JP2013241982A - Rotary valve - Google Patents

Rotary valve Download PDF

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JP2013241982A
JP2013241982A JP2012115052A JP2012115052A JP2013241982A JP 2013241982 A JP2013241982 A JP 2013241982A JP 2012115052 A JP2012115052 A JP 2012115052A JP 2012115052 A JP2012115052 A JP 2012115052A JP 2013241982 A JP2013241982 A JP 2013241982A
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valve body
valve
rotary
rotary valve
upper seat
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JP6013026B2 (en
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Kenichi Mochizuki
健一 望月
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Fujikoki Corp
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Abstract

PROBLEM TO BE SOLVED: To provide a rotary valve that can maximally reduce frictional resistance (sliding resistance) between a valve body and a valve element without causing an increase in size and cost or the like, and can smoothly rotate the valve element without causing a response delay.SOLUTION: A rotary valve includes: a valve body 20 that has an upper valve seat 15, a valve element accommodating chamber 14, side ports 11, 12, and a bottom port 13; and a valve element 20 that has a rotary shaft 25 and a cylindrical part 22 having a flat top 23 and an open lower surface, and in which an opening 30 having a predetermined shape and continuously changing opening areas of the side ports 11, 12 by rotation is provided in the cylindrical part 22. Pressure equalizing holes 35, 35, etc. are formed in the top 23 of the valve element 20. A washer (an annular member) 45 formed of a resin material excellent in slippage is interposed between a lower surface 15b of the upper valve seat 15 and the top 23.

Description

本発明は、弁本体内に回転自在に収容された弁体により、弁本体に形成された少なくとも一つの側部ポートと底部ポートを開閉又は開度調整するようにされた切換弁、流量調整弁、分配弁、混合弁等として使用されるロータリー弁に関する。   The present invention relates to a switching valve, a flow control valve, which is configured to open / close or adjust the opening of at least one side port and bottom port formed in a valve body by a valve body rotatably accommodated in the valve body. The present invention relates to rotary valves used as distribution valves, mixing valves, and the like.

この種のロータリー弁の一つとして、従来、例えば、図５に示される如くのものが考えられている（下記特許文献１、２等も参照）。   As one of the rotary valves of this type, conventionally, for example, a valve as shown in FIG. 5 has been considered (see also Patent Documents 1 and 2 below).

図示例のロータリー弁１’は、基本的には、弁本体１０と、この弁本体１０内に回転自在に収容された弁体２０と、この弁体２０を回転駆動するためのステッピングモータ５０とを備えている。   The illustrated rotary valve 1 ′ basically includes a valve main body 10, a valve body 20 rotatably accommodated in the valve main body 10, and a stepping motor 50 for rotating the valve body 20. It has.

弁本体１０は、中央部に軸受穴１６が形成された上側受座１５を有し、この上側受座１５上に取付具等を介してステッピングモータ５０がボルトナット類で取り付けられている。弁本体１０は、上側受座１５の下面を天井部とする円筒状の弁体収容室１４を有し、該弁体収容室１４の周壁部に開口する側部ポート１１、１２が設けられるとともに、弁体収容室１４と同軸に開口する底部ポート１３が設けられている。側部ポート１１と側部ポート１２は、この例においては１８０度の角度間隔をあけて左右に配在され、それらには入出口を構成する継手部３１、３２が連設されている。また、底部ポート１３は継手部３３を兼ねるようになっている。   The valve body 10 has an upper receiving seat 15 in which a bearing hole 16 is formed at a central portion, and a stepping motor 50 is attached to the upper receiving seat 15 with bolts and nuts via a fixture or the like. The valve main body 10 has a cylindrical valve body housing chamber 14 having the lower surface of the upper seat 15 as a ceiling, and side ports 11 and 12 that open to the peripheral wall portion of the valve body housing chamber 14 are provided. A bottom port 13 opening coaxially with the valve body accommodating chamber 14 is provided. In this example, the side port 11 and the side port 12 are arranged on the left and right sides with an angular interval of 180 degrees, and joint portions 31 and 32 constituting the inlet / outlet are connected to them. Further, the bottom port 13 also serves as the joint portion 33.

弁体２０は、弁本体１０の弁体収容室１４内に回動可能に挿置されて回転軸線Ｏ回りに回転せしめられるようになっている。   The valve body 20 is rotatably inserted into the valve body housing chamber 14 of the valve body 10 and can be rotated around the rotation axis O.

より詳細には、弁体２０は、図４（Ｂ）に示される如くに、平坦な頭頂部２３付きで下面開口の円筒状部２２を有する樹脂成形品であって、その円筒状部（の周壁部）２２が、前記側部ポート１１、１２を閉塞するシール面部として機能するようにされ、かつ、この円筒状部２２に、側部ポート１１、１２の開口面積を弁体２０の回転に伴って連続的に変化させる所定形状（例えば、両端が半円形の長円形）の開口部３０（図５）が設けられている。この開口部３０は、弁体２０の回転角度で見て所定角度だけ開口せしめられている。図４（Ｂ）においては、開口部３０は、円筒状部２２の奥側に配置されているため図示されていない。   More specifically, as shown in FIG. 4B, the valve body 20 is a resin molded product having a flat top portion 23 and a cylindrical portion 22 having a lower surface opening. (Circumferential wall portion) 22 functions as a sealing surface portion for closing the side ports 11 and 12, and the opening area of the side ports 11 and 12 is set to the cylindrical portion 22 to rotate the valve body 20. The opening part 30 (FIG. 5) of the predetermined shape (for example, both ends semicircular oval) changed continuously is provided. The opening 30 is opened by a predetermined angle when viewed from the rotation angle of the valve body 20. In FIG. 4B, the opening 30 is not shown because it is disposed on the back side of the cylindrical portion 22.

弁体２０の頭頂部２３の上面中央には、前記軸受穴１６に回動可能に嵌挿される回転軸部２５が突設されている。この回転軸部２５の下部には、Ｏリング２９、２９が装着される、３段の鍔状部２８からなる装着溝が設けられ、その上部には、ステッピングモータの出力軸と一体回転可能に連結するためのセレーション軸部２６及び非円形断面（Ｄカット形状等）の凸部２７が設けられている。   At the center of the top surface of the top portion 23 of the valve body 20, a rotating shaft portion 25 that is rotatably inserted into the bearing hole 16 is projected. A lower part of the rotary shaft 25 is provided with a mounting groove formed of a three-stage hook-like part 28 to which O-rings 29 and 29 are attached. A serration shaft portion 26 for connection and a convex portion 27 having a non-circular cross section (D cut shape or the like) are provided.

加えて、回転軸部２５における前記セレーション軸部２６の下端と前記鍔状部２８の最上段のものとの間（前記軸受穴１６の上端面より若干上方）の部位には鍔状部２８と同径の大径部３７が形成され、この大径部３７と鍔状部２８の最上段のものとの間に環状溝３８が形成されており、この環状溝３８に、弁体２０の回転は許容するが下方への抜けを阻止する弁体係止具としてのクリップ４０が装着されている（図５参照）。   In addition, the flange portion 28 and the portion between the lower end of the serration shaft portion 26 and the uppermost portion of the flange portion 28 (slightly above the upper end surface of the bearing hole 16) in the rotary shaft portion 25 are provided. A large-diameter portion 37 having the same diameter is formed, and an annular groove 38 is formed between the large-diameter portion 37 and the uppermost portion of the bowl-shaped portion 28, and the rotation of the valve body 20 is performed in the annular groove 38. Is attached, but a clip 40 is mounted as a valve body locking tool that prevents downward slipping (see FIG. 5).

クリップ４０は、図４（Ｃ）に示される如くに、概略ＶないしＵ字状に折り曲げられた１本の弾性線材からなり、外側に開く先端案内部４１ａ、前記回転軸部２５の環状溝３８に圧接嵌合せしめられる円弧状部４１ｂを有する一対の挟持片部４１、４１と、該一対の挟持片部４１、４１を連結するとともに、それらが相互に離隔する方向に押し拡げられたとき、それらを元に戻す方向に付勢する折曲ばね部４２と、からなっている。   As shown in FIG. 4 (C), the clip 40 is made of a single elastic wire bent approximately in a V or U shape, and has a leading end guide portion 41a that opens outward, and an annular groove 38 of the rotary shaft portion 25. When the pair of sandwiching piece parts 41, 41 having the arcuate part 41b press-fitted to and the pair of sandwiching piece parts 41, 41 are coupled and expanded in the direction in which they are separated from each other, And a bending spring portion 42 for urging them in a direction to return them to their original positions.

このクリップ４０を装着するにあたっては、弁体２０の回転軸部２５を軸受穴１６に下側から貫挿した後、回転軸部２５の環状溝３８に側部ポート１１側から先端案内部４１ａ、４１ａを前にして円弧状部４１ｂ、４１ｂが前記環状溝３８に外嵌されるまで押し込む。これにより、クリップ４０は上側受座１５の上面１５ａ上に載置され、弁体２０全体がクリップ４０により回転は許容するが下方への抜けを阻止された状態で係止される。この状態では、弁体２０の頭頂部２３と上側受座１５の下面１５ｂとの間には、若干の隙間１８ｃが形成される。   In mounting the clip 40, after the rotary shaft portion 25 of the valve body 20 is inserted into the bearing hole 16 from below, the tip guide portion 41a from the side port 11 side into the annular groove 38 of the rotary shaft portion 25, 41a is pushed forward until the arc-shaped portions 41b and 41b are fitted into the annular groove 38. As a result, the clip 40 is placed on the upper surface 15a of the upper seat 15, and the entire valve body 20 is allowed to rotate by the clip 40 but is locked in a state in which it is prevented from falling downward. In this state, a slight gap 18 c is formed between the top 23 of the valve body 20 and the lower surface 15 b of the upper seat 15.

このような構成のロータリー弁１’においては、弁体２０が図５に示される如くの位置に回転せしめられて、その開口部３０が側部ポート１１を開いているときには、流体（例えば水）が側部ポート１１から底部ポート１３へと流れ、その流量は弁体２０の回転位置すなわち開口部３０による側部ポート１１の開口面積に応じたものとなる。
弁体２０の開口部３０が反対側の側部ポート１２を開いているときも同様である。
また、上記とは逆に、流体を底部ポート１３から側部ポート１１と側部ポート１２のいずれかへ選択的に流すことも可能である。 In the rotary valve 1 ′ having such a configuration, when the valve body 20 is rotated to a position as shown in FIG. 5 and the opening 30 opens the side port 11, fluid (for example, water) Flows from the side port 11 to the bottom port 13, and the flow rate thereof corresponds to the rotational position of the valve body 20, that is, the opening area of the side port 11 by the opening 30.
The same applies when the opening 30 of the valve body 20 opens the side port 12 on the opposite side.
In contrast to the above, it is also possible to selectively flow the fluid from the bottom port 13 to either the side port 11 or the side port 12.

以上は、当ロータリー弁１’を三方弁、流量調整弁、開閉弁等として使用する場合であるが、その他、開口部３０の形状を変えるなどすることにより、例えば側部ポート１１からの水と側部ポート１２からの湯との混合比率を調整する混合弁としても使用できるし、底部ポート１３からの流体を所望比率で側部ポート１１と側部ポート１２に分配する分配弁として使用することもできる。   The above is a case where the rotary valve 1 'is used as a three-way valve, a flow rate adjusting valve, an on-off valve, etc. In addition, by changing the shape of the opening 30, for example, water from the side port 11 It can also be used as a mixing valve that adjusts the mixing ratio with hot water from the side port 12 and can be used as a distribution valve that distributes the fluid from the bottom port 13 to the side port 11 and the side port 12 at a desired ratio. You can also.

特開２００３−２２２２５３号公報JP 2003-222253 A 特開２００８−２９８１６９号公報JP 2008-298169 A

前記した如くの従来のロータリー弁は、次のような改善すべき課題がある。
すなわち、弁体２０が側部ポート１１、１２を閉鎖する際の流体の漏れ量を少なくしたり、あるいは流量調整を精緻に行うためには、弁体２０の側面（円筒状部２２の側面）と弁体収容室１４との間隙をなるべく小さくする必要があり、この結果、円筒状部２２の側面と弁体収容室１４との間は事実上シールされる。 The conventional rotary valve as described above has the following problems to be improved.
That is, in order to reduce the amount of fluid leakage when the valve body 20 closes the side ports 11 and 12 or to precisely adjust the flow rate, the side surface of the valve body 20 (side surface of the cylindrical portion 22). Therefore, the gap between the side surface of the cylindrical portion 22 and the valve body storage chamber 14 is effectively sealed.

しかし、前記ロータリー弁１’では、流体が弁体２０内を流れるようになっている関係上、その流体の圧力で、弁体２０が上側受座１５側に強く押圧される。つまり、図５においては弁体２０の頭頂部２３と上側受座１５の下面１５ｂとの間に隙間１８ｃが形成されているが、流体圧力で弁体２０が上方に押し上げられて該隙間１８ｃがなくなり、この結果、頭頂部２３が弁本体１０の上側受座１５の下面１５ｂに強く押し付けられる。このように、頭頂部２３と上側受座１５の下面１５ｂとは略全域にわたって接触するのでその接触面積が大きく、大きな摩擦抵抗（摺動抵抗）が発生する。   However, in the rotary valve 1 ′, because the fluid flows in the valve body 20, the valve body 20 is strongly pressed toward the upper seat 15 by the pressure of the fluid. That is, in FIG. 5, the gap 18 c is formed between the top 23 of the valve body 20 and the lower surface 15 b of the upper seat 15, but the valve body 20 is pushed upward by the fluid pressure, and the gap 18 c is formed. As a result, the crown 23 is strongly pressed against the lower surface 15 b of the upper seat 15 of the valve body 10. Thus, since the top 23 and the lower surface 15b of the upper seat 15 are in contact with each other over almost the entire area, the contact area is large and a large frictional resistance (sliding resistance) occurs.

あるいはまた、隙間１８ｃがなくならなくても、ステッピングモータ５０の出力軸に対してその中心軸方向に強い力が加えられ、該モータ５０に対する負荷が増大する。   Alternatively, even if the gap 18c does not disappear, a strong force is applied to the output shaft of the stepping motor 50 in the center axis direction, and the load on the motor 50 increases.

このような傾向は、流体が弁体２０の下側から導入され、一旦、頭頂部２３の下面に当たってから弁体２０の側面から導出される場合、あるいは流体が弁体の２０の側面から導入されて弁体の下側へ導出される場合においても、流体圧力が高く、かつ通過流量が小さい場合には顕著である。   Such a tendency is caused when the fluid is introduced from the lower side of the valve body 20 and is once derived from the side surface of the valve body 20 after hitting the lower surface of the crown 23 or the fluid is introduced from the side surface of the valve body 20. Even in the case of being led out to the lower side of the valve body, it is remarkable when the fluid pressure is high and the passing flow rate is small.

このため、弁体に応答遅れが生じたり、弁体が円滑に回転しなくなるおそれがあり、それを避けるには、発生トルクの大きなモータ等の駆動手段が必要となり、ロータリー弁の大型化、コストアップ等を招く。   For this reason, there may be a delay in response to the valve body, or the valve body may not rotate smoothly. To avoid this, driving means such as a motor with large generated torque is required, which increases the size and cost of the rotary valve. Invite up.

かかる問題を解消するための一つの方策として、前記特許文献１の図１に符号２０で示されるように、上側受座１５と頭頂部２３との間にワッシャ類を介装することが考えられるが、それだけでは、摩擦抵抗を十分に低減することはできない。   As one measure for solving such a problem, it is considered that a washer is interposed between the upper seat 15 and the top 23 as indicated by reference numeral 20 in FIG. However, the frictional resistance cannot be sufficiently reduced by itself.

本発明は、上記課題に鑑みてなされたもので、その目的とするところは、大型化、コストアップ等を招くことなく、弁本体と弁体との間の摩擦抵抗（摺動抵抗）を可及的に低減し得て、弁体の応答遅れを生じさせることなく円滑に回転させることのできるロータリー弁を提供することにある。   The present invention has been made in view of the above problems, and its object is to enable frictional resistance (sliding resistance) between the valve body and the valve body without incurring an increase in size or cost. An object of the present invention is to provide a rotary valve that can be reduced as much as possible and can be smoothly rotated without causing a response delay of the valve body.

前記目的を達成すべく、本発明に係るロータリー弁は、上側受座、該上側受座の下面を天井部とする円筒状の弁体収容室、該弁体収容室の周壁部に開口する少なくとも一つの側部ポート、及び前記弁体収容室と同軸に開口する底部ポートを有する弁本体と、回転軸部及び該回転軸部の下側に連なる頭頂部付きで下面開口の円筒状部を有し、該円筒状部に、前記側部ポートの開口面積を回転に伴って変化させる所定形状の開口部が設けられた弁体と、を備え、前記弁体の頭頂部に少なくとも１つの均圧孔が形成されていることを特徴としている。   In order to achieve the above object, a rotary valve according to the present invention includes an upper seat, a cylindrical valve body storage chamber having a lower surface of the upper seat as a ceiling, and at least an opening in a peripheral wall portion of the valve body storage chamber. A valve body having one side port and a bottom port that opens coaxially with the valve body storage chamber, and a cylindrical portion with a bottom surface opening with a rotating shaft portion and a top portion connected to the lower side of the rotating shaft portion. And a valve body provided with an opening having a predetermined shape for changing the opening area of the side port with rotation in the cylindrical part, and at least one pressure equalization at the top of the valve body It is characterized in that a hole is formed.

前記均圧孔は、好ましくは、前記弁体の回転軸線を中心とした同一円周上に設けられる。
他の好ましい態様では、均圧孔は、横断面円形状又は横断面円弧状とすることができる。
他の好ましい態様では、前記上側受座の下面と前記頭頂部との間に環状部材が介装される。
さらに他の好ましい態様では、環状部材は滑り性の優れた材料により形成される。 The pressure equalizing holes are preferably provided on the same circumference around the rotation axis of the valve body.
In another preferred embodiment, the pressure equalizing hole may have a circular cross section or a circular arc cross section.
In another preferred embodiment, an annular member is interposed between the lower surface of the upper seat and the top of the head.
In still another preferred embodiment, the annular member is formed of a material having excellent slipperiness.

本発明に係るロータリー弁では、弁体の円筒状部内の圧力が増大しても、弁体の頭頂部に形成された均圧孔を通じて円筒状部内と弁体の頭頂部及び弁体収容室の間に形成される背圧室との均圧が行われるので、弁体の頭頂部が上側受座の下面に強く押し付けられることは緩和され、頭頂部と上側受座の下面との間の摩擦抵抗（摺動抵抗）を効果的に低減することができる。   In the rotary valve according to the present invention, even if the pressure in the cylindrical part of the valve body increases, the inside of the cylindrical part, the top part of the valve body, and the valve body storage chamber through the pressure equalization holes formed in the top part of the valve body. Since pressure equalization with the back pressure chamber formed between them is performed, it is relieved that the top of the valve body is strongly pressed against the lower surface of the upper seat, and friction between the top of the head and the lower surface of the upper seat is reduced. Resistance (sliding resistance) can be effectively reduced.

その結果、大型化、コストアップ等を招くことなく、弁本体と弁体との間の摩擦抵抗（摺動抵抗）を可及的に低減し得て、応答遅れを生じさせることなく弁体を円滑に回転させることが可能となる。   As a result, the frictional resistance (sliding resistance) between the valve body and the valve body can be reduced as much as possible without causing an increase in size and cost, and the valve body can be produced without causing a response delay. It can be rotated smoothly.

また、上記の構成に加え、上側受座の下面と弁体の頭頂部との間に環状部材が介装されることにより、上側受座の下面と弁体の頭頂部との間に積極的に背圧室とが形成され、上記の均圧が速やかに行われる。   Further, in addition to the above configuration, an annular member is interposed between the lower surface of the upper seat and the top of the valve body, so that it is positively provided between the lower surface of the upper seat and the top of the valve body. And a back pressure chamber are formed, and the pressure equalization is performed quickly.

さらに、環状部材が滑り性の良い材料により形成されることにより、弁体が上方に押し付けられても、頭頂部と上側受座の下面との間の摩擦抵抗（摺動抵抗）がさらに低減され、弁体をより一層円滑に回転させることができる。   Further, since the annular member is formed of a material having good sliding property, even if the valve body is pressed upward, the frictional resistance (sliding resistance) between the crown and the lower surface of the upper seat is further reduced. The valve body can be rotated more smoothly.

本発明に係るロータリー弁の一実施例を示す部分切欠断面図。The partial notch sectional view which shows one Example of the rotary valve which concerns on this invention. 図１に示されるロータリー弁の部分切欠斜視図（右側部ポート：開）。FIG. 2 is a partially cutaway perspective view of the rotary valve shown in FIG. 1 (right port: open). 図１に示されるロータリー弁の部分切欠斜視図（左側部ポート：開）。FIG. 2 is a partially cutaway perspective view of the rotary valve shown in FIG. 1 (left side port: open). （Ａ）図１に示される本発明例の弁体を示す斜視図、（Ｂ）図５に示される従来例の弁体を示す斜視図、（Ｃ）図１、図５に示されるクリップを示す平面図。(A) Perspective view showing the valve body of the present invention example shown in FIG. 1, (B) Perspective view showing the conventional valve body shown in FIG. 5, (C) Clip shown in FIG. 1 and FIG. FIG. 従来のロータリー弁の一例を示す部分切欠断面図。The partially notched sectional view which shows an example of the conventional rotary valve.

以下、本発明の実施形態を図面を参照しながら説明する。
図１は、本発明に係るロータリー弁の一実施例を示す部分切欠断面図である。
図示例のロータリー弁１は、前述した図５に示されるロータリー弁１’と基本構成は同じであるので、対応する部分には同じ符号を付してそれらの重複説明は省略し、以下においては相違点（本発明の特徴部分）を重点的に説明する。 Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a partially cutaway sectional view showing an embodiment of a rotary valve according to the present invention.
Since the rotary valve 1 in the illustrated example has the same basic configuration as the rotary valve 1 ′ shown in FIG. 5 described above, the corresponding parts are denoted by the same reference numerals, and a duplicate description thereof is omitted. Differences (characteristic features of the present invention) will be described mainly.

本実施例のロータリー弁１も、従来例のロータリー弁１’と同様に、弁本体１０には、上側受座１５、弁体収容室１４、側部ポート１１、１２、及び底部ポート１３が設けられ、また、弁体２０は、回転軸部２５及び該回転軸部の下側に連なり、弁体２０の回転軸線Оに垂直な平坦な面を持つ頭頂部２３付きで下面開口の円筒状部２２を有し、該円筒状部２２に、前記側部ポート１１、１２の開口面積を回転に伴って連続的に変化させる所定形状の開口部３０が設けられている。また、上側受座１５の下面１５ｂも、頭頂部２３の形状に対応するように、回転軸線Оに垂直な平面とされている。   Similarly to the conventional rotary valve 1 ′, the rotary valve 1 of the present embodiment is also provided with an upper seat 15, a valve body accommodating chamber 14, side ports 11 and 12, and a bottom port 13 in the valve body 10. In addition, the valve body 20 is connected to the rotary shaft portion 25 and the lower side of the rotary shaft portion, and has a top portion 23 having a flat surface perpendicular to the rotation axis O of the valve body 20 and a cylindrical portion having a lower surface opening. The cylindrical portion 22 is provided with an opening 30 having a predetermined shape that continuously changes the opening area of the side ports 11 and 12 with rotation. Further, the lower surface 15b of the upper seat 15 is also a plane perpendicular to the rotation axis O so as to correspond to the shape of the crown 23.

そして、図４（Ａ）に良く示されるように、弁体２０の平坦な頭頂部２３に同一寸法かつ横断面円形状の４個の均圧孔３５、３５、３５、３５が形成されている。この４個の均圧孔３５は、弁体２０の回転軸線Ｏを中心とした同一円周上に等角度（９０度）間隔で配置されている。なお、図４（Ａ）においては、開口部３０は、円筒状部２２の奥側に配置されているため図示されていない。   4A, four pressure equalizing holes 35, 35, 35, 35 having the same size and a circular cross section are formed in the flat top 23 of the valve body 20. As shown in FIG. . The four pressure equalizing holes 35 are arranged at equal angles (90 degrees) on the same circumference around the rotation axis O of the valve body 20. In FIG. 4A, the opening 30 is not shown because it is disposed on the back side of the cylindrical portion 22.

上記に加え、上側受座１５の下面１５ｂと頭頂部２３との間に、テフロン（登録商標）等の滑り性に優れたシート状又は板状の樹脂材料からなるワッシャ（環状部材）４５が弁体２０の回転軸部２５の下端に外嵌された状態で介装されている。この外嵌は、ワッシャ４５の内径部と回転軸部２５の外周部との間に多少の隙間を有するように緩く行われても良い。ワッシャ４５は円環状の部材により、あるいは矩形等の輪郭部材に円筒孔を設けることにより形成される。   In addition to the above, a washer (annular member) 45 made of a sheet-like or plate-like resin material having excellent slipperiness such as Teflon (registered trademark) is provided between the lower surface 15b of the upper seat 15 and the top 23. The body 20 is interposed in a state of being fitted on the lower end of the rotary shaft portion 25 of the body 20. This external fitting may be performed loosely so as to have a slight gap between the inner diameter portion of the washer 45 and the outer peripheral portion of the rotating shaft portion 25. The washer 45 is formed by an annular member or by providing a cylindrical hole in a contour member such as a rectangle.

この例においては、ワッシャ４５は、前記４個の均圧孔３５の一部を覆っており、４個の均圧孔３５の外周寄りの部位は常時開口している。この結果、弁体２０の頭頂部２３と弁体収容室１４の上面（上側弁座１５の下面１５ｂ）との間には、少なくともワッシャ４５の厚み分だけ、均圧孔３５に常時連通する背圧室１８が形成される。   In this example, the washer 45 covers a part of the four pressure equalizing holes 35, and a portion near the outer periphery of the four pressure equalizing holes 35 is always open. As a result, between the top 23 of the valve body 20 and the upper surface of the valve body housing chamber 14 (the lower surface 15b of the upper valve seat 15), a back that is always in communication with the pressure equalizing hole 35 at least by the thickness of the washer 45. A pressure chamber 18 is formed.

かかる構成のロータリー弁１’においては、弁体２０が図１及び図２に示される如くの位置に回転せしめられて、その開口部３０が右側部ポート１１を開いているときには、流体（例えば水）が側部ポート１１から底部ポート１３へと流れ、その流量は弁体２０の回転位置すなわち開口部３０による側部ポート１１の開口面積に応じたものとなる。   In the rotary valve 1 ′ having such a configuration, when the valve body 20 is rotated to a position as shown in FIGS. 1 and 2 and the opening 30 opens the right side port 11, fluid (for example, water) ) Flows from the side port 11 to the bottom port 13, and the flow rate corresponds to the rotational position of the valve body 20, that is, the opening area of the side port 11 by the opening 30.

また、図３に示される如くに、弁体２０の開口部３０が反対側の左側部ポート１２を開いているときも同様である。
また、上記とは逆に、流体を底部ポート１３から側部ポート１１と側部ポート１２のいずれかへ選択的に流すことも可能である。 Further, as shown in FIG. 3, the same applies when the opening 30 of the valve body 20 opens the left port 12 on the opposite side.
In contrast to the above, it is also possible to selectively flow the fluid from the bottom port 13 to either the side port 11 or the side port 12.

以上は、当ロータリー弁１を三方弁又は流量調整弁として使用する場合であるが、その他、開口部３０の形状を変えるなどすることにより、例えば側部ポート１１からの水と側部ポート１２からの湯との混合比率を調整する混合弁としても使用できるし、底部ポート１３からの流体を所望比率で側部ポート１１と側部ポート１２に分配する分配弁として使用することもできる。   The above is a case where the rotary valve 1 is used as a three-way valve or a flow rate adjusting valve. In addition, for example, by changing the shape of the opening 30, for example, It can also be used as a mixing valve that adjusts the mixing ratio with hot water or as a distribution valve that distributes the fluid from the bottom port 13 to the side port 11 and the side port 12 at a desired ratio.

上記した如くの構成とされた本実施例のロータリー弁１では、流体が弁体２０の下側から導入され、一旦、頭頂部２３の下面に当たってから弁体２０の側面から導出される場合のように、弁体２０を頭頂部２３側に強く押圧する力が作用しても、弁体２２の頭頂部２３に形成された４個の均圧孔３５を通じて円筒状部２２内と背圧室１８との均圧が速やかに行われる。   In the rotary valve 1 of the present embodiment configured as described above, the fluid is introduced from the lower side of the valve body 20, once hits the lower surface of the crown 23, and then led out from the side surface of the valve body 20. Even if a force that strongly presses the valve body 20 toward the top 23 is applied, the inside of the cylindrical portion 22 and the back pressure chamber 18 are passed through the four pressure equalizing holes 35 formed in the top 23 of the valve 22. The pressure equalization is performed promptly.

ここで、背圧室１８内に流入した流体は、さらに軸受穴１６と回転軸部２５との間に流入するため、該流体によりＯリング２９が押圧され、この結果、弁体２０は上方に多少押し上げられようとするが、上記均圧の結果、弁体２０の頭頂部２３がワッシャ４５を介して上側受座１５の下面１５ｂに強く押し付けられることは、均圧孔３５を設けない従来のロータリー弁に比較して大幅に緩和され、これらの間の摩擦抵抗（摺動抵抗）を効果的に低減することができる。   Here, since the fluid flowing into the back pressure chamber 18 further flows between the bearing hole 16 and the rotary shaft portion 25, the O-ring 29 is pressed by the fluid, and as a result, the valve body 20 is moved upward. As a result of the pressure equalization, the top 23 of the valve body 20 is strongly pressed against the lower surface 15b of the upper seat 15 via the washer 45. As a result, the pressure equalization hole 35 is not provided. Compared to the rotary valve, the pressure is greatly relaxed, and the frictional resistance (sliding resistance) between them can be effectively reduced.

流体が弁体２０の側面から導入されて弁体２０の下側へ導出される場合であっても、流体圧力が比較的高くかつ通過流量が小さいときにおいては、やはり弁体２０を頭頂部２３側に強く押圧する力が作用するが、この場合においても同様に、頭頂部２３が上側受座１５の下面１５ｂに強く押し付けられることは緩和される。   Even when the fluid is introduced from the side surface of the valve body 20 and led out to the lower side of the valve body 20, when the fluid pressure is relatively high and the passing flow rate is small, the valve body 20 is again moved to the top 23. Although the force which presses strongly to the side acts, also in this case, it is relieve | moderated that the top part 23 is strongly pressed on the lower surface 15b of the upper seat 15 similarly.

したがって、弁体２０より閉塞される側部ポート１１又は１２からの流体の漏洩を極力防止すべく、円筒状部２２の表面（側面）と弁体収容室１４との間の隙間をなるべく小さくして、事実上、これらの間をシールしても、当該ロータリー弁１の大型化、コストアップ等を招くことなく、弁本体１０と弁体２０との間の摩擦抵抗（摺動抵抗）を可及的に低減し得て、応答遅れを生じさせることなく円滑に弁体を回転させることが可能となる。   Therefore, the gap between the surface (side surface) of the cylindrical portion 22 and the valve body accommodating chamber 14 is made as small as possible in order to prevent leakage of fluid from the side port 11 or 12 closed by the valve body 20 as much as possible. In fact, even if these spaces are sealed, the friction resistance (sliding resistance) between the valve body 10 and the valve body 20 can be increased without causing an increase in the size and cost of the rotary valve 1. It can be reduced as much as possible, and the valve body can be smoothly rotated without causing a response delay.

また、上側受座１５の下面１５ｂと弁体２０の頭頂部２３との間に滑り性に優れた樹脂材料からなるワッシャ４５が介装されているので、頭頂部２３と上側受座１５の下面１５ｂとの間の摩擦抵抗（摺動抵抗）がさらに低減され、弁体をより一層円滑に回転させることができる。   In addition, since a washer 45 made of a resin material having excellent slipperiness is interposed between the lower surface 15 b of the upper seat 15 and the top 23 of the valve body 20, the lower surface of the top 23 and the upper seat 15. The frictional resistance (sliding resistance) with respect to 15b is further reduced, and the valve body can be rotated more smoothly.

さて、均圧孔３５の寸法、形状、個数、配列状態等は上記実施例のものに限られないことは勿論であり、また、ワッシャ４５等の他の部分も、本発明の要旨を逸脱しない範囲で上記実施例に種々の改変を施すことができる。   Needless to say, the size, shape, number, arrangement state, etc. of the pressure equalizing holes 35 are not limited to those of the above embodiment, and other parts such as the washer 45 do not depart from the gist of the present invention. Various modifications can be made to the above-described embodiment within a range.

すなわち、上述の説明においては、同一寸法かつ横断面円形状の均圧孔３５が４個、弁体２０の回転軸線Ｏを中心とした同一円周上に等角度間隔で配置されるものとしたが、本発明は特にこれのみに限定されることはなく、均圧孔の個数は１個以上であれば良い。   That is, in the above description, four equalizing holes 35 having the same size and a circular cross section are arranged at equal angular intervals on the same circumference around the rotation axis O of the valve body 20. However, the present invention is not particularly limited to this, and the number of pressure equalizing holes may be one or more.

また、均圧孔を複数設ける場合においては、その設置角度は弁体２０の回転軸線Ｏを中心とした同一円周上に不等角度間隔で配置されても良い。   When a plurality of pressure equalizing holes are provided, the installation angles may be arranged at unequal angular intervals on the same circumference around the rotation axis O of the valve body 20.

さらに、均圧孔を複数設ける場合においては、均圧孔は、同一円周上に配置されなくても良い。   Furthermore, in the case where a plurality of pressure equalizing holes are provided, the pressure equalizing holes may not be arranged on the same circumference.

さらにまた、均圧孔は図４（Ａ）に示されたような横断面円形状である必要はなく、横断面円弧状に形成されても良い。この場合、均圧孔は、弁体２０の回転軸線Оを中心とした横断面円弧状に形成されることもできる。   Furthermore, the pressure equalizing holes do not have to have a circular cross section as shown in FIG. 4A, and may be formed in a circular arc shape. In this case, the pressure equalizing hole can be formed in an arc shape with a cross section centering on the rotation axis O of the valve body 20.

さらにまた、図１の事例では、均圧孔３５は、その一部がワッシャ４５に覆われるように頭頂部２３に設けられているが、ワッシャ４５にその一部が覆われないように（すなわち閉鎖されないように）頭頂部２３に設けられても良い。   Furthermore, in the example of FIG. 1, the pressure equalizing hole 35 is provided in the top 23 so that a part thereof is covered by the washer 45, but the part is not covered by the washer 45 (that is, It may be provided on the top 23 (so as not to be closed).

さらにまた、ワッシャ４５を設けることにより、弁体２０の頭頂部２３と上側受座１５の下面１５ｂとの間に背圧室１８が積極的に形成されるが、このワッシャ４５は特に設けられなくても良い。すなわち、ワッシャ４５を設けない場合には、頭頂部２３と下面１５ｂとが接触した状態で弁体２０内に流体が流入することがあるが、この場合においても、該弁体２０内に流入する流体がその圧力により均圧孔３５を介して、頭頂部２３と下面１５ｂとの間に流入し、事実上、背圧室に相当する流体空間が形成される。   Furthermore, by providing the washer 45, the back pressure chamber 18 is positively formed between the top 23 of the valve body 20 and the lower surface 15b of the upper seat 15, but this washer 45 is not particularly provided. May be. That is, when the washer 45 is not provided, the fluid may flow into the valve body 20 in a state where the top 23 and the lower surface 15b are in contact with each other, but in this case also, the fluid flows into the valve body 20. The fluid flows into the space between the top 23 and the lower surface 15b through the pressure equalizing hole 35 due to the pressure, and a fluid space corresponding to a back pressure chamber is formed in practice.

さらにまた、弁体２０の頭頂部２３は、弁体２０の回転軸線Оに垂直な平坦な面であり、上側受座１５の下面１５ｂも同様に、回転軸線Оに垂直な平面とされるものとして説明したが、本発明はこれのみに限定されることはなく、頭頂部２３を円錐形、半球状形等とし、上側受座１５の下面１５ｂも頭頂部２３の形状に対応するような円錐形、半球状形等としても良いことは当然である。   Furthermore, the top portion 23 of the valve body 20 is a flat surface perpendicular to the rotational axis O of the valve body 20, and the lower surface 15b of the upper seat 15 is similarly a plane perpendicular to the rotational axis O. However, the present invention is not limited to this, and the crown 23 has a conical shape, a hemispherical shape, etc., and the lower surface 15b of the upper seat 15 has a cone corresponding to the shape of the crown 23. Of course, it may be a shape, a hemispherical shape, or the like.

さらにまた、当該ロータリー弁は、弁本体の側面に設けられた２つの側部ポート（側部ポート１１及び１２）を備えるものとして説明したが、本発明はこれのみに限定されることはなく、側部ポートは３つ以上でも良く、また側部ポートを１つとして当該ロータリー弁を開閉弁等として利用しても良いことは当然である。   Furthermore, although the rotary valve has been described as including two side ports (side ports 11 and 12) provided on the side surface of the valve body, the present invention is not limited to this, Naturally, the number of side ports may be three or more, and the rotary valve may be used as an on-off valve or the like with one side port.

１ ロータリー弁
１０ 弁本体
１１ 側部ポート
１２ 側部ポート
１３ 底部ポート
１５ 上側受座
１６ 軸受穴
１８ 背圧室
２０ 弁体
２２ 円筒状部
２３ 頭頂部
２５ 回転軸部
３０ 開口部
３５ 均圧孔
４５ ワッシャ（環状部材）
５０ ステッピングモータ DESCRIPTION OF SYMBOLS 1 Rotary valve 10 Valve body 11 Side port 12 Side port 13 Bottom port 15 Upper seat 16 Bearing hole 18 Back pressure chamber 20 Valve body 22 Cylindrical part 23 Head top part 25 Rotary shaft part 30 Opening part 35 Pressure equalizing hole 45 Washer (annular member)
50 Stepping motor

Claims (6)

上側受座、該上側受座の下面を天井部とする円筒状の弁体収容室、該弁体収容室の周壁部に開口する少なくとも一つの側部ポート、及び前記弁体収容室と同軸に開口する底部ポートを有する弁本体と、回転軸部及び該回転軸部の下側に連なる頭頂部付きで下面開口の円筒状部を有し、該円筒状部に、前記側部ポートの開口面積を回転に伴って変化させる所定形状の開口部が設けられた弁体と、を備えたロータリー弁であって、
前記弁体の頭頂部に少なくとも１つの均圧孔が形成されていることを特徴とするロータリー弁。 An upper seat, a cylindrical valve body storage chamber having a ceiling on the lower surface of the upper seat, at least one side port opened in the peripheral wall of the valve body storage chamber, and coaxial with the valve body storage chamber A valve body having an open bottom port; a rotating shaft portion; a top portion connected to a lower side of the rotating shaft portion; and a cylindrical portion having a lower surface opening; and the opening area of the side port in the cylindrical portion A valve body provided with an opening of a predetermined shape that changes with rotation,
A rotary valve characterized in that at least one pressure equalizing hole is formed in the top of the valve body. 前記均圧孔は、前記弁体の回転軸線を中心とした同一円周上に設けられていることを特徴とする請求項１に記載のロータリー弁。   2. The rotary valve according to claim 1, wherein the pressure equalizing holes are provided on the same circumference around a rotation axis of the valve body. 前記均圧孔は、横断面円形状であることを特徴とする請求項１又は２記載のロータリー弁。   The rotary valve according to claim 1 or 2, wherein the pressure equalizing hole has a circular cross section. 前記均圧孔は、横断面円弧状であることを特徴とする請求項１又は２記載のロータリー弁。   The rotary valve according to claim 1, wherein the pressure equalizing hole has an arc shape in cross section. 前記上側受座の下面と前記頭頂部との間に環状部材が介装されていることを特徴とする請求項１ないし４のいずれかに記載のロータリー弁。   The rotary valve according to any one of claims 1 to 4, wherein an annular member is interposed between the lower surface of the upper seat and the top of the head. 前記環状部材は、滑り性に優れた材料より成ることを特徴とする請求項５記載のロータリー弁。   The rotary valve according to claim 5, wherein the annular member is made of a material excellent in slipperiness.
JP2012115052A 2012-05-18 2012-05-18 Rotary valve Active JP6013026B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016023704A (en) * 2014-07-18 2016-02-08 株式会社不二工機 Flow channel switching valve
JP2020070826A (en) * 2018-10-30 2020-05-07 株式会社テージーケー Control valve

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS646567A (en) * 1987-06-29 1989-01-11 Toto Ltd Selector valve
JP2003222253A (en) * 2002-01-25 2003-08-08 Mitsubishi Electric Corp Mixing valve and water heater using this mixing valve
JP2009228764A (en) * 2008-03-21 2009-10-08 Fuji Koki Corp Flow regulating valve
JP2012036925A (en) * 2010-08-04 2012-02-23 Eagle Industry Co Ltd Two-way valve
JP2012047192A (en) * 2010-08-24 2012-03-08 Eagle Industry Co Ltd Three-way valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS646567A (en) * 1987-06-29 1989-01-11 Toto Ltd Selector valve
JP2003222253A (en) * 2002-01-25 2003-08-08 Mitsubishi Electric Corp Mixing valve and water heater using this mixing valve
JP2009228764A (en) * 2008-03-21 2009-10-08 Fuji Koki Corp Flow regulating valve
JP2012036925A (en) * 2010-08-04 2012-02-23 Eagle Industry Co Ltd Two-way valve
JP2012047192A (en) * 2010-08-24 2012-03-08 Eagle Industry Co Ltd Three-way valve

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016023704A (en) * 2014-07-18 2016-02-08 株式会社不二工機 Flow channel switching valve
JP2020070826A (en) * 2018-10-30 2020-05-07 株式会社テージーケー Control valve
JP7116486B2 (en) 2018-10-30 2022-08-10 株式会社テージーケー control valve

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