition, a compression coil spring 25 is accommodated as an “elastic member” of the present invention between the closing board 22 and the partition lid 31, and the first valve body 20 is biased toward the lower end side of the linear motion range by the compression coil spring 25. Has been. And the 1st valve body 20 is arrange | positioned at the lower end side of the linear motion range, and the 1st valve port 13 will be in a valve closing state because the taper surface 20T contact | abuts to the valve seat 13Z of the 1st valve port 13. FIG.

筒部２１の上端面とフランジ部２２Ｅの下面との間には、摺動シール２３が挟持されている。詳細には、摺動シール２３は、筒部２１とフランジ部２２Ｅとの挟持される前は、平板形のリング状をなしている。また、フランジ部２２Ｅの下面の外縁部には、断面三角形の環状突起２２Ｆが形成され、筒部２１の上部外面には、筒部２１の外径を段付き状に縮径した外側小径部２１Ｅが形成されている。そして、摺動シール２３のうち内縁部のみが筒部２１とフランジ部２２Ｅとの間に挟持され、摺動シール２３の外縁側が環状突起２２Ｆに押圧されて外側小径部２１Ｅ側に折り曲げられた状態で、摺動シール２３が支持凹部１７の内側面に密着している。 A sliding seal 23 is sandwiched between the upper end surface of the cylindrical portion 21 and the lower surface of the flange portion 22E. Specifically, the sliding seal 23 has a flat ring shape before being sandwiched between the cylindrical portion 21 and the flange portion 22E. Further, an annular protrusion 22F having a triangular cross section is formed on the outer edge portion of the lower surface of the flange portion 22E. Is formed. Then, only the inner edge portion of the sliding seal 23 is sandwiched between the tube portion 21 and the flange portion 22E, and the outer edge side of the sliding seal 23 is pressed by the annular protrusion 22F and bent to the outer small diameter portion 21E side. In this state, the sliding seal 23 is in close contact with the inner surface of the support recess 17.

閉塞盤２２における円柱部２２Ｄの中心部の周りには、複数の連通孔２２Ａが貫通形成されている。そして、支持凹部１７の内部と第１弁体２０の内部とが連通孔２２Ａ群を介して連通して、本発明に係る背面部屋１８になっている。 A plurality of communication holes 22 A are formed through the central portion of the cylindrical portion 22 D in the closing board 22. And the inside of the support recessed part 17 and the inside of the 1st valve body 20 are connected via 22 A of communicating holes, and it is the back room 18 which concerns on this invention.

閉塞盤２２における円柱部２２Ｄの中心部には、シャフト支持孔２２Ｂが貫通形成されている。そして、そのシャフト支持孔２２Ｂとその上方の前述した異形孔３１Ａとに、図１に示した直動シャフト３２が挿通されている。直動シャフト３２は、上側から螺子部３２Ａ、異形シャフト部３２Ｂ及び円形シャフト部３２Ｃを並べて備えている。それらのうち円形シャフト部３２Ｃは、断面円形をなしてシャフト支持孔２２Ｂに直動可能に挿通されている。また、異形シャフト部３２Ｂは、丸棒の周面の一部に平坦面を形成した構造をなして、異形孔３１Ａに挿通され、これにより、直動シャフト３２が回転を規制された状態で直動するようになっている。そして、直動シャフト３２の上端の螺子部３２Ａが、モータ４０に備えたロータ４２の螺子孔４２Ｎに螺合している。 A shaft support hole 22 B is formed through the central portion of the cylindrical portion 22 D in the closing board 22. The linear motion shaft 32 shown in FIG. 1 is inserted into the shaft support hole 22B and the above-described deformed hole 31A above the shaft support hole 22B. The linear motion shaft 32 includes a screw portion 32A, a deformed shaft portion 32B, and a circular shaft portion 32C arranged from above. Among them, the circular shaft portion 32C has a circular cross section and is inserted into the shaft support hole 22B so as to be capable of linear movement. Further, the deformed shaft portion 32B has a structure in which a flat surface is formed on a part of the peripheral surface of the round bar, and is inserted into the deformed hole 31A, so that the linear motion shaft 32 is controlled in a state where the rotation is restricted. It comes to move. The screw portion 32 A at the upper end of the linear motion shaft 32 is screwed into the screw hole 42 N of the rotor 42 provided in the motor 40.

具体的には、モータ４０は、例えばステッピングモータであって、上下に延びた筒形ケース４０Ｈの外側にコイルユニット４１を嵌合固定して備える一方、筒形ケース４０Ｈの内側にロータ４２を回転可能に収容している。そして、筒形ケース４０Ｈの下端部が筒形ベース３０の上端部内側に嵌合固定されている。また、ロータ４２の下端部は、ベアリング４５Ａを介して筒形ケース４０Ｈに支持され、ロータ４２の上端部は、滑り軸受４５Ｂを介して筒形ケース４０Ｈに回転可能に支持されている。そして、ロータ４２の中心部に前述した螺子孔４２Ｎが備えられて直動シャフト３２の螺子部３２Ａと螺合している。なお、筒形ケース４０Ｈと直動シャフト３２との間には、ロータ４２の回転範囲を制限するストッパ機構４４が設けられている。 Specifically, the motor 40 is a stepping motor, for example, and includes a coil unit 41 fitted and fixed to the outside of a cylindrical case 40H that extends vertically, and a rotor 42 that rotates inside the cylindrical case 40H. Contained as possible. The lower end portion of the cylindrical case 40H is fitted and fixed to the inner side of the upper end portion of the cylindrical base 30. The lower end of the rotor 42 is supported by the cylindrical case 40H via a bearing 45A, and the upper end of the rotor 42 is rotatably supported by the cylindrical case 40H via a sliding bearing 45B. The above-described screw hole 42N is provided in the central portion of the rotor 42, and is screwed into the screw portion 32A of the linear motion shaft 32. A stopper mechanism 44 that limits the rotational range of the rotor 42 is provided between the cylindrical case 40H and the linear motion shaft 32.

直動シャフト３２の下端部には、第２弁体３７が取り付けられている。第２弁体３７は、連結スリーブ３３に弁本体３５を組み付けてなる。連結スリーブ３３は、上端有底、下端開放の円筒状をなし、その外径は、直動シャフト３２の円形シャフト部３２Ｃの外径より大きくなっている。また、連結スリーブ３３の上面中央からは、中央突部３３Ｂが突出していて、その中央突部３３Ｂが円形シャフト部３２Ｃ側の先端に穿孔された結合孔３２Ｄに圧入されている。さらには、連結スリーブ３３の上面外縁部と閉塞盤２２の下面は、本発明に係る弁体当接部３８Ａ，３８Ｂになっている。 A second valve body 37 is attached to the lower end portion of the linear motion shaft 32. The second valve body 37 is formed by assembling the valve body 35 to the connecting sleeve 33. The connection sleeve 33 has a cylindrical shape with an upper end and a bottom opening, and an outer diameter thereof is larger than an outer diameter of the circular shaft portion 32 C of the linear motion shaft 32. Further, a central protrusion 33B protrudes from the center of the upper surface of the connecting sleeve 33, and the central protrusion 33B is press-fitted into a coupling hole 32D drilled at the tip on the circular shaft portion 32C side. Furthermore, the outer edge portion of the upper surface of the connecting sleeve 33 and the lower surface of the closing board 22 are valve body contact portions 38A and 38B according to the present invention.

弁本体３５は、円柱体の上端部から側方に鍔部３５Ｆを張り出し、下端外面にテーパ面３５Ｔを備えた構造をなしている。そして、弁本体３５は、連結スリーブ３３に対して圧縮コイルバネ３４に次いで挿入され、その後に連結スリーブ３３に圧入された抜止リング３６によって抜け止めされている。そして、圧縮コイルバネ３４の弾発力によって鍔部３５Ｆが抜止リング３６に押し付けられて、弁本体３５の下端部が連結スリーブ３３から突出した状態に保持されている。 The valve main body 35 has a structure in which a flange portion 35F projects laterally from the upper end portion of the cylindrical body, and a tapered surface 35T is provided on the lower end outer surface. The valve body 35 is inserted into the connecting sleeve 33 next to the compression coil spring 34, and is then prevented from coming off by a retaining ring 36 press-fitted into the connecting sleeve 33. Then, the flange portion 35F is pressed against the retaining ring 36 by the elastic force of the compression coil spring 34, and the lower end portion of the valve body 35 is held in a state protruding from the connecting sleeve 33.

そして、第２弁体３７が直動シャフト３２と共に下方に移動すると、図１に示すようにテーパ面３５Ｔが第２弁口２４の弁座２４Ｚに当接して第２弁口２４が閉弁される。そこから第２弁体３７が上方に移動すると、図３に示すように第２弁口２４が開弁された後に、図４に示すように第２弁体３７の弁体当接部３８Ａが第１弁体２０の弁体当接部３８Ｂに当接し、更に図５に示すように第２弁体３７が上方に移動することで、第１弁体２０が上方に移動して第１弁口１３が開弁する。 When the second valve element 37 moves downward together with the linear movement shaft 32, the tapered surface 35T comes into contact with the valve seat 24Z of the second valve port 24 and the second valve port 24 is closed as shown in FIG. The When the second valve body 37 moves upward from there, after the second valve port 24 is opened as shown in FIG. 3, the valve body abutting portion 38A of the second valve body 37 is opened as shown in FIG. When the second valve element 37 moves upward as shown in FIG. 5, the first valve element 20 moves upward and contacts the valve element abutting portion 38 B of the first valve element 20. The mouth 13 opens.

本実施形態の電動弁１０の構成に関する説明は以上である。次に、電動弁１０の作用効果について説明する。電動弁１０は、第１及び第２の横孔１４，１５（図１参照）に、図示しない流体回路（例えば、エアコンの冷媒回路）のパイプが接続されて、第１横孔１４から第２横孔１５へと流す流体の流量を制御する。具体的には、直動シャフト３２が可動範囲の下端側に移動すると、図２に示すように、第１弁口１３が第１弁体２０にて閉弁されると共に、第２弁口２４が第２弁体３７により閉弁されて、電動弁１０により流体の流れが遮断される。 This is the end of the description of the configuration of the motor-operated valve 10 of the present embodiment. Next, the effect of the motor operated valve 10 will be described. In the motor-operated valve 10, pipes of a fluid circuit (not shown) (for example, a refrigerant circuit of an air conditioner) (not shown) are connected to the first and second lateral holes 14 and 15 (see FIG. 1), and the second lateral hole 14 to the second lateral hole 14 and 15 (see FIG. 1). The flow rate of the fluid flowing to the side hole 15 is controlled. Specifically, when the linear motion shaft 32 moves to the lower end side of the movable range, the first valve port 13 is closed by the first valve body 20 and the second valve port 24 as shown in FIG. Is closed by the second valve body 37 and the flow of fluid is blocked by the motor-operated valve 10.

このとき、第１弁体２０は、その直動方向と非平行な受圧面に作用する流体圧力により、閉弁側に付勢する閉弁側軸力か、開弁側に付勢する開弁側軸力を受ける。具体的には、第１及び第２の弁口１３，２４が共に閉弁した状態で、流路１６における第１弁口１３より上流側の高圧の流体圧力を受ける第１弁体２０の外面では、段差面２０Ｓの受圧により閉弁側軸力が発生する一方、テーパ面２０Ｔの受圧により開弁側軸力が発生する。ここで、段差面２０Ｓ及びテーパ面２０Ｔを、第１弁体２０の直動方向と直交する架空の軸直交面に投影させた場合の投影面積は略同一であるので（正確には、僅かに段差面２０Ｓの方が広い）、それら段差面２０Ｓによる閉弁側軸力とテーパ面２０Ｔによる開弁側軸力は概ね相殺し合う。 At this time, the first valve body 20 is opened by a valve closing side axial force that is biased toward the valve closing side or a valve opening side that is biased toward the valve opening side by the fluid pressure acting on the pressure receiving surface that is not parallel to the linear motion direction Receives side axial force. Specifically, the outer surface of the first valve body 20 that receives a high fluid pressure upstream of the first valve port 13 in the flow path 16 in a state where both the first and second valve ports 13 and 24 are closed. Then, the valve closing side axial force is generated by the pressure received by the stepped surface 20S, while the valve opening side axial force is generated by the pressure received by the tapered surface 20T. Here, the projected areas when the step surface 20S and the tapered surface 20T are projected onto an imaginary axis orthogonal surface orthogonal to the linear motion direction of the first valve body 20 are substantially the same (exactly, slightly The step closing surface 20S is wider), and the valve closing side axial force by the stepped surface 20S and the valve opening side axial force by the tapered surface 20T substantially cancel each other.

また、第１及び第２の弁口１３，２４が共に閉弁した状態では、第１弁口１３より上流側の高圧の流体圧力が、オリフィス２０Ｄを通して背面部屋１８の内部にも作用する。そして、第１弁体２０のうち背面部屋１８側で高圧の流体圧力を受ける受圧面を軸直交面に投影させた場合の投影面積は、互いに逆向きに流体圧力を受ける受圧面の面積分を相殺すると、支持凹部１７の断面積と略同一になる。また、第１弁体２０のうち第１弁口１３より下流側の低圧の流体圧力を受ける受圧面の投影面積は、第１弁口１３の断面積と略同一になる。ここで、支持凹部１７の内側面と第１弁口１３の内側面とは同一径の円筒面になっているので、第１弁体２０のうち第１弁口１３より上流側の高圧の流体圧力を受ける受圧面の投影面積と、第１弁口１３より下流側の低圧の流体圧力を受ける受圧面の投影面積とは、略同一になる。従って、第１及び第２の弁口１３，２４が共に閉弁した状態では、第１弁口１３より上流側と下流側の流体圧力との差圧を、第１弁口１３の断面積に乗じて求められる比較的高い閉弁側軸力と圧縮コイルバネ２５の弾発力とを合わせた力が第１弁体２０に作用し、第１弁口１３が強固に閉弁される。 When both the first and second valve ports 13 and 24 are closed, the high-pressure fluid pressure upstream of the first valve port 13 also acts on the inside of the back chamber 18 through the orifice 20D. The projected area when the pressure receiving surface that receives high fluid pressure on the back chamber 18 side of the first valve body 20 is projected onto the axis orthogonal plane is the area of the pressure receiving surface that receives fluid pressure in opposite directions. When offset, it becomes substantially the same as the cross-sectional area of the support recess 17. Further, the projected area of the pressure receiving surface that receives the low pressure fluid pressure downstream of the first valve port 13 in the first valve body 20 is substantially the same as the cross-sectional area of the first valve port 13. Here, since the inner surface of the support recess 17 and the inner surface of the first valve port 13 are cylindrical surfaces having the same diameter, a high-pressure fluid upstream of the first valve port 13 in the first valve body 20. The projected area of the pressure receiving surface that receives pressure and the projected area of the pressure receiving surface that receives low-pressure fluid pressure downstream from the first valve port 13 are substantially the same. Accordingly, in a state where both the first and second valve ports 13 and 24 are closed, the differential pressure between the fluid pressure upstream and downstream of the first valve port 13 is set to the cross-sectional area of the first valve port 13. A force obtained by combining the relatively high valve closing side axial force obtained by multiplication and the elastic force of the compression coil spring 25 acts on the first valve body 20, and the first valve port 13 is firmly closed.

図２に示すように第１及び第２の弁口１３，２４が共に閉弁した状態からモータ４０を一方に回転させて直動シャフト３２と共に第２弁体３７を上昇させていくと、図３に示すように第２弁口２４が徐々に開いて行き、閉弁状態の第１弁口１３より上流側の流体が、オリフィス２０Ｄと第２弁口２４とを通って第１弁口１３の下流側へと流れる。即ち、流体が電動弁１０を通過する。 As shown in FIG. 2, when the motor 40 is rotated in one direction from the state where both the first and second valve ports 13 and 24 are closed, the second valve body 37 is raised together with the linear motion shaft 32. 3, the second valve port 24 gradually opens, and the fluid upstream of the closed first valve port 13 passes through the orifice 20 D and the second valve port 24, and the first valve port 13. It flows to the downstream side. That is, the fluid passes through the motor-operated valve 10.

ここで、第２弁体３７が第２弁口２４を閉弁したときのモータ４０の回転位置をモータ４０の原点位置とすると、その原点位置からのモータ４０の回転量と、電動弁１０を通過する流体の流量との関係は、図６に示すようになる。即ち、モータ４０が原点位置から所定の回転量Ｐ１を回転して第２弁口２４の弁開度が所定値に達すると、それ以上、モータ４０を回転しても電動弁１０を通過する流体の流量が変化しない状態が続く。詳細には、第２弁体３７にて一部を閉塞された第２弁口２４の開口面積は、当初は、オリフィス２０Ｄの開口面積より狭いが、第２弁体３７が上昇していく過程で同一になる（本実施形態では、例えば、第２弁体３７の下端面が第２弁口２４の開口面から僅かに浮いたところで第２弁口２４の開口面積とオリフィス２０Ｄの開口面積とが同じになる）。これにより、一時的に、オリフィス２０Ｄを通して第１弁体２０に流れ込む流量以上の流体が第２弁口２４を通して第１弁体２０外に排出されて、当初は、流路１６のうち第１弁口１３より上流側の高圧の流体圧力と同じであった背面部屋１８内が、第１弁口１３より下流側の低圧の流体圧力と同じになる。また、第２弁体３７がさらに上昇すると、第２弁口２４の開口面積がオリフィス２０Ｄの開口面積より広くなるが、その後、第２弁口２４の開口面積がいくら広くなっても、第２弁口２４から流れ出る流体の流量は、その上流側に位置するオリフィス２０Ｄの開口面積及びオリフィス２０Ｄの前後の差圧のみによって定まる流量に維持される。 Here, when the rotation position of the motor 40 when the second valve body 37 closes the second valve port 24 is the origin position of the motor 40, the rotation amount of the motor 40 from the origin position and the motor-operated valve 10 are The relationship with the flow rate of the fluid passing through is as shown in FIG. That is, when the motor 40 rotates the predetermined rotation amount P1 from the origin position and the valve opening degree of the second valve port 24 reaches a predetermined value, the fluid that passes through the motor-operated valve 10 even if the motor 40 is rotated further. The state where the flow rate does not change continues. Specifically, the opening area of the second valve port 24 partially blocked by the second valve element 37 is initially narrower than the opening area of the orifice 20D, but the process in which the second valve element 37 rises. (In this embodiment, for example, when the lower end surface of the second valve body 37 slightly floats from the opening surface of the second valve port 24, the opening area of the second valve port 24 and the opening area of the orifice 20D) Are the same). As a result, fluid whose flow rate is higher than the flow rate flowing into the first valve body 20 through the orifice 20D is temporarily discharged out of the first valve body 20 through the second valve port 24, and initially the first valve in the flow path 16 is discharged. The inside of the back chamber 18 which was the same as the high pressure fluid pressure upstream of the port 13 becomes the same as the low pressure fluid pressure downstream of the first valve port 13. Further, when the second valve body 37 is further raised, the opening area of the second valve port 24 becomes larger than the opening area of the orifice 20D, but after that, no matter how wide the opening area of the second valve port 24 becomes, The flow rate of the fluid flowing out from the valve port 24 is maintained at a flow rate determined only by the opening area of the orifice 20D located on the upstream side and the differential pressure before and after the orifice 20D.

そして、第２弁体３７がさらに上昇して、モータ４０の原点位置から回転量が図６に示した回転量Ｐ２に達したときに、図４に示すように第２弁体３７の弁体当接部３８Ａが第１弁体２０の弁体当接部３８Ｂに当接して、第１弁体２０が第２弁体３７から開弁側軸力を受ける。このとき、背面部屋１８内と第１弁口１３より下流側との流体圧力が略同一になっていて、第１弁体２０は概ね圧縮コイルバネ２５の弾発力のみで閉弁側に付勢されているので、モータ４０は、比較的、小さい動力で第１弁体２０を開弁方向に移動することができる。すると、図５に示すように第１弁口１３が開弁して、図６の回転量Ｐ２の右側に示すように、モータ４０の回転量の増加に対して電動弁１０を通過する流体の流量の増加が大きくなり、やがて、流体の流量が一定になる。また、上記した動作と逆に第２弁体３７を移動すれば第１弁口１３、第２弁口２４の順番で閉弁される。そして、モータ４０にて第１及び第２の弁体２０，３７を任意の位置に移動することで、電動弁１０を通過する流体の流量を所望の値に制御することができる。 Then, when the second valve body 37 further rises and the rotation amount reaches the rotation amount P2 shown in FIG. 6 from the origin position of the motor 40, the valve body of the second valve body 37 as shown in FIG. The contact portion 38 A contacts the valve body contact portion 38 B of the first valve body 20, and the first valve body 20 receives the valve opening side axial force from the second valve body 37. At this time, the fluid pressures in the back chamber 18 and the downstream side of the first valve port 13 are substantially the same, and the first valve body 20 is generally biased toward the valve closing side only by the elastic force of the compression coil spring 25. Therefore, the motor 40 can move the first valve body 20 in the valve opening direction with relatively small power. Then, as shown in FIG. 5, the first valve port 13 is opened, and as shown on the right side of the rotation amount P2 in FIG. The increase in flow rate becomes large, and eventually the fluid flow rate becomes constant. Moreover, if the 2nd valve body 37 is moved contrary to above-described operation | movement, it will close in the order of the 1st valve port 13 and the 2nd valve port 24. FIG. And the flow volume of the fluid which passes the motor operated valve 10 can be controlled to a desired value by moving the 1st and 2nd valve bodies 20 and 37 to arbitrary positions with the motor 40. FIG.

上述したように本実施形態の電動弁１０では、第１及び第２の弁口１３，２４が共に閉弁した状態では、第１弁体２０が、流体の差圧と圧縮コイルバネ２５の弾発力とに基づく比較的強い力で閉弁状態に保持され、第１弁口１３が閉弁しかつ第２弁口２４が開弁した状態では、第１弁体２０が圧縮コイルバネ２５のみに基づく比較的弱い力で閉弁状態に保持される。これにより、モータ４０にて第１弁体２０を開弁側に移動するために必要な駆動力が小さくなり、駆動源であるモータ４０を小さくすることができる。また、支持凹部１７の内側面と第１弁体２０の外側面との間に摺動シール２３を備えているので、オリフィス２０Ｄ以外から流路１６の流体が背面部屋１８に流れこむことを防ぐことができる。これにより、第１弁口１３が閉弁しかつ第２弁口２４が開弁した状態では、背面部屋１８の流出入する流体の流量が、オリフィス２０Ｄの開口面積に応じた大きさで安定し（図６のグラフの水平部分）、電動弁１０の動作も安定する。 As described above, in the motor-operated valve 10 according to the present embodiment, the first valve body 20 has the fluid pressure difference and the elastic spring of the compression coil spring 25 when both the first and second valve ports 13 and 24 are closed. When the first valve port 13 is closed and the second valve port 24 is opened with the relatively strong force based on the force, the first valve body 20 is based only on the compression coil spring 25. The valve is kept closed with a relatively weak force. Thereby, the driving force required to move the first valve body 20 to the valve opening side by the motor 40 is reduced, and the motor 40 that is a driving source can be reduced. Further, since the sliding seal 23 is provided between the inner surface of the support recess 17 and the outer surface of the first valve body 20, the fluid in the flow path 16 is prevented from flowing into the back chamber 18 from other than the orifice 20D. be able to. As a result, in a state where the first valve port 13 is closed and the second valve port 24 is opened, the flow rate of the fluid flowing into and out of the back chamber 18 is stabilized at a size corresponding to the opening area of the orifice 20D. (The horizontal part of the graph of FIG. 6), the operation of the motor-operated valve 10 is also stabilized.

［第２実施形態］
本実施形態の電動弁１０Ｖは、図７に示されており、第１弁体２０Ｖにおける筒部２１Ｖの構造と、第１弁口１３の弁座１３Ｖの形状とが第１実施形態と異なる。即ち、第１弁口１３の開口縁には、第１弁体２０Ｖの直動方向に対して垂直に配された平面状の弁座１３Ｖが設けられている。また、第１弁体２０Ｖの筒部２１Ｖの下端部には、フランジ部２０Ｈが備えられ、フランジ部２０Ｈを含む第１弁体２０Ｖ全体の下面が、第１弁口１３より径が大きな円形の平坦面になっている。そして、その第１弁体２０Ｖの下面の外縁部に環状溝２０Ｇが形成されて、そこにパッキン３９が収容されている。 [Second Embodiment]
The motor-operated valve 10V of the present embodiment is shown in FIG. 7, and the structure of the cylinder portion 21V in the first valve body 20V and the shape of the valve seat 13V of the first valve port 13 are different from those of the first embodiment. That is, a planar valve seat 13V arranged perpendicular to the linear movement direction of the first valve body 20V is provided at the opening edge of the first valve port 13. Further, the lower end portion of the cylindrical portion 21V of the first valve body 20V is provided with a flange portion 20H, and the lower surface of the entire first valve body 20V including the flange portion 20H is circular with a diameter larger than that of the first valve port 13. It is a flat surface. And the annular groove 20G is formed in the outer edge part of the lower surface of the 1st valve body 20V, and the packing 39 is accommodated there.

この構成によれば、第１弁体２０Ｖのパッキン３９により第１弁体２０Ｖと弁座１３Ｖとの衝突音を抑えることができると共に、第１実施形態の第１弁体２０の構造に比べ、第１弁口１３を急峻に閉弁状態と開弁状態とに切り替えることができる。 According to this configuration, the collision noise between the first valve body 20V and the valve seat 13V can be suppressed by the packing 39 of the first valve body 20V, and compared with the structure of the first valve body 20 of the first embodiment, The first valve port 13 can be sharply switched between a valve closing state and a valve opening state.

［他の実施形態］
本発明は、前記実施形態に限定されるものではなく、例えば、以下に説明するような実施形態も本発明の技術的範囲に含まれ、さらに、下記以外にも要旨を逸脱しない範囲内で種々変更して実施することができる。 [Other Embodiments]
The present invention is not limited to the above-described embodiment. For example, the embodiments described below are also included in the technical scope of the present invention, and various other than the following can be made without departing from the scope of the invention. It can be changed and implemented.

（１）前記第１実施形態の電動弁１０には、支持凹部１７の内側面と第１弁体２０の外側面との間に摺動シール２３が備えられていたが、摺動シールを備えない構造にしてもよい。但し、摺動シールを備えない場合には、支持凹部１７の内側面と第１弁体２０の外側面との間の隙間も本発明に係る「オリフィス」の役割を果たすので、その隙間の隙間の開口面積とオリフィス２０Ｄの開口面積とを合わせた面積を、第２弁口２４の全開時の開口面積より小さくする必要がある。 (1) The motor-operated valve 10 according to the first embodiment includes the sliding seal 23 between the inner surface of the support recess 17 and the outer surface of the first valve body 20, but includes a sliding seal. The structure may be omitted. However, when a sliding seal is not provided, the gap between the inner surface of the support recess 17 and the outer surface of the first valve body 20 also plays the role of the “orifice” according to the present invention. The total area of the opening area of the orifice 20D and the opening area of the orifice 20D needs to be smaller than the opening area when the second valve port 24 is fully opened.

（２）前記第１実施形態の電動弁１０では、第１弁口１３が閉弁した状態において、第２弁体３７を第２弁口２４から離間させても電動弁１０を通過する流体の流量に変化が生じない領域があったが、そのような領域をなくしてもよい。即ち、第２弁体３７を第２弁口２４から離間させるに従って電動弁１０を通過する流体の流量に増加する間に、第２弁体３７が第１弁体２０に当接して第１弁体２０が開くようにしてもよい。 (2) In the motor-operated valve 10 of the first embodiment, the fluid passing through the motor-operated valve 10 even when the second valve body 37 is separated from the second valve port 24 in a state where the first valve port 13 is closed. Although there is a region where the flow rate does not change, such a region may be eliminated. That is, the second valve body 37 abuts against the first valve body 20 while the flow rate of the fluid passing through the motor-operated valve 10 increases as the second valve body 37 is moved away from the second valve port 24. The body 20 may be opened.

１０，１０Ｖ電動弁
１１Ｓベース部材
１３第１弁口
１３Ｚ弁座
１６流路
１６Ａ屈曲部
１７支持凹部
１８背面部屋
２０，２０Ｖ第１弁体
２０Ａ底壁
２０Ｄオリフィス
２０Ｔテーパ面
２３摺動シール
２４第２弁口
２５圧縮コイルバネ（弾性部材）
３７第２弁体
３８Ａ，３８Ｂ弁体当接部
３９パッキン
４０モータ（駆動源） 10, 10V Motorized valve 11S Base member 13 First valve port 13Z Valve seat 16 Flow path 16A Bending portion 17 Supporting recess 18 Back chamber 20, 20V First valve body 20A Bottom wall 20D Orifice 20T Taper surface 23 Sliding seal 24 Second Valve port 25 Compression coil spring (elastic member)
37 2nd valve body 38A, 38B Valve body contact part 39 Packing 40 Motor (drive source)

Claims

A base member (11S) having a bent channel (16);
A first valve port (13) formed by restricting the downstream side of the bent portion (16A) of the flow path (16);
A support recess (17) facing the first valve port (13) across the bent portion (16A);
A cylindrical shape having a bottom wall (20A) at one end is fitted into the support recess (17) so as to be directly movable, and the first valve port (13) is inserted at the end on the bottom wall (20A) side. A first valve body (20, 20V) that opens and closes;
An elastic member (25) for urging the first valve body (20, 20V) toward the valve closing side;
A back room (18) formed across the inside of the support recess (17) and the inside of the first valve body (20, 20V);
An orifice (20D) that penetrates the first valve body (20, 20V) from the side to the inside and outside and communicates the upstream portion with the back chamber (18) from the first valve port (13);
A second valve port (24) penetrating through the bottom wall (20A) of the first valve body (20, 20V) and having a larger opening area than the orifice (20D);
A second valve body (37) that moves directly inside the first valve body (20, 20V) to open and close the second valve port (24);
A drive source (40) capable of holding the second valve element (37) in an arbitrary linear motion position;
The first valve body (20, 20V) and the second valve body (37) are formed, the second valve port (24) is opened, and the second valve body (37) is further moved to the second valve body (37). During the movement away from the valve port (24), the two valve bodies (37) contact each other in the middle of moving to open the first valve body (20, 20V). 20V), a motor-operated valve (10, 10V) provided with a valve body abutting portion (38A, 38B) that transmits to the motor.

The sliding seal (23) provided in one side of the inner surface of the said support recessed part (17) and the outer surface of the said 1st valve body (20, 20V), and the other is slidably contacted. Motorized valve (10, 10V).

The inner side surface of the support recess (17) and the inner side surface of the first valve port (13) form a concentric circular shape having substantially the same diameter,
The front end portion of the first valve body (20) is provided with a tapered surface (20T) that enters the first valve port (13) and contacts the opening edge of the first valve port (13). The motor-operated valve (10) according to claim 1 or 2.

A flat valve seat (13V) arranged perpendicular to the linear movement direction of the first valve body (20V) is provided at the opening edge of the first valve port (13).
The motor-operated valve (10V) according to claim 1 or 2, wherein the first valve body (20V) is provided with a packing (39) that contacts the valve seat (13V).