JP2022115501A - flow control valve - Google Patents

flow control valve Download PDF

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JP2022115501A
JP2022115501A JP2021012119A JP2021012119A JP2022115501A JP 2022115501 A JP2022115501 A JP 2022115501A JP 2021012119 A JP2021012119 A JP 2021012119A JP 2021012119 A JP2021012119 A JP 2021012119A JP 2022115501 A JP2022115501 A JP 2022115501A
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valve body
orifice
valve
flow control
rotary
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JP7320853B2 (en
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康平 菱谷
Kohei Hishitani
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Fujikoki Corp
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Fujikoki Corp
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Priority to JP2021012119A priority Critical patent/JP7320853B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/14—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit operated by one actuating member, e.g. a handle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/10—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with two or more closure members not moving as a unit
    • F16K11/105—Three-way check or safety valves with two or more closure members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F16K15/042—Check valves with guided rigid valve members shaped as balls with a plurality of balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
    • F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/44—Mechanical actuating means
    • F16K31/53—Mechanical actuating means with toothed gearing
    • F16K31/535—Mechanical actuating means with toothed gearing for rotating valves

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

To provide a flow control valve capable of performing high-accuracy flow control while suppressing backflow of fluid.SOLUTION: A flow control valve comprises a valve body having a valve seat with a first orifice and a second orifice, and a first valve body and a second valve body held movably in the direction of approaching and separating from the valve seat, and has a rotary valve body that rotates so that contact positions between the first valve body and second valve body and the valve seat change. The rotary valve body has a first rotational position where the first valve body overlaps the first orifice and the second valve body overlaps the second orifice when viewed along a rotation axis of the rotary valve body.SELECTED DRAWING: Figure 1

Description

本発明は、流量制御弁に関する。 The present invention relates to flow control valves.

一般に、ヒートポンプ式冷暖房システム等において流路制御弁として、弁体を回転させることにより流路の切り換を行うロータリー式の流路切換弁を備えている。 2. Description of the Related Art In general, a heat pump air conditioning system or the like is provided with a rotary flow path switching valve that switches a flow path by rotating a valve body as a flow path control valve.

この種の流路切換弁としては、特許文献１に示す四方切換弁がある。特許文献１の四方切換弁は、主弁ハウジングに配在された回転弁体を有し主弁ハウジング内に高圧の冷媒を導入し、回転弁体内の流路に低圧の冷媒を導入することにより、回転弁体の弁シート面を対接する弁シート面に押し付けてシール性を確保している。 As this type of flow path switching valve, there is a four-way switching valve disclosed in Patent Document 1. The four-way switching valve of Patent Document 1 has a rotary valve body arranged in a main valve housing, and introduces high-pressure refrigerant into the main valve housing, and introduces low-pressure refrigerant into a flow path in the rotary valve body. , the valve seat surface of the rotary valve body is pressed against the opposing valve seat surface to ensure sealing performance.

特開２０１８－１９４０３２号公報JP 2018-194032 A

しかしながら、接続された２つのポート内で高圧と低圧とを交互に切り替える切換弁以外に回転弁体を用いる場合は、高圧の冷媒を弁体のシールに利用することが難しいため、閉弁時のシール性を確保する必要がある。また、閉弁状態から開弁状態まで、精度よく流量制御を行いたいという要請もある。 However, when using a rotary valve element other than a switching valve that alternately switches between high pressure and low pressure within two connected ports, it is difficult to use high-pressure refrigerant to seal the valve element. It is necessary to ensure sealing performance. There is also a demand for accurate flow rate control from the valve closed state to the valve open state.

本発明の目的は、流体の逆流を抑制しつつ、高精度な流量制御を行える流量制御弁を提供することにある。 SUMMARY OF THE INVENTION An object of the present invention is to provide a flow control valve capable of highly accurate flow control while suppressing reverse flow of fluid.

上記目的を達成するために、本発明による流量制御弁は、
第１オリフィスと第２オリフィスとを備えた弁シートを有する弁本体と、
前記弁シートに接離する方向に移動可能に保持された第１弁体および第２弁体とを備え、前記第１弁体および前記第２弁体と前記弁シートとの接触位置が変化するように回転する回転弁体と、を有し、
前記回転弁体は、前記回転弁体の回転軸に沿った方向から見て、前記第１弁体が前記第１オリフィスと重なるとともに、前記第２弁体が前記第２オリフィスと重なる第１の回転位置に回転可能であることを特徴とする。 In order to achieve the above object, the flow control valve according to the present invention
a valve body having a valve seat with a first orifice and a second orifice;
A first valve body and a second valve body are movably held in a direction of contacting and separating from the valve seat, and a contact position between the first valve body and the second valve body and the valve seat changes. and a rotating valve body that rotates like
The rotary valve body has a first configuration in which the first valve body overlaps the first orifice and the second valve body overlaps the second orifice when viewed from the direction along the rotation axis of the rotary valve body. It is characterized by being rotatable to a rotating position.

本発明によれば、流体の逆流を抑制しつつ、高精度な流量制御を行える流量制御弁を提供することができる。 ADVANTAGE OF THE INVENTION According to this invention, the flow control valve which can control a flow with high precision while suppressing a reverse flow of a fluid can be provided.

図１は、本実施の形態にかかる流量制御弁を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing a flow control valve according to this embodiment. 図２は、図１に示す流量制御弁に用いられている遊星ギヤ式減速機構を分解して示す斜視図である。FIG. 2 is an exploded perspective view of a planetary gear reduction mechanism used in the flow control valve shown in FIG. 図３は、回転弁体と弁シートとを組み合わせた状態で示す斜視図である。FIG. 3 is a perspective view showing a state in which the rotary valve body and the valve seat are combined. 図４は、回転弁体を下面側から見た斜視図である。FIG. 4 is a perspective view of the rotary valve body as viewed from below. 図５は、回転弁体と弁シートの断面一部を示す側面図であり、閉弁状態を示している。FIG. 5 is a side view showing part of the cross section of the rotary valve body and the valve seat, showing the valve closed state. 図６は、回転弁体と弁シートの断面一部を示す側面図であり、中間開度を示している。FIG. 6 is a side view showing a partial cross section of the rotary valve body and the valve seat, showing an intermediate degree of opening. 図７は、回転弁体と弁シートの断面一部を示す側面図であり、全開状態を示している。FIG. 7 is a side view showing part of the cross section of the rotary valve body and the valve seat, showing the fully open state. 図８は、最大間隔を縦軸に、回転弁体の回転角度を横軸にとって示す、開弁特性のグラフである。FIG. 8 is a graph of valve opening characteristics in which the vertical axis represents the maximum distance and the horizontal axis represents the rotation angle of the rotary valve body.

以下、図面を参照して、本発明にかかる実施形態の流量制御弁について説明する。
図１は、本実施の形態にかかる流量制御弁を示す縦断面図である。図２は、図１に示す流量制御弁に用いられている遊星ギヤ式減速機構を分解して示す斜視図であるが、理解しやすいように一部をカットして示している。なお、本明細書で上方というときは、駆動部側を意味し、下方とは弁シート側を意味するものとする。 Hereinafter, flow control valves according to embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a flow control valve according to this embodiment. FIG. 2 is an exploded perspective view of the planetary gear type reduction mechanism used in the flow control valve shown in FIG. In this specification, the term "upper" means the side of the driving part, and the term "downward" means the side of the valve seat.

（流量制御弁の構成）
流量制御弁１は、駆動部１１と、当該駆動部１１による回転駆動力が入力されて歯車減速を行う遊星ギヤ式減速機構（以下、「減速部」とする）４０と、弁シート１０と、キャン３０とを備えている。流量制御弁１の軸線をＬとする。 (Configuration of flow control valve)
The flow control valve 1 includes a driving portion 11, a planetary gear type reduction mechanism (hereinafter referred to as a “reduction portion”) 40 that performs gear reduction by inputting rotational driving force from the driving portion 11, a valve seat 10, A can 30 is provided. Let L be the axis of the flow control valve 1 .

キャン３０は、受け部材６８を介して弁シート１０に固着された気密容器であって、薄肉の有頂円筒状を有する。駆動部１１は、ステータ２と、ステータ２によって回転駆動される永久磁石型のロータ組立体８とを有している。ステータ２は、キャン３０の外周部に固定配設されボビンに巻き付けられた一対のコイル１４０が樹脂と一体にモールドされて構成された電動モータの励磁装置である。ロータ組立体８は、キャン３０の内部において回転自在に支持されている。ステータ２とロータ組立体８とにより、電動モータの一例としてのステッピングモータが構成される。 The can 30 is an airtight container fixed to the valve seat 10 via a receiving member 68, and has a thin-walled truncated cylindrical shape. The drive unit 11 has a stator 2 and a permanent magnet type rotor assembly 8 that is rotationally driven by the stator 2 . The stator 2 is an excitation device for an electric motor, which is constructed by integrally molding a pair of coils 140 fixedly disposed on the outer periphery of the can 30 and wound around a bobbin with resin. The rotor assembly 8 is rotatably supported inside the can 30 . The stator 2 and rotor assembly 8 constitute a stepping motor as an example of an electric motor.

ステータ２は、キャン３０に対して着脱自在に嵌装され、取付用金具１８０により所定位置でキャン３０に固定される。この例では、キャン３０の下端近傍に形成されたドーム部３１が取付用金具１８０に形成された穴１８２に弾性的に嵌合し、それによりステータ２がキャン３０に対して位置決めされる。ステータ２の励磁のため、コイル１４０に対し不図示のリードを介して外部の電源から給電が行われる。 The stator 2 is detachably fitted to the can 30 and fixed to the can 30 at a predetermined position by a mounting bracket 180 . In this example, the dome portion 31 formed near the lower end of the can 30 is elastically fitted into the hole 182 formed in the mounting bracket 180 , thereby positioning the stator 2 with respect to the can 30 . In order to excite the stator 2, power is supplied to the coil 140 from an external power source through leads (not shown).

弁シート１０は、略円盤状の本体１０ａと、円管部１０ｂとを同軸に連設してなる。本体１０ａの内部には、軸線Ｌに対し平行にかつ等距離で、円筒状の第１オリフィス１４と、円筒状の第２オリフィス１６が配設される。本体１０ａに、第１オリフィス１４に連通するようにして第１配管２０が接続され、また第２オリフィス１６に連通するようにして第２配管２２が接続されている。円管部１０ｂには、内外周を連通する一対の横穴１８が形成されている。 The valve seat 10 is formed by coaxially connecting a substantially disk-shaped body 10a and a circular tube portion 10b. A cylindrical first orifice 14 and a cylindrical second orifice 16 are arranged parallel to and equidistant from the axis L inside the body 10a. A first pipe 20 is connected to the main body 10 a so as to communicate with the first orifice 14 , and a second pipe 22 is connected so as to communicate with the second orifice 16 . A pair of lateral holes 18 are formed in the circular pipe portion 10b so as to communicate between the inner and outer circumferences thereof.

さらに弁シート１０の外周には、段部１３が形成され、この段部１３に受け部材６８の内周が突き当てられて嵌合している。これにより、弁シート１０とキャン３０との軸線Ｌ方向の位置決めがなされる。弁シート１０とキャン３０との間に弁室５が形成される。 Further, a stepped portion 13 is formed on the outer periphery of the valve seat 10, and the inner periphery of the receiving member 68 is abutted against and fitted to the stepped portion 13. As shown in FIG. As a result, the valve seat 10 and the can 30 are positioned in the direction of the axis L. A valve chamber 5 is formed between the valve seat 10 and the can 30 .

減速部４０は、図２に示すように、ロータ組立体８と一体の太陽ギヤ４１と、例えばプラスチックを成形加工して形成されているキャリヤ４２に回転自在に支持され且つ太陽ギヤ４１と噛み合う複数（この例では３個）の軸線方向に長い遊星ギヤ４３と、太陽ギヤと同心に配置されていて各遊星ギヤ４３の一部分（上側部分）と噛み合うリングギヤ４４と、リングギヤ４４の歯数と僅かに歯数が異なる内歯が内周に形成された（即ち、リングギヤ４４とは転位関係にある）出力ギヤ部４５ａを備えた回転弁体４５とを備えている。太陽ギヤ４１、キャリヤ４２、リングギヤ４４及び回転弁体４５は、ＰＰＳ（ポリフェニレンサルファイド樹脂）から形成されていると好ましい。 As shown in FIG. 2, the reduction section 40 is rotatably supported by a sun gear 41 integrated with the rotor assembly 8 and a carrier 42 formed by molding plastic, for example, and has a plurality of gears meshing with the sun gear 41. (three in this example) long planetary gears 43 in the axial direction, a ring gear 44 arranged concentrically with the sun gear and meshing with a part (upper part) of each planetary gear 43, and the number of teeth of the ring gear 44 and slightly A rotary valve body 45 is provided with an output gear portion 45a in which internal teeth with different numbers of teeth are formed on the inner periphery (that is, in a displaced relationship with the ring gear 44). The sun gear 41, carrier 42, ring gear 44 and rotary valve body 45 are preferably made of PPS (polyphenylene sulfide resin).

図２から明らかなように、各遊星ギヤ４３は、リングギヤ４４と噛み合うと同時に、一部分（下側部分）において、回転弁体４５の出力ギヤ部４５ａと噛み合っている。 As is clear from FIG. 2, each planetary gear 43 meshes with the ring gear 44 and at the same time, partially (lower portion) meshes with the output gear portion 45a of the rotary valve body 45. As shown in FIG.

ロータ組立体８は、磁性材料を含有するプラスチック材料（ここではＰＰＳ）によって、周壁としての筒体２０２と中央に配設される太陽ギヤ部材２０４とが一体に有頂筒状に成形されている。またロータ組立体８は、太陽ギヤ部材２０４を軸線方向に貫通するシャフト２０１(図１）によって、キャン３０内部において回転自在に支持されている。 The rotor assembly 8 is made of a plastic material containing a magnetic material (here, PPS), and a cylindrical body 202 as a peripheral wall and a sun gear member 204 disposed in the center are integrally molded into a truncated cylindrical shape. . The rotor assembly 8 is rotatably supported inside the can 30 by a shaft 201 (FIG. 1) that axially penetrates the sun gear member 204 .

図２に示すように、太陽ギヤ部材２０４の中心に植設された円筒の外周に太陽ギヤ４１が形成されている。リングギヤ４４は、例えばプラスチックを成形加工して作られたリング状のギヤである。 As shown in FIG. 2, a sun gear 41 is formed on the outer periphery of a cylinder implanted in the center of the sun gear member 204 . The ring gear 44 is a ring-shaped gear made by molding plastic, for example.

このような構成によれば、電動モータの出力回転が入力される太陽ギヤ４１が自転回転をすると、太陽ギヤ４１とリングギヤ４４とに噛み合う遊星ギヤ４３が自転しながら太陽ギヤ４１の回りを公転回転する。遊星ギヤ４３は、リングギヤ４４との関係で転位した関係にある回転弁体４５と噛み合っているので、遊星ギヤ４３のこの回転により、回転弁体４５は、転位の程度（歯数差）に応じてリングギヤ４４に対して例えば５０対１程度の相対的に非常に高い減速比で回転する。遊星ギヤ４３が転位した関係にあるリングギヤ４４と出力ギヤ部４５ａとに噛み合っている遊星ギヤ機構は、不思議遊星ギヤ機構と称されている。 According to such a configuration, when the sun gear 41 to which the output rotation of the electric motor is input rotates, the planetary gear 43 meshing with the sun gear 41 and the ring gear 44 rotates and revolves around the sun gear 41 while rotating. do. Since the planetary gear 43 meshes with the rotary valve body 45 which is in a displaced relationship with the ring gear 44, the rotation of the planetary gear 43 causes the rotary valve body 45 to move according to the degree of dislocation (difference in the number of teeth). It rotates at a relatively very high reduction ratio of, for example, about 50:1 with respect to the ring gear 44 . A planetary gear mechanism in which the planetary gear 43 is engaged with the ring gear 44 and the output gear portion 45a in a displaced relationship is called a paradox planetary gear mechanism.

キャリヤ４２は、３つの柱部４２ａを平行に上面外周に植設してなる下部円盤４２ｂと、環状のプレート４２ｃとを有し、柱部４２ａを介して下部円盤４２ｂとプレート４２ｃとが平行に固定されている。下部円盤４２ｂは、シャフト２０１が回転可能に嵌合する嵌合孔４２ｈを備える。 The carrier 42 has a lower disk 42b, which is made up of three columns 42a planted in parallel on the outer circumference of the upper surface, and an annular plate 42c. Fixed. The lower disc 42b has a fitting hole 42h into which the shaft 201 is rotatably fitted.

一方、周方向に隣接する柱部４２ａの間において、亜鉛合金から形成された遊星ギヤ４３の両端が、下部円盤４２ｂとプレート４２ｃとに対して回転自在に保持されており、これにより遊星ギヤ４３はキャリヤ４２に対して回転可能となっている。 On the other hand, between the columns 42a adjacent in the circumferential direction, both ends of the planetary gear 43 made of zinc alloy are rotatably held with respect to the lower disk 42b and the plate 42c. are rotatable with respect to the carrier 42 .

図３は、回転弁体４５と弁シート１０とを組み合わせた状態で示す斜視図であり、回転弁体４５を軸線に沿った平面で切断して示している。 FIG. 3 is a perspective view showing a state in which the rotary valve body 45 and the valve seat 10 are combined, and shows the rotary valve body 45 cut along a plane along the axis.

図１、３において、回転弁体４５は、上側が中空で下方が中実の略円筒形状を備える。具体的に回転弁体４５は、上述した出力ギヤ部４５ａと、中空円筒底面に形成された袋穴４５ｂと、上下方向に沿って平行に配置された第１連通孔４５ｃ及び第２連通孔４５ｄと、回転弁体４５の外周から第１連通孔４５ｃ及び第２連通孔４５ｄに対して、それぞれ連通するように形成された均圧孔４５ｅ、４５ｆと、下面中央に形成された小円筒部４５ｇとを有する。袋穴４５ｂには、シャフト２０１の下端が相対回転可能に嵌合する。 1 and 3, the rotary valve body 45 has a substantially cylindrical shape with a hollow upper side and a solid lower side. Specifically, the rotary valve body 45 includes the output gear portion 45a described above, a blind hole 45b formed in the bottom surface of the hollow cylinder, and a first communication hole 45c and a second communication hole 45d arranged in parallel along the vertical direction. , equalizing holes 45e and 45f formed so as to communicate with the first communication hole 45c and the second communication hole 45d from the outer periphery of the rotary valve body 45, and a small cylindrical portion 45g formed in the center of the lower surface. and The lower end of the shaft 201 is fitted in the blind hole 45b so as to be relatively rotatable.

第１連通孔４５ｃ及び第２連通孔４５ｄの下端側には、それぞれ拡径した拡径円筒部４５ｈ，４５ｉが形成されており、その内部にコイルバネ５１，５３が配置されている。図１に示すように、拡径円筒部４５ｈ，４５ｉは、弁シート１０の第１オリフィス１４、第２オリフィス１６に対して、それぞれ同軸に配置されている。コイルバネ５１がボール５５を弁シート１０に向かって付勢する第１付勢部材を構成し，コイルバネ５３がボール５７を弁シート１０に向かって付勢する第２付勢部材を構成する。 Enlarged diameter cylindrical portions 45h and 45i are formed at the lower ends of the first communication hole 45c and the second communication hole 45d, respectively, and coil springs 51 and 53 are arranged therein. As shown in FIG. 1, the enlarged diameter cylindrical portions 45h and 45i are arranged coaxially with the first orifice 14 and the second orifice 16 of the valve seat 10, respectively. The coil spring 51 constitutes a first biasing member that biases the ball 55 toward the valve seat 10 , and the coil spring 53 constitutes a second biasing member that biases the ball 57 toward the valve seat 10 .

図４は、回転弁体４５を下面側から見た斜視図である。図４に示すように、回転弁体４５には、小円筒部４５ｇの周囲において、周方向に向かうにしたがって上端側に変位する螺旋状面４５ｊが形成されている。さらに軸線Ｌに直交する平坦面４５ｋが、拡径円筒部４５ｈの周囲において螺旋状面４５ｊに接続するようにして形成されている。 FIG. 4 is a perspective view of the rotary valve body 45 as seen from the bottom side. As shown in FIG. 4, the rotary valve body 45 is formed with a spiral surface 45j that displaces upward in the circumferential direction around the small cylindrical portion 45g. Further, a flat surface 45k perpendicular to the axis L is formed around the enlarged diameter cylindrical portion 45h so as to connect to the spiral surface 45j.

図３に示すように、回転弁体４５の小円筒部４５ｇは、弁シート１０の本体１０ａの上面（軸線Ｌに直交する平面)１９に形成された係合孔１７に回転可能に嵌合している。螺旋状面４５ｊは、上面１９に対して傾斜したテーパ面を構成する。 As shown in FIG. 3, the small cylindrical portion 45g of the rotary valve body 45 is rotatably fitted in an engagement hole 17 formed in the upper surface (a plane perpendicular to the axis L) 19 of the main body 10a of the valve seat 10. ing. The spiral surface 45j constitutes a tapered surface that is inclined with respect to the upper surface 19. As shown in FIG.

回転弁体４５の平坦面４５ｋが、弁シート１０の本体１０ａの上面１９に当接した状態で、図１に示すように、拡径円筒部４５ｈのコイルバネ５１と第１オリフィス１４との間にボール５５が配置され、拡径円筒部４５ｉのコイルバネ５３と第２オリフィス１６との間にボール５７が配置される。拡径円筒部４５ｈとボール５５とは同径であり、拡径円筒部４５ｉとボール５７とは同径である。ボール５５が第１弁体を構成し、ボール５７が第２弁体を構成する。弁体としてはボールに限らず、先端に半球または円錐台などを形成した円柱でもよい。なお、弁シート１０に接離する方向に移動可能に保持された第１弁体および第２弁体をいずれもボールにすることにより、正逆両方向の流れ方向に対しても閉弁時の漏れ量を少なくできる。 With the flat surface 45k of the rotary valve body 45 in contact with the upper surface 19 of the main body 10a of the valve seat 10, as shown in FIG. A ball 55 is arranged, and a ball 57 is arranged between the coil spring 53 of the enlarged diameter cylindrical portion 45i and the second orifice 16. As shown in FIG. The enlarged diameter cylindrical portion 45h and the ball 55 have the same diameter, and the enlarged diameter cylindrical portion 45i and the ball 57 have the same diameter. The ball 55 constitutes the first valve body, and the ball 57 constitutes the second valve body. The valve body is not limited to a ball, and may be a cylinder having a hemisphere or a truncated cone at its tip. By making both the first valve body and the second valve body, which are movably held on the valve seat 10 so as to be able to move toward and away from the valve seat 10, to prevent leakage in both forward and reverse flow directions when the valve is closed. can be reduced.

図１において、弁シート１０の円管部１０ｂ内に、回転弁体４５の下端側外周が嵌合し、さらに円管部１０ｂの上端外周とリングギヤ４４の外周とが、薄肉円筒部材であるギアケース２２０により連結されている。このため、回転弁体４５と弁シート１０とは軸線Ｌ方向に離間することなく、相対回転可能となっており、相対回転によりボール５５およびボール５７と弁シート１０との接触位置が変化する。 In FIG. 1, the outer periphery of the lower end of the rotary valve body 45 is fitted in the circular tube portion 10b of the valve seat 10, and the outer periphery of the upper end of the circular tube portion 10b and the outer periphery of the ring gear 44 are formed into thin cylindrical members. They are connected by a case 220 . Therefore, the rotary valve body 45 and the valve seat 10 are relatively rotatable without being separated from each other in the direction of the axis L, and the relative rotation changes the contact positions between the balls 55 and 57 and the valve seat 10 .

（流量制御弁の動作）
図５～８を参照して、本実施形態にかかる流量制御弁１の動作を説明する。第１配管２０と第２配管２２は、冷凍サイクルに接続されているものとする。 (Operation of flow control valve)
The operation of the flow control valve 1 according to this embodiment will be described with reference to FIGS. It is assumed that the first pipe 20 and the second pipe 22 are connected to a refrigeration cycle.

（閉弁時）
まず、外部電源から給電されない状態では、ロータ組立体８の回転角度はゼロであり、図１，５に示す閉弁状態となる。なお、閉弁状態での回転弁体４５の回転位置を第１の回転位置とし、開弁状態（閉弁状態以外)での回転弁体４５の回転角度を第２の回転位置とする。第１の回転位置において、回転弁体４５の回転軸に沿った方向から見て、ボール５５が第１オリフィス１４と重なるとともに、ボール５７が第２オリフィス１６と重なる。 (When closed)
First, when no power is supplied from the external power source, the rotation angle of the rotor assembly 8 is zero and the valve is closed as shown in FIGS. The rotational position of the rotary valve element 45 in the closed state is defined as the first rotational position, and the rotational angle of the rotary valve element 45 in the open state (other than the closed state) is defined as the second rotational position. At the first rotational position, the ball 55 overlaps the first orifice 14 and the ball 57 overlaps the second orifice 16 when viewed along the rotation axis of the rotary valve body 45 .

この時、ボール５５は第１オリフィス１４の上端に位置してこれを閉止し、またボール５７は第２オリフィス１６の上端に位置してこれを閉止する。しかしながら、例えば第１配管２０側が高圧で、第２配管２２側が低圧であるとした場合、第１配管２０側の圧力がコイルバネ５１の付勢力に勝り、ボール５５を第１オリフィス１４から離間させる場合もある。 At this time, the ball 55 is positioned at the upper end of the first orifice 14 to close it, and the ball 57 is positioned at the upper end of the second orifice 16 to close it. However, if, for example, the first pipe 20 side has a high pressure and the second pipe 22 side has a low pressure, the pressure on the first pipe 20 side overcomes the biasing force of the coil spring 51 and separates the ball 55 from the first orifice 14. There is also

かかる場合、第１配管２０から第１オリフィス１４を介して弁室５内に進入した冷媒(流体)は、横穴１８及び円管部１０ｂと回転弁体４５との隙間、並びに均圧孔４５ｆを介して、第２連通孔４５ｄ内に至る。このとき、第２連通孔４５ｄ内の圧力は、ボール５７を挟んだ第２オリフィス１６内の圧力より高くなるため、ボール５７は第２オリフィス１６に向かって付勢され、これにより第１配管２０から第２配管２２に向かう冷媒の流れが阻止される。 In this case, the refrigerant (fluid) that has entered the valve chamber 5 from the first pipe 20 through the first orifice 14 passes through the lateral hole 18, the gap between the circular pipe portion 10b and the rotary valve body 45, and the pressure equalizing hole 45f. through the second communication hole 45d. At this time, the pressure in the second communication hole 45 d becomes higher than the pressure in the second orifice 16 sandwiching the ball 57 , so the ball 57 is urged toward the second orifice 16 . to the second pipe 22 is blocked.

これに対し、第２配管２２側が高圧で、第１配管２０側が低圧であるとした場合、第２配管２２側の圧力がコイルバネ５３の付勢力に勝り、ボール５７を第２オリフィス１６から離間させる場合もある。 On the other hand, if the pressure on the side of the second pipe 22 is high and the pressure on the side of the first pipe 20 is low, the pressure on the side of the second pipe 22 overcomes the biasing force of the coil spring 53 and separates the ball 57 from the second orifice 16. In some cases.

かかる場合、第２配管２２から第２オリフィス１６を介して弁室５内に進入した冷媒は、横穴１８及び円管部１０ｂと回転弁体４５との隙間、並びに均圧孔４５ｅを介して、第１連通孔４５ｃ内に至る。このとき、第１連通孔４５ｃ内の圧力は、ボール５５を挟んだ第１オリフィス１４内の圧力より高くなるため、ボール５５は第１オリフィス１４に向かって付勢され、これにより第２配管２２から第１配管２０に向かう冷媒の流れが阻止される。 In this case, the refrigerant that has entered the valve chamber 5 from the second pipe 22 through the second orifice 16 passes through the horizontal hole 18, the gap between the circular pipe portion 10b and the rotary valve body 45, and the pressure equalizing hole 45e. It reaches inside the first communication hole 45c. At this time, the pressure in the first communication hole 45 c becomes higher than the pressure in the first orifice 14 sandwiching the ball 55 , so the ball 55 is urged toward the first orifice 14 . to the first pipe 20 is blocked.

以上より明らかであるが、閉弁時において、第１配管２０と第２配管２２のいずれが高圧になった場合でも、ボール５５、５７が逆止弁となって、高圧側配管から低圧側配管に向かう冷媒の流れを阻止することができる。したがって、付勢力の弱いコイルバネ５１，５３を用いた場合でも、逆止弁の効果を発揮できるため、付勢力の強いコイルバネを用いた場合に比して各部の強度確保の必要がなく、また操作性の向上を図れる。 As is clear from the above, even if either the first pipe 20 or the second pipe 22 becomes high pressure when the valve is closed, the balls 55 and 57 function as check valves, and the pressure from the high pressure side pipe to the low pressure side pipe is reduced. can block the flow of refrigerant towards the Therefore, even when the coil springs 51 and 53 with weak biasing force are used, the effect of the check valve can be exhibited. can improve sexuality.

（開弁時）
次に、制御信号に応じて外部電源から給電が行われると、ステータ２が磁力を発生する。かかる磁力に応じた角度だけ、ロータ組立体８が回転駆動され、所定方向に回転力を発生する。かかる回転力は太陽ギヤ４１に伝達され、減速部４０を介して減速され、出力ギヤ部４５ａに伝達され、回転弁体４５が軸線Ｌ回りに回転する。 (when valve is open)
Next, when power is supplied from an external power supply according to the control signal, the stator 2 generates magnetic force. The rotor assembly 8 is rotationally driven by an angle corresponding to the magnetic force to generate rotational force in a predetermined direction. This rotational force is transmitted to the sun gear 41, decelerated through the reduction section 40, transmitted to the output gear section 45a, and the rotary valve body 45 rotates around the axis L. As shown in FIG.

すると、図６に示すように、ボール５５は第１オリフィス１４の上端から離間し、弁シート１０の上面１９へと移動する。このとき、第１オリフィス１４の上端は、回転弁体４５の螺旋状面４５ｊに対向する。また図示していないが、ボール５７も第２オリフィス１６の上端から離間し、弁シート１０の上面１９へと移動するため、第２オリフィス１６の上端も、回転弁体４５の螺旋状面４５ｊに対向する。換言すれば、回転弁体４５が第１の回転位置と異なる回転位置に回転すると、ボール５５は、第１オリフィス１４から上面１９上へと移動し、ボール５７は、第２オリフィス１６から上面１９上へと移動する。図７に、回転弁体４５が最大角度回転した全開状態を示す。 Then, as shown in FIG. 6, the ball 55 is separated from the upper end of the first orifice 14 and moves to the upper surface 19 of the valve seat 10 . At this time, the upper end of the first orifice 14 faces the spiral surface 45j of the rotary valve body 45. As shown in FIG. Although not shown, the ball 57 also moves away from the upper end of the second orifice 16 and moves to the upper surface 19 of the valve seat 10, so that the upper end of the second orifice 16 also touches the spiral surface 45j of the rotary valve body 45. opposite. In other words, when the rotary valve body 45 rotates to a rotational position different from the first rotational position, the ball 55 moves from the first orifice 14 onto the upper surface 19 and the ball 57 moves from the second orifice 16 onto the upper surface 19. move up. FIG. 7 shows a fully open state in which the rotary valve body 45 is rotated by the maximum angle.

回転弁体４５が回転すると、図６，７に示すように、弁シート１０の上面１９と螺旋状面４５ｊとの間に、回転弁体４５の回転角度に応じた隙間ができるため、この隙間を介して第１オリフィス１４と第２オリフィス１６のうち一方から他方へと冷媒が流れることとなる。 When the rotary valve body 45 rotates, as shown in FIGS. 6 and 7, a gap corresponding to the rotation angle of the rotary valve body 45 is formed between the upper surface 19 of the valve seat 10 and the spiral surface 45j. , the coolant flows from one of the first orifice 14 and the second orifice 16 to the other.

例えば第１配管２０側が高圧側で、第２配管２２側が低圧側であるとすると、第１配管２０から第１オリフィス１４を介して流量制御弁１内に進入した冷媒は、弁シート１０の上面１９と螺旋状面４５ｊとの間の隙間を通過して、横穴１８を抜け、弁室５に至る。さらに、冷媒は弁室５から、反対側の横穴１８を抜けて、弁シート１０の上面１９と螺旋状面４５ｊとの間の隙間を通過して、第２オリフィス１６を介して第２配管２２に至ることとなる。なお、第１配管２０側が低圧側で、第２配管２２側が高圧側である場合、以上とは逆の方向に冷媒が流れることとなる。 For example, assuming that the first pipe 20 side is the high pressure side and the second pipe 22 side is the low pressure side, the refrigerant that has entered the flow control valve 1 from the first pipe 20 through the first orifice 14 reaches the upper surface of the valve seat 10. It passes through the gap between 19 and the spiral surface 45j, passes through the lateral hole 18, and reaches the valve chamber 5. Further, the refrigerant flows from the valve chamber 5 through the side hole 18 on the opposite side, passes through the gap between the upper surface 19 of the valve seat 10 and the spiral surface 45j, and passes through the second orifice 16 to the second pipe 22. It will lead to When the first pipe 20 side is the low pressure side and the second pipe 22 side is the high pressure side, the refrigerant flows in the opposite direction.

ここで、第１オリフィス１４の近傍における上面１９と、回転弁体４５の螺旋状面４５ｊとの最大間隔Ｈが、第２オリフィス１６の近傍における上面１９と、回転弁体４５の螺旋状面４５ｊとの間隔よりも小さいとすると、第１オリフィス１４と第２オリフィス１６との間を流れる冷媒の量は、最大間隔Ｈの大きさにより制御されることとなる。 Here, the maximum distance H between the upper surface 19 near the first orifice 14 and the spiral surface 45j of the rotary valve body 45 is equal to the distance between the upper surface 19 near the second orifice 16 and the spiral surface 45j of the rotary valve body 45. , the amount of refrigerant flowing between the first orifice 14 and the second orifice 16 is controlled by the size of the maximum distance H.

また、第１オリフィス１４の近傍における上面１９と、回転弁体４５の螺旋状面４５ｊとの最大間隔Ｈは、回転弁体４５の回転量と、螺旋状面４５ｊの螺旋角度に応じて変化する。 Also, the maximum distance H between the upper surface 19 near the first orifice 14 and the spiral surface 45j of the rotary valve body 45 changes according to the amount of rotation of the rotary valve body 45 and the spiral angle of the spiral surface 45j. .

図８は、最大間隔Ｈを縦軸に、回転弁体４５の回転角度を横軸にとって示す、開弁特性のグラフである。本実施の形態においては、螺旋状面４５ｊの螺旋角度が一定であるため、図８に実線Ａで示すように、回転弁体４５の回転角度に従って最大間隔Ｈはリニアに変化する。 FIG. 8 is a graph of valve opening characteristics in which the vertical axis represents the maximum distance H and the horizontal axis represents the rotation angle of the rotary valve body 45 . In this embodiment, since the spiral angle of the spiral surface 45j is constant, the maximum interval H linearly changes according to the rotation angle of the rotary valve body 45, as indicated by the solid line A in FIG.

なお、回転弁体４５の回転位置に応じて、螺旋状面４５ｊの螺旋角度を変化させることで、２次曲線を描いて流量が増減する図８の一点鎖線Ｂ、あるいは所定角度から急激に流量が増大する点線Ｃで示すような開弁特性などを得ることができる。 By changing the helical angle of the helical surface 45j in accordance with the rotational position of the rotary valve body 45, the flow rate increases or decreases by drawing a quadratic curve along the dashed dotted line B in FIG. It is possible to obtain valve opening characteristics such as those indicated by the dotted line C in which .

一方、逆特性の制御信号に応じて外部電源から給電が行われると、ロータ組立体８が逆方向に回転駆動され、それにより回転弁体４５も逆方向に回転し、図６，７に示す開弁状態から、図５に示す閉弁状態へと移行する。これにより、第１オリフィス１４と第２オリフィス１６との間で冷媒の流れが遮断される。 On the other hand, when power is supplied from the external power source in response to the control signal having the opposite characteristic, the rotor assembly 8 is driven to rotate in the opposite direction, thereby rotating the rotary valve body 45 in the opposite direction as shown in FIGS. From the valve open state, the valve is shifted to the valve closed state shown in FIG. This blocks the flow of coolant between the first orifice 14 and the second orifice 16 .

本実施の形態によれば、ステッピングモータの回転運動を減速部４０を介して回転弁体４５に伝達するため、高い分解能にて精度よく回転弁体４５を回転させることができる。このため、図８に従って、冷媒の流量制御を精度よく行うことができる。また、本発明は二方弁として説明を行ったが、同様に三方弁等の多方弁にも本発明は適用できる。 According to the present embodiment, since the rotary motion of the stepping motor is transmitted to the rotary valve body 45 via the speed reducer 40, the rotary valve body 45 can be rotated with high resolution and accuracy. Therefore, according to FIG. 8, it is possible to accurately control the flow rate of the refrigerant. Moreover, although the present invention has been described as a two-way valve, the present invention can be applied to a multi-way valve such as a three-way valve as well.

１ 流量制御弁
２ ステータ
５ 弁室
８ ロータ組立体
１０ 弁シート
１４ 第１オリフィス
１６ 第２オリフィス
２０ 第１配管
２２ 第２配管
３０ キャン
４０ 遊星ギヤ式減速機構(減速部)
４５ 回転弁体

1 flow control valve 2 stator 5 valve chamber 8 rotor assembly 10 valve seat 14 first orifice 16 second orifice 20 first pipe 22 second pipe 30 can 40 planetary gear reduction mechanism (reduction part)
45 rotary valve body

Claims (7)

第１オリフィスと第２オリフィスとを備えた弁シートを有する弁本体と、
前記弁シートに接離する方向に移動可能に保持された第１弁体および第２弁体とを備え、前記第１弁体および前記第２弁体と前記弁シートとの接触位置が変化するように回転する回転弁体と、を有し、
前記回転弁体は、前記回転弁体の回転軸に沿った方向から見て、前記第１弁体が前記第１オリフィスと重なるとともに、前記第２弁体が前記第２オリフィスと重なる第１の回転位置に回転可能であることを特徴とする流量制御弁。 a valve body having a valve seat with a first orifice and a second orifice;
A first valve body and a second valve body are movably held in a direction of contacting and separating from the valve seat, and a contact position between the first valve body and the second valve body and the valve seat changes. and a rotating valve body that rotates like
The rotary valve body has a first configuration in which the first valve body overlaps the first orifice and the second valve body overlaps the second orifice when viewed from the direction along the rotation axis of the rotary valve body. A flow control valve, characterized in that it is rotatable to a rotational position. モータの回転速度を減速して前記回転弁体を回転する減速部をさらに有する請求項１の流量制御弁。 2. The flow control valve according to claim 1, further comprising a deceleration section for decelerating the rotational speed of the motor to rotate the rotary valve body. 前記弁シートは前記回転軸に直交する面に平行な平面を有し、前記回転弁体は、前記平面に対して傾斜したテーパ面を有することを特徴とする請求項１または２に記載の流量制御弁。 3. The flow rate according to claim 1, wherein the valve seat has a plane parallel to a plane orthogonal to the rotation axis, and the rotary valve body has a tapered surface inclined with respect to the plane. control valve. 前記回転弁体が前記第１の回転位置と異なる回転位置にあるときに、前記第１弁体は、前記第１オリフィスから前記平面上へと移動し、前記第２弁体は、前記第２オリフィスから前記平面上へと移動することを特徴とする請求項１～３のいずれか一項に記載の流量制御弁。 When the rotary valve body is at a rotational position different from the first rotational position, the first valve body moves from the first orifice onto the plane, and the second valve body moves from the second orifice to the plane. A flow control valve according to any one of claims 1 to 3, characterized in that it moves from an orifice onto said plane. 前記回転弁体の第１連通孔内に配置され、前記第１弁体を前記弁シートに向かって付勢する第１付勢部材と、前記回転弁体の第２連通孔内に配置され、前記第２弁体を前記弁シートに向かって付勢する第２付勢部材とを有することを特徴とする請求項１～４のいずれか一項に記載の流量制御弁。 a first biasing member arranged in the first communication hole of the rotary valve body and biasing the first valve body toward the valve seat; and a first biasing member arranged in the second communication hole of the rotary valve body, The flow control valve according to any one of claims 1 to 4, further comprising a second biasing member that biases the second valve body toward the valve seat. 前記第１弁体及び前記第２弁体はボールであることを特徴とする請求項１～５のいずれか一項に記載の流量制御弁。 The flow control valve according to any one of claims 1 to 5, wherein the first valve body and the second valve body are balls. 前記減速部は、遊星ギヤを有し、前記遊星ギヤと噛み合う出力ギヤ部が前記回転弁体と一体に形成されている請求項２に記載の流量制御弁。

3. The flow control valve according to claim 2, wherein the speed reducing portion has a planetary gear, and an output gear portion meshing with the planetary gear is formed integrally with the rotary valve body.
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62174180U (en) * 1986-04-25 1987-11-05
JPH11230386A (en) * 1998-02-12 1999-08-27 Tgk Co Ltd Four-way changeover valve
JP2005042821A (en) * 2003-07-22 2005-02-17 Nichiden Kogyo Kk Directional control valve
JP2005240909A (en) * 2004-02-26 2005-09-08 Fuji Koki Corp Rotary motor-driven valve using planetary gear mechanism
US20120204979A1 (en) * 2009-10-21 2012-08-16 Zhaokeng Pan Multi-channel stepped motor operated gas adjusting valve

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62174180U (en) * 1986-04-25 1987-11-05
JPH11230386A (en) * 1998-02-12 1999-08-27 Tgk Co Ltd Four-way changeover valve
JP2005042821A (en) * 2003-07-22 2005-02-17 Nichiden Kogyo Kk Directional control valve
JP2005240909A (en) * 2004-02-26 2005-09-08 Fuji Koki Corp Rotary motor-driven valve using planetary gear mechanism
US20120204979A1 (en) * 2009-10-21 2012-08-16 Zhaokeng Pan Multi-channel stepped motor operated gas adjusting valve

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