JP2008232290A - Needle valve, and refrigerating cycle device having the same - Google Patents

Needle valve, and refrigerating cycle device having the same Download PDF

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Publication number
JP2008232290A
JP2008232290A JP2007073408A JP2007073408A JP2008232290A JP 2008232290 A JP2008232290 A JP 2008232290A JP 2007073408 A JP2007073408 A JP 2007073408A JP 2007073408 A JP2007073408 A JP 2007073408A JP 2008232290 A JP2008232290 A JP 2008232290A
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Prior art keywords
valve
valve port
port
needle
fluid
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JP2007073408A
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Japanese (ja)
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Soichiro Tomioka
総一郎 富岡
Takashi Hirakawa
尚 平川
Seiichi Nakano
誠一 中野
Daiki Nakagawa
大樹 中川
Yutaka Kaneko
裕 金子
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Priority to JP2007073408A priority Critical patent/JP2008232290A/en
Priority to CNA200810080692XA priority patent/CN101270817A/en
Publication of JP2008232290A publication Critical patent/JP2008232290A/en
Pending legal-status Critical Current

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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
    • F16K47/00—Means in valves for absorbing fluid energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F25B41/35—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators by rotary motors, e.g. by stepping motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Lift Valve (AREA)
  • Details Of Valves (AREA)
  • Electrically Driven Valve-Operating Means (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a needle valve capable of preventing generation of noise of high frequency of the audible wavelength band. <P>SOLUTION: The needle valve 1 comprises a valve casing 10 and a valve element 30. A valve port 24 having a valve port 12 is provided on the valve casing 10. The valve element 30 is attached/detached to/from the valve port 24 to change the opening. A flow rate adjusting part 33 of the valve element 30 is tapered. The ratio L1/D is 3.5-5.0, when the angle θ is over 0° and ≤45°, where θ denotes the angle formed by the flow rate adjusting part 33 at the section passing through the axis of the valve element 30, D denotes the inside diameter of the valve port 12, and L1 denotes the overall length of the valve port 12 in the axial direction. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、冷凍サイクル装置などに用いられて、内側に冷媒などの流体を通すニードル弁及びこのニードル弁を有する冷凍サイクル装置に関する。   The present invention relates to a needle valve that is used in a refrigeration cycle apparatus or the like and allows a fluid such as a refrigerant to pass inside, and a refrigeration cycle apparatus having the needle valve.

冷凍サイクル装置などの流体を循環させる各種の装置では、各種のニードル弁（例えば、特許文献１参照）が用いられている。特許文献１に示されたニードル弁は、内側に冷媒などの流体を通す流路が形成された弁箱と、弁箱の弁座に接離自在に設けられた針状の弁体と、前記弁体を前記弁座に接離させる駆動部とを備えている。   Various devices such as a refrigeration cycle device that circulate fluid use various needle valves (see, for example, Patent Document 1). The needle valve shown in Patent Document 1 includes a valve box in which a flow path for passing a fluid such as a refrigerant is formed inside, a needle-like valve body that is provided so as to be able to contact and separate from a valve seat of the valve box, And a drive unit for bringing the valve body into contact with and separating from the valve seat.

前述した特許文献１に示されたニードル弁は、駆動部のステータのコイルなどに電流が印加させることで、当該駆動部のロータを回転させることで、弁体を弁座に設けられた弁口に接離させて、開度を変更して、前述した流体の流量を適宜変更する。
特開２００６−９７９４７号公報 The above-described needle valve disclosed in Patent Document 1 has a valve port provided on a valve seat by rotating a rotor of the driving unit by applying a current to a coil of a stator of the driving unit. The flow rate of the fluid is changed as appropriate by changing the opening degree.
JP 2006-97947 A

前述した特許文献１に示されたニードル弁は、弁箱に形成された流路内を流れる流体の流れは、弁口の内縁ではがれて、弁口の内面からはがれたまま即ち所謂乱流のまま弁口内を通って、当該ニードル弁の下流に導かれる。このように、従来のニードル弁では、弁口口内を流体が所謂乱流のまま流れるので、特に、開度の少ない即ち弁口と弁体とが近接した状態で、弁箱内を流体が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音即ち高い音が生じてしまう。   In the needle valve shown in Patent Document 1 described above, the flow of the fluid flowing in the flow path formed in the valve box is peeled off at the inner edge of the valve port and is separated from the inner surface of the valve port, that is, so-called turbulent flow. It passes through the valve port and is guided downstream of the needle valve. As described above, in the conventional needle valve, the fluid flows in the so-called turbulent flow in the valve opening, so that the fluid flows in the valve box particularly when the opening is small, that is, the valve opening and the valve body are close to each other. In this case, a high-frequency sound in an audible wavelength band of 1 kHz to 20 kHz, that is, a high sound is generated.

したがって、本発明の目的は、特に、可聴波長帯域の高周波の騒音が生じることを防止できるニードル弁及びこのニードル弁を有する冷凍サイクル装置を提供することにある。   Accordingly, an object of the present invention is to provide a needle valve that can prevent generation of high frequency noise in an audible wavelength band, and a refrigeration cycle apparatus having the needle valve.

前記目的を達成するために、請求項１に記載の本発明のニードル弁は、内側に流体を通しかつ長手方向に内径が一定に形成された弁口が設けられた弁ポートと、前記弁ポートに接離自在に設けられかつ当該弁ポートに近づくのにしたがって先細となる針状に形成されているとともに、前記弁ポートに接離することで開度を変更する弁体と、を備えたニードル弁において、前記弁体の軸芯を通る断面において、当該弁体の先端部のなす角度をθとし、前記弁口の内径をＤとし、前記弁口の軸芯方向の全長をＬ１とすると、前記角度θが０度を超えかつ４５度以下である場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下であるとともに、前記角度θが４５度を越えて６０度未満である場合に、Ｌ１／Ｄが２．０以上でかつ４．０以下であることを特徴としている。   In order to achieve the above object, the needle valve of the present invention according to claim 1 comprises a valve port provided with a valve port through which fluid is passed and a constant inner diameter is formed in the longitudinal direction, and the valve port. And a valve body that is formed in a needle shape that tapers toward and away from the valve port and changes its opening degree by contacting and separating from the valve port. In the valve, in a cross section passing through the axis of the valve body, when the angle formed by the tip of the valve body is θ, the inner diameter of the valve port is D, and the total length in the axial direction of the valve port is L1, When the angle θ is greater than 0 degree and not greater than 45 degrees, L1 / D is not less than 3.5 and not greater than 5.0, and the angle θ is greater than 45 degrees and less than 60 degrees In addition, L1 / D is 2.0 or more and 4.0 or less. It is set to.

請求項２に記載の本発明のニードル弁は、請求項１記載のニードル弁において、前記弁ポートの前記弁口が開口しかつ前記ニードル弁と相対する弁座には、当該弁座から凸でかつ前記弁口よりも内径が大きく形成されているとともに当該弁口と同軸状の円環状部が設けられていることを特徴としている。   The needle valve according to a second aspect of the present invention is the needle valve according to the first aspect, wherein the valve port of the valve port is open and the valve seat facing the needle valve is convex from the valve seat. In addition, the inner diameter is larger than that of the valve port, and an annular portion coaxial with the valve port is provided.

請求項３に記載の本発明の冷凍サイクル装置は、請求項１又は請求項２記載のニードル弁を冷媒回路中に有することを特徴としている。   A refrigeration cycle apparatus according to a third aspect of the present invention includes the needle valve according to the first or second aspect in a refrigerant circuit.

請求項１に記載された本発明のニードル弁は、弁口の内径Ｄと弁口の全長Ｌ１との関係が、弁体の先端部のなす角度θが０度を超えかつ４５度以下である場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下となる関係であり、かつ、角度θが４５度を越えて６０度未満である場合に、Ｌ１／Ｄが２．０以上でかつ４．０以下でなる関係である。即ち、弁口の内径Ｄに対して、弁口の全長Ｌ１を十分に長く形成して、弁口の内縁ではがれた流体の流れを再度、弁口の内面に付着させるようにしている。即ち、弁口内での流体の流れを層流に保っている。   In the needle valve according to the first aspect of the present invention, the relationship between the inner diameter D of the valve port and the total length L1 of the valve port is such that the angle θ formed by the tip of the valve body exceeds 0 degree and is 45 degrees or less. In this case, when L1 / D is 3.5 or more and 5.0 or less, and the angle θ is more than 45 degrees and less than 60 degrees, L1 / D is 2.0 or more. And a relationship of 4.0 or less. That is, the entire length L1 of the valve port is formed sufficiently long with respect to the inner diameter D of the valve port, and the flow of the fluid that has peeled off at the inner edge of the valve port is again attached to the inner surface of the valve port. That is, the fluid flow in the valve port is maintained in a laminar flow.

したがって、弁口内での流体の流れを層流に保つので、弁口内での流体の流れの乱れによる騒音が発生することを防止できるとともに、下流に乱流のまま流体を導くことを防止できる。よって、特に、開度の少ない即ち弁口と弁体とが近接した状態で、流体が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音が発生することを防止できる即ち高い音が生じることを防止できる。   Therefore, since the fluid flow in the valve port is maintained in a laminar flow, it is possible to prevent noise from being generated due to the turbulence of the fluid flow in the valve port and to prevent the fluid from being guided in the turbulent flow downstream. Therefore, particularly when the fluid flows in a state where the opening degree is small, that is, in the state where the valve opening and the valve body are close to each other, it is possible to prevent generation of high frequency sound in the audible wavelength band of 1 kHz to 20 kHz, that is, high sound is generated. Can be prevented.

請求項２に記載された本発明のニードル弁は、弁座に弁口と同軸でかつ弁口よりも内径の大きな円環状部が設けられているので、弁口内に導かれる流体が、円環状部内に導かれる際にその流量が一度制限される。このため、勿論、弁口内に導かれる流体の流量が制限される。   In the needle valve according to the second aspect of the present invention, the valve seat is provided with an annular portion that is coaxial with the valve port and has a larger inner diameter than the valve port. The flow rate is once limited when led into the section. For this reason, of course, the flow rate of the fluid guided into the valve port is limited.

さらに、弁口の内縁で流れがはがれる前に、流体が、円環状部の内縁でその流れがはがれる。このために、弁口の内縁ではがれる流体の流れの乱れが、直接弁口の内縁ではがれる場合よりも小さくなる。   Furthermore, before the flow is separated at the inner edge of the valve port, the fluid is separated at the inner edge of the annular portion. For this reason, the turbulence of the fluid flow that peels off at the inner edge of the valve port is smaller than when the fluid flow peels off directly at the inner edge of the valve port.

よって、弁口内に導かれる流体の流量が制限されるとともに、弁口の内縁で生じる流体の流れの乱れが小さくなるので、一旦乱流となった流体の流れを再度、弁口の内面に付着させることが確実にでき、弁口内での流体の流れを確実に層流に保つことができる。よって、特に、開度の少ない即ち弁口と弁体とが近接した状態で、流体が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音が発生することを防止できる即ち高い音が生じることを確実に防止できる。   Therefore, the flow rate of the fluid guided into the valve port is limited, and the disturbance of the fluid flow generated at the inner edge of the valve port is reduced, so that the turbulent fluid flow once again adheres to the inner surface of the valve port. The fluid flow in the valve port can be reliably maintained in a laminar flow. Therefore, particularly when the fluid flows in a state where the opening degree is small, that is, in the state where the valve opening and the valve body are close to each other, it is possible to prevent generation of high frequency sound in the audible wavelength band of 1 kHz to 20 kHz, that is, high sound is generated. Can be surely prevented.

請求項３に記載された本発明の冷凍サイクル装置は、前述したニードル弁を備えているので、特に、ニードル弁の開度の少ない即ち弁口と弁体とが近接した状態で、流体が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音が発生することを防止できる即ち高い音が生じることを防止できる。   Since the refrigeration cycle apparatus according to the third aspect of the present invention includes the needle valve described above, the fluid flows particularly when the opening of the needle valve is small, that is, when the valve port and the valve body are close to each other. At this time, it is possible to prevent the generation of high-frequency sound in the audible wavelength band of 1 kHz to 20 kHz, that is, it is possible to prevent the generation of high sound.

以下に、本発明の一実施形態にかかるニードル弁を、図１及び図２を参照して説明する。   Hereinafter, a needle valve according to an embodiment of the present invention will be described with reference to FIGS. 1 and 2.

図１に示すニードル弁１は、例えば、冷凍サイクル装置に用いられ、流体としての冷媒の流量を変化させる所謂膨張弁として用いられる。   A needle valve 1 shown in FIG. 1 is used, for example, in a refrigeration cycle apparatus, and is used as a so-called expansion valve that changes the flow rate of a refrigerant as a fluid.

ニードル弁１は、図１に示すように、カップ状の金屑製あるいは合成樹脂製の弁箱１０を有する。弁箱１０は、弁室１１と、弁室１１の後述する弁体３０と相対する弁座２２に開口形成された丸穴形状の弁口１２と、横継手１３を接続され弁室１１に直接連通する入ロポート１４と、下継手１５を接続され弁口１２を経て弁室１１に連通する出ロポート１６とを有する。即ち、弁箱１０は、その内側に入ロポート１４と弁室１１と弁口１２と出ロポート１６とに亘って、前述した冷媒を流す流路が形成されている。また、弁箱１０の図１中の上端部内には、円筒状の弁ガイド部材３４が取り付けられている。   As shown in FIG. 1, the needle valve 1 has a valve box 10 made of cup-shaped gold dust or synthetic resin. The valve box 10 is connected directly to the valve chamber 11 by connecting a valve chamber 11, a round hole-shaped valve opening 12 formed in a valve seat 22 facing the valve body 30 described later of the valve chamber 11, and a lateral joint 13. The inlet port 14 communicates, and the outlet port 16 is connected to the lower joint 15 and communicates with the valve chamber 11 via the valve port 12. That is, the valve box 10 is formed with a flow passage through which the above-described refrigerant flows over the inlet port 14, the valve chamber 11, the valve port 12, and the outlet port 16. A cylindrical valve guide member 34 is attached to the upper end of the valve box 10 in FIG.

弁口１２は、断面丸形で直線状に延在した孔であるとともに、その内径Ｄがその長手方向の全長に亘って一定に形成されて、その内側に流体としての冷媒を流す。また、弁箱１０の前記弁座２２及び弁口１２を含み、かつ弁体３０と間隔をあけて相対する部分は、特許請求の範囲に記載された弁ポート２４をなしている。即ち、ニードル弁１は、弁口１２が形成された弁ポート２４を備えている。   The valve port 12 is a hole having a round cross section and extending linearly, and an inner diameter D thereof is formed over the entire length in the longitudinal direction, and a refrigerant as a fluid flows inside the hole. Further, a portion of the valve box 10 including the valve seat 22 and the valve port 12 and facing the valve body 30 with a space therebetween forms a valve port 24 described in the claims. That is, the needle valve 1 includes a valve port 24 in which a valve port 12 is formed.

弁箱１０の図１中の上部には、円筒状の蓋部材２８が同軸的に取り付けられており、この蓋部材２８の図１中の上部に取付板１７によって固定支持部材(雌ねじ部材)１８が固定されている。回定支持部材１８にはガイド孔１９が形成されている。ガイド孔１９は弁口１２と同心位置にあり、ガイド孔１９には、円筒状の弁ホルダ２０が軸芯方向(上下方向)、つまり弁開閉方向に摺動可能に嵌合している。これにより、弁ホルダ２０は弁箱１０内を軸芯方向に移動可能である。   A cylindrical lid member 28 is coaxially attached to the upper part of the valve box 10 in FIG. 1, and a fixing support member (female screw member) 18 is attached to the upper part of the lid member 28 in FIG. Is fixed. A guide hole 19 is formed in the rotation support member 18. The guide hole 19 is concentric with the valve port 12, and a cylindrical valve holder 20 is fitted in the guide hole 19 so as to be slidable in the axial direction (vertical direction), that is, in the valve opening / closing direction. Thereby, the valve holder 20 can move in the valve box 10 in the axial direction.

弁ホルダ２０は、図１中の下端の内周に円環状の下側リップ部材２１が取り付けられ、その図１中の上端の内周に円環状の上側リップ片２３が一体に形成されている。下側リップ部材２１の図１中の上面は、円環段差状に形成された上向きのストッパ面部２５をなしている。なお、弁ホルダ２０には、均圧孔１０５が形成されている。   In the valve holder 20, an annular lower lip member 21 is attached to the inner periphery of the lower end in FIG. 1, and an annular upper lip piece 23 is integrally formed on the inner periphery of the upper end in FIG. . The upper surface of the lower lip member 21 in FIG. 1 forms an upward stopper surface portion 25 formed in an annular step shape. A pressure equalizing hole 105 is formed in the valve holder 20.

弁ホルダ２０に取り付けられた下側リップ部材２１に、金属製あるいは合成樹脂製の弁体３０が軸芯方向に変位可能に取り付けられている。弁体３０は、円柱状の針状に形成され、下側リップ部材２１の内側に形成された開口２６に遊嵌合、つまり、弁ホルダ２０に対して径方向に変位できるよう所定の径方向間隙を有する状態で通されて、そして、図１中の上端部から凸に設けられた環段差部(肩部)３２の下底面が下側リップ部材２１の上面に係合することにより、弁ホルダ２０より回転可能に吊り下げ支持されている。   A metal or synthetic resin valve body 30 is attached to the lower lip member 21 attached to the valve holder 20 so as to be displaceable in the axial direction. The valve body 30 is formed in a cylindrical needle shape and loosely fits into an opening 26 formed inside the lower lip member 21, that is, in a predetermined radial direction so that it can be displaced in the radial direction with respect to the valve holder 20. The lower bottom surface of the annular stepped portion (shoulder portion) 32 that is passed through in a state having a gap and that protrudes from the upper end portion in FIG. 1 engages with the upper surface of the lower lip member 21. The holder 20 is supported so as to be rotatable from the holder 20.

さらに、弁体３０は、弁ガイド部材３４内に通されて、その軸芯に沿って移動自在に当該弁ガイド部材３４に支持されている。弁体３０は、図１中の下側に位置しかつ弁座２２即ち弁ポート２４と相対する先端部が円錐形をした流量調整部３３をなしており、流量調整部３３は。下側リップ部材２１の内側の開口２６より弁口１２へ向けて突出している。このように、弁体３０は、軸芯方向に移動自在とされることで、弁ポート２４に接離自在に設けられ、その流量調整部３３が弁ポート２４に近づくのにしたがって先細となるように形成されている。   Further, the valve body 30 is passed through the valve guide member 34 and supported by the valve guide member 34 so as to be movable along the axial center thereof. The valve body 30 is positioned on the lower side in FIG. 1 and has a flow rate adjusting portion 33 having a conical tip at the front end facing the valve seat 22, that is, the valve port 24. It protrudes toward the valve port 12 from the opening 26 inside the lower lip member 21. As described above, the valve body 30 is movable in the axial direction so as to be able to contact and separate from the valve port 24 so that the flow rate adjustment portion 33 tapers as the valve port 24 approaches. Is formed.

弁体３０は、流量調整部３３の弁口１２に対する進入度(軸芯方向位置)に応じて、冷媒の定量的な流量制御を行い、流量調整部３３が弁口１２の周りの弁座２２に当接着座することにより、弁口１２を閉じる(閉塞する)全閉状態になる。   The valve body 30 performs quantitative flow rate control of the refrigerant according to the degree of penetration (position in the axial direction) of the flow rate adjusting unit 33 with respect to the valve port 12, and the flow rate adjusting unit 33 controls the valve seat 22 around the valve port 12. The valve seat 12 is closed (closed) by closing the adhesive seat.

弁ホルダ２０には、後述するステッピングモータ７０のロータ軸をなす雄ねじ軸７３の下端部７４が、弁ホルダ２０の上側リップ片２３の内側の開口２７を遊嵌合状態で貫通している。この遊嵌合状態とは、弁ホルダ２０と雄ねじ軸７３とが相対的に径方向に変位できることを云う。   A lower end portion 74 of a male screw shaft 73 that forms a rotor shaft of a stepping motor 70 described later passes through the valve holder 20 through the opening 27 inside the upper lip piece 23 of the valve holder 20 in a loosely fitted state. The loose fitting state means that the valve holder 20 and the male screw shaft 73 can be relatively displaced in the radial direction.

雄ねじ軸７３の下端部７４、つまり、雄ねじ軸７３と、弁体３０との間には、リテーナ部材３５が配置されている。リテーナ部材３５は、円柱状に形成され、勿論、弁ホルダ２０内に収容されており、その図１中の上端には、ばねリテーナを兼ねたフランジ状の吊下係合部７５がその全周に亘って凸に一体形成されている。吊下係合部７５は、図１中の上面側にて、フッ素樹脂等の高滑性プラスチックをコーテイングしたもの、あるいは高滑性プラスチックからなるワッシヤ２９，３１を挟んで弁ホルダ２０の上側リップ片２３に回転可能に係合している。この係合により、弁ホルダ２０が雄ねじ軸７３より回転可能に吊り下げ支持される。   The retainer member 35 is disposed between the lower end portion 74 of the male screw shaft 73, that is, between the male screw shaft 73 and the valve body 30. The retainer member 35 is formed in a columnar shape and, of course, is accommodated in the valve holder 20. A flange-like suspension engaging portion 75 that also serves as a spring retainer is disposed at the upper end in FIG. It is integrally formed to be convex over the entire area. The suspension engaging portion 75 is formed by coating the upper lip of the valve holder 20 on the upper surface side in FIG. The piece 23 is rotatably engaged. By this engagement, the valve holder 20 is suspended and supported so as to be rotatable from the male screw shaft 73.

リテーナ部材３５に設けられた吊下係合部７５と、弁体３０の環段差部(肩部)３２との間には、内側にリテーナ部材３５を通した圧縮コイルばね３６が所定の予荷重を与えられた状態で取り付けられている。   A compression coil spring 36 through which the retainer member 35 is passed inside has a predetermined preload between the hanging engagement portion 75 provided on the retainer member 35 and the annular step portion (shoulder portion) 32 of the valve body 30. It is attached in the given state.

雄ねじ軸７３の外周面には、雄ねじ部３７が形成されている。雄ねじ部３７は固定支持部材１８に形成された雌ねじ部(雌ねじ孔)３８にねじ係合している。このねじ係合により、雄ねじ軸７３は、回転に伴って軸芯方向、つまり、弁開閉方向に移動する。この雄ねじ部３７と雌ねじ部３８とのねじ係合によって送りねじ機構が構成され、送りねじ機構は、雄ねじ軸７３の回転運動を弁開閉方向の直線運動に変換する。   A male screw portion 37 is formed on the outer peripheral surface of the male screw shaft 73. The male screw portion 37 is screw-engaged with a female screw portion (female screw hole) 38 formed in the fixed support member 18. By this screw engagement, the male screw shaft 73 moves in the axial direction, that is, in the valve opening / closing direction with rotation. The feed screw mechanism is constituted by the screw engagement between the male screw portion 37 and the female screw portion 38, and the feed screw mechanism converts the rotational motion of the male screw shaft 73 into a linear motion in the valve opening / closing direction.

蓋部材２８の図１中の上部には、ステッビングモータ７０のキャン状のロータケース７１が溶接等によって気密に固定されている。ロータケース７１内には、外周面部７２Ａを多板前磁されたヨーク７２が回転可能に設けられている。ヨーク７２にはヨーク軸を兼ねている雄ねじ軸７３の図１中の中央部が固定連結されている。   A can-shaped rotor case 71 of a stepping motor 70 is airtightly fixed to the upper portion of the lid member 28 in FIG. 1 by welding or the like. In the rotor case 71, a yoke 72 whose outer peripheral surface portion 72A is pre-magnetized in multiple plates is rotatably provided. A central portion in FIG. 1 of a male screw shaft 73 also serving as a yoke shaft is fixedly connected to the yoke 72.

ロータケース７１の外側には、ステータコイルユニット７７が差し込み装着されている。ステータコイルユニット７７は、詳細を図示されていないが、ステッピングモータ用のものとして、内部に、磁極歯、巻線部、電気配線部を有する周知の気密モールド構造のものである。   A stator coil unit 77 is inserted and attached to the outside of the rotor case 71. Although not shown in detail, the stator coil unit 77 has a well-known airtight mold structure having a magnetic pole tooth, a winding part, and an electric wiring part therein for a stepping motor.

ロータケース７１内には、ロータケース７１の天井部より垂下固定されたガイド支持筒７８と、ガイド支持筒７８の外周部に装着された螺旋ガイド線体７９と、ガイド支持筒７８の上端部に形成された固定ストッパ部８０と、螺旋ガイド線体７９に螺合した可動ストッパ部材８１と、可動ストッパ部材８１と係合してこれを蹴り回すヨーク７２の突起部８２とがあり、これらによって、弁開あるいは弁閉のストッパが構成されている。また、ガイド支持筒７８は、雄ねじ軸７３の図１中の上端部７６を内側に通して、当該雄ねじ軸７３を回転自在に支持している。   In the rotor case 71, a guide support tube 78 suspended from the ceiling of the rotor case 71, a spiral guide wire 79 mounted on the outer periphery of the guide support tube 78, and an upper end portion of the guide support tube 78 There are a fixed stopper portion 80 formed, a movable stopper member 81 screwed into the spiral guide wire body 79, and a protrusion 82 of the yoke 72 that engages and kicks the movable stopper member 81, thereby A valve opening or valve closing stopper is configured. Further, the guide support cylinder 78 passes the upper end 76 in FIG. 1 of the male screw shaft 73 inward, and rotatably supports the male screw shaft 73.

ステッピングモータ７０は、ロータ７２によって雄ねじ軸７３を回転駆動し、回転に伴う雄ねじ軸７３の軸芯方向移動によって弁ホルダ２０と共に弁体３０を弁開閉方向に直線移動させる。これにより、弁体３０の流量調整部３３の弁口１２に対する軸芯方向位置(弁開閉方向の直線移動位置)が変わり、その軸芯方向位置に応じて弁口１２の実効開口面積が増減し、冷媒の定量的な流量制御が行われる。このように、弁体３０は、弁口１２が設けられた弁ポート２４に接離することで、冷媒の流量を変更即ちニードル弁１の開度を変更する。   The stepping motor 70 rotationally drives the male screw shaft 73 by the rotor 72, and linearly moves the valve body 30 in the valve opening / closing direction together with the valve holder 20 by the axial movement of the male screw shaft 73 accompanying the rotation. Thereby, the axial direction position (linear movement position in the valve opening / closing direction) of the valve body 30 with respect to the valve port 12 of the flow rate adjusting unit 33 changes, and the effective opening area of the valve port 12 increases or decreases according to the axial direction position. Quantitative flow rate control of the refrigerant is performed. Thus, the valve body 30 changes the flow rate of the refrigerant, that is, changes the opening degree of the needle valve 1 by making contact with and separating from the valve port 24 in which the valve port 12 is provided.

弁体３０の弁開閉方向の図１中の下方に向かう降下移動により、弁口１２の実効開口面積が徐々に低減し、これに応じて弁口１２を流れる流体の流量が徐々に低減する。弁体３０が弁開閉方向に所定量降下移動すると、弁体３０の流量調整部３３が弁座２２に当接着座することにより、弁口１２が閉塞される全開状態になる。   Due to the downward movement of the valve body 30 in the valve opening / closing direction in FIG. 1, the effective opening area of the valve port 12 is gradually reduced, and the flow rate of the fluid flowing through the valve port 12 is gradually reduced accordingly. When the valve body 30 is moved downward by a predetermined amount in the valve opening / closing direction, the flow rate adjusting portion 33 of the valve body 30 comes into contact with the valve seat 22 so that the valve port 12 is closed.

また、本実施形態のニードル弁１では、図２に示すように、弁体３０の軸芯を通る断面において当該弁体３０の流量調整部３３即ち先端部の外周面同士のなす角度をθとし、弁口１２の内径をＤとし、弁口１２の軸芯方向の全長をＬ１とすると、角度が０度を超えかつ４５度以下の場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下となっている。図示例では、角度θが、約３５度でＬ１／Ｄが３．５となっている。   Further, in the needle valve 1 of the present embodiment, as shown in FIG. 2, an angle formed by the flow rate adjusting portion 33 of the valve body 30, that is, the outer peripheral surface of the tip portion, is θ in a cross section passing through the axial center of the valve body 30. When the inner diameter of the valve port 12 is D and the total length in the axial direction of the valve port 12 is L1, when the angle exceeds 0 degree and is 45 degrees or less, L1 / D is 3.5 or more and 5. 0 or less. In the illustrated example, the angle θ is about 35 degrees and L1 / D is 3.5.

前述した構成のニードル弁１は、図６に示された冷凍サイクル装置の冷媒回路中に設けられて、当該冷凍サイクル装置の膨張弁として機能する。   The needle valve 1 configured as described above is provided in the refrigerant circuit of the refrigeration cycle apparatus shown in FIG. 6 and functions as an expansion valve of the refrigeration cycle apparatus.

この冷凍サイクル装置は、図６に示すように、圧縮機１０１と、凝縮器（室外熱交換器）１０２と、膨張弁として用いられる前述したニードル弁１と、蒸発器（室内熱交換器）１０４と、これらをループ接続する冷媒通路１０５〜１０８とを有する。   As shown in FIG. 6, this refrigeration cycle apparatus includes a compressor 101, a condenser (outdoor heat exchanger) 102, the needle valve 1 used as an expansion valve, and an evaporator (indoor heat exchanger) 104. And refrigerant passages 105 to 108 that connect them in a loop.

この冷凍サイクル装置は、空気調和装置（冷房）や冷凍・冷蔵庫等で使用される。なお、上述したこのニードル弁１が適用される冷凍サイクル装置は、図６に示されているような基本的な冷凍サイクル装置に限られることはなく、四方弁の組み込みにより、冷媒回路における冷媒流れ方向を逆転できる冷房・暖房用の空気調和装置や、室内機に二つの熱交換器が直列接続され、その二つの熱交換器間に追加の膨張弁を有する冷暖房・除湿可能な空気調和装置等、あらゆる冷凍サイクル装置にも適用可能である。   This refrigeration cycle apparatus is used in air conditioners (cooling), refrigeration / refrigerators, and the like. The above-described refrigeration cycle apparatus to which the needle valve 1 is applied is not limited to the basic refrigeration cycle apparatus as shown in FIG. 6, and the refrigerant flow in the refrigerant circuit can be achieved by incorporating a four-way valve. Air conditioning equipment for cooling and heating that can reverse the direction, air conditioning equipment that can be used for air conditioning and dehumidification with two heat exchangers connected in series to the indoor unit and an additional expansion valve between the two heat exchangers It can be applied to any refrigeration cycle apparatus.

本実施形態によれば、弁口１２の内径Ｄと弁口１２の全長Ｌ１との関係が、弁体３０の先端のなす角度θが０度を超えかつ４５度以下である場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下となる関係である。即ち、弁口１２の内径Ｄに対して、弁口１２の全長Ｌ１を十分に長く形成して、弁口１２の内縁ではがれた流体としての冷媒の流れを再度、弁口１２の内面に付着させるようにしている。即ち、弁口１２内での流体の流れを層流に保っている。   According to this embodiment, when the relationship between the inner diameter D of the valve port 12 and the total length L1 of the valve port 12 is such that the angle θ formed by the tip of the valve body 30 exceeds 0 degree and is 45 degrees or less, L1 / In this relationship, D is 3.5 or more and 5.0 or less. That is, the entire length L1 of the valve port 12 is formed sufficiently long with respect to the inner diameter D of the valve port 12, and the flow of the refrigerant as the fluid peeled off at the inner edge of the valve port 12 is again attached to the inner surface of the valve port 12. I try to let them. That is, the fluid flow in the valve port 12 is maintained in a laminar flow.

したがって、弁口１２内での流体としての冷媒の流れを層流に保つので、弁口１２内での流体としての冷媒の流れの乱れによる騒音が発生することを防止できるとともに、下流に乱流のまま流体としての冷媒を導くことを防止できる。よって、特に、開度の少ない即ち弁口１２と弁体３０とが近接した状態で、流体としての冷媒が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音が発生することを防止できる即ち高い音が生じることを防止できる。   Therefore, the flow of the refrigerant as the fluid in the valve port 12 is maintained in a laminar flow, so that it is possible to prevent noise due to the turbulence of the flow of the refrigerant as the fluid in the valve port 12 and to turbulent downstream It is possible to prevent the refrigerant as a fluid from being led. Therefore, it is possible to prevent the generation of high-frequency sound in the audible wavelength band from 1 kHz to 20 kHz, particularly when the refrigerant as a fluid flows in a state where the opening degree is small, that is, the valve port 12 and the valve body 30 are close to each other. That is, it is possible to prevent a high sound from being generated.

前述した実施形態では、角度θが０度を超えかつ４５度以下である場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下となっている。しかしながら、本発明では、図５に示すように、前記角度θが４５度を越えて６０度未満である場合に、Ｌ１／Ｄが２．０以上でかつ４．０以下でなっていても良い。なお、図５に示された例では、角度θが、約４５度でＬ１／Ｄが２．５となっている。この場合も、前述した実施形態と同様に、弁口１２の内径Ｄに対して、弁口１２の全長Ｌ１を十分に長く形成して、弁口１２の内縁ではがれた流体としての冷媒の流れを再度、弁口１２の内面に付着させるようにして、特に、高い騒音の発生を防止できる。   In the above-described embodiment, when the angle θ exceeds 0 degree and is 45 degrees or less, L1 / D is 3.5 or more and 5.0 or less. However, in the present invention, as shown in FIG. 5, when the angle θ is more than 45 degrees and less than 60 degrees, L1 / D may be 2.0 or more and 4.0 or less. . In the example shown in FIG. 5, the angle θ is about 45 degrees and L1 / D is 2.5. Also in this case, similarly to the above-described embodiment, the entire length L1 of the valve port 12 is formed sufficiently long with respect to the inner diameter D of the valve port 12, and the refrigerant flows as a fluid separated at the inner edge of the valve port 12. Is attached to the inner surface of the valve port 12 in particular, so that particularly high noise can be prevented.

また、本発明では、図３及び図４に示すように、弁箱１０の弁ポート２４に円環状部３９を一体に設けても良い。なお、図３及び図４において、前述した実施形態と同一部分には、同一符号を付して説明を省略する。円環状部３９は、その内径が弁口１２の内径Ｄよりも大きい円環状に形成され、かつ弁座２２から弁体３０に向かって凸に形成されているとともに、弁口１２と同軸に配置されている。なお、図３では、弁体３０の外径が円環状部３９の内径よりも大きな場合を示し、図４は、弁体３０の外径が円環状部３９の内径よりも小さな場合を示している。   Moreover, in this invention, as shown in FIG.3 and FIG.4, you may provide the annular part 39 in the valve port 24 of the valve box 10 integrally. 3 and 4, the same parts as those of the above-described embodiment are denoted by the same reference numerals and description thereof is omitted. The annular portion 39 is formed in an annular shape whose inner diameter is larger than the inner diameter D of the valve port 12, is formed to protrude from the valve seat 22 toward the valve body 30, and is arranged coaxially with the valve port 12. Has been. 3 shows a case where the outer diameter of the valve body 30 is larger than the inner diameter of the annular portion 39, and FIG. 4 shows a case where the outer diameter of the valve body 30 is smaller than the inner diameter of the annular portion 39. Yes.

これらの場合には、弁座２２に弁口１２と同軸でかつ弁口１２よりも内径の大きな円環状部３９が設けられているので、弁口１２内に導かれる流体としての冷媒が、円環状部３９内に導かれる際にその流量が一度制限される。このため、勿論、弁口１２内に導かれる流体としての冷媒の流量が制限される。   In these cases, the valve seat 22 is provided with the annular portion 39 that is coaxial with the valve port 12 and has a larger inner diameter than the valve port 12, so that the refrigerant as the fluid guided into the valve port 12 is circular. When guided into the annular portion 39, the flow rate is once limited. For this reason, of course, the flow rate of the refrigerant as the fluid guided into the valve port 12 is limited.

さらに、弁口１２の内縁で流れがはがれる前に、流体としての冷媒が、円環状部３９の内縁でその流れがはがれる。このために、弁口１２の内縁ではがれる流体としての冷媒の流れの乱れが、直接弁口１２の内縁ではがれる場合よりも小さくなる。   Further, before the flow is separated at the inner edge of the valve port 12, the refrigerant as the fluid is separated at the inner edge of the annular portion 39. For this reason, the disturbance of the flow of the refrigerant as the fluid that is peeled off at the inner edge of the valve port 12 is smaller than that in the case of being peeled off at the inner edge of the valve port 12 directly.

よって、弁口１２内に導かれる流体としての冷媒の流量が制限されるとともに、弁口１２の内縁で生じる流体としての冷媒の流れの乱れを小さくなるので、一旦乱流となった流体としての冷媒の流れを再度、弁口１２の内面に付着させることが確実にでき、弁口１２内での流体としての冷媒の流れを確実に層流に保つことができる。よって、特に、開度の少ない即ち弁口１２と弁体３０とが近接した状態で、流体としての冷媒が流れる際に、１ｋＨｚから２０ｋＨｚの可聴波長帯域の高周波の音が発生することを防止できる即ち高い音が生じることを確実に防止できる。   Therefore, the flow rate of the refrigerant as the fluid guided into the valve port 12 is limited, and the disturbance of the refrigerant flow as the fluid generated at the inner edge of the valve port 12 is reduced. The refrigerant flow can be reliably attached to the inner surface of the valve port 12 again, and the refrigerant flow as the fluid in the valve port 12 can be reliably maintained in a laminar flow. Therefore, it is possible to prevent the generation of high-frequency sound in the audible wavelength band from 1 kHz to 20 kHz, particularly when the refrigerant as a fluid flows in a state where the opening degree is small, that is, in a state where the valve port 12 and the valve body 30 are close to each other. That is, it is possible to surely prevent a high sound from being generated.

なお、前述した実施形態は本発明の代表的な形態を示したに過ぎず、本発明は、実施形態に限定されるものではない。即ち、本発明の骨子を逸脱しない範囲で種々変形して実施することができる。例えば、前述した実施形態では、冷凍サイクル装置を構成する膨張弁をなすニードル弁１を示している。   In addition, embodiment mentioned above only showed the typical form of this invention, and this invention is not limited to embodiment. That is, various modifications can be made without departing from the scope of the present invention. For example, in the above-described embodiment, the needle valve 1 constituting the expansion valve constituting the refrigeration cycle apparatus is shown.

しかしながら、本発明のニードル弁１は、冷凍サイクル装置以外の装置を構成する各種の用途に用いられても良い。要するに、本発明のニードル弁１は、各種の流体の流量を制御しても良い。また、本発明のニードル弁１は、角度θと内径Ｄと全長Ｌ１とが前述した関係を満たしていれば、各部の寸法を適宜変更しても良いことは勿論である。   However, the needle valve 1 of the present invention may be used for various applications constituting devices other than the refrigeration cycle device. In short, the needle valve 1 of the present invention may control the flow rates of various fluids. Further, in the needle valve 1 of the present invention, as long as the angle θ, the inner diameter D, and the total length L1 satisfy the above-described relationship, it is needless to say that the dimensions of each part may be changed as appropriate.

本発明の一実施形態のニードル弁の断面図である。It is sectional drawing of the needle valve of one Embodiment of this invention. 図１に示されたニードル弁の要部を拡大して示す断面図である。It is sectional drawing which expands and shows the principal part of the needle valve shown by FIG. 図２に示されたニードル弁の変形例の要部の断面図である。It is sectional drawing of the principal part of the modification of the needle valve shown by FIG. 図２に示されたニードル弁の他の変形例の要部の断面図である。It is sectional drawing of the principal part of the other modification of the needle valve shown by FIG. 図２に示されたニードル弁の更に他の変形例の要部の断面図である。It is sectional drawing of the principal part of the further another modification of the needle valve shown by FIG. 図１に示されたニードル弁を備えた冷凍サイクル装置の冷媒回路図である。It is a refrigerant circuit figure of the refrigerating cycle device provided with the needle valve shown by FIG.

符号の説明Explanation of symbols

１ ニードル弁
１２ 弁口
２２ 弁座
２４ 弁ポート
３０ 弁体
３３ 流量調整部（先端部）
３９ 円環状部
θ 角度
Ｌ１ 全長
Ｄ 内径 DESCRIPTION OF SYMBOLS 1 Needle valve 12 Valve port 22 Valve seat 24 Valve port 30 Valve body 33 Flow volume adjustment part (tip part)
39 Toroidal part θ Angle L1 Total length D Inner diameter

Claims (3)

内側に流体を通しかつ長手方向に内径が一定に形成された弁口が設けられた弁ポートと、
前記弁ポートに接離自在に設けられかつ当該弁ポートに近づくのにしたがって先細となる針状に形成されているとともに、前記弁ポートに接離することで開度を変更する弁体と、を備えたニードル弁において、
前記弁体の軸芯を通る断面において、当該弁体の先端部のなす角度をθとし、前記弁口の内径をＤとし、前記弁口の軸芯方向の全長をＬ１とすると、
前記角度θが０度を超えかつ４５度以下である場合に、Ｌ１／Ｄが３．５以上でかつ５．０以下であるとともに、
前記角度θが４５度を越えて６０度未満である場合に、Ｌ１／Ｄが２．０以上でかつ４．０以下であることを特徴とするニードル弁。 A valve port provided with a valve port that allows fluid to pass inside and has a constant inner diameter in the longitudinal direction;
A valve body that is provided so as to be able to contact with and separate from the valve port and is tapered as it approaches the valve port, and a valve body whose opening degree is changed by contacting and separating from the valve port. In the provided needle valve,
In a cross section passing through the axis of the valve body, when the angle formed by the tip of the valve body is θ, the inner diameter of the valve port is D, and the total length in the axial direction of the valve port is L1,
When the angle θ exceeds 0 degree and is 45 degrees or less, L1 / D is 3.5 or more and 5.0 or less,
When the angle θ is greater than 45 degrees and less than 60 degrees, L1 / D is 2.0 or more and 4.0 or less. 前記弁ポートの前記弁口が開口しかつ前記ニードル弁と相対する弁座には、当該弁座から凸でかつ前記弁口よりも内径が大きく形成されているとともに当該弁口と同軸状の円環状部が設けられていることを特徴とする請求項１記載のニードル弁。   The valve seat of the valve port that is open and opposed to the needle valve has a circular shape that is convex from the valve seat and has an inner diameter larger than that of the valve port and is coaxial with the valve port. The needle valve according to claim 1, wherein an annular portion is provided. 請求項１又は請求項２記載のニードル弁を冷媒回路中に有することを特徴とする冷凍サイクル装置。   A refrigeration cycle apparatus comprising the needle valve according to claim 1 or 2 in a refrigerant circuit.
JP2007073408A 2007-03-20 2007-03-20 Needle valve, and refrigerating cycle device having the same Pending JP2008232290A (en)

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