JP2006266667A - Expansion valve and freezing apparatus - Google Patents

Expansion valve and freezing apparatus Download PDF

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JP2006266667A
JP2006266667A JP2005362503A JP2005362503A JP2006266667A JP 2006266667 A JP2006266667 A JP 2006266667A JP 2005362503 A JP2005362503 A JP 2005362503A JP 2005362503 A JP2005362503 A JP 2005362503A JP 2006266667 A JP2006266667 A JP 2006266667A
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valve body
valve
peripheral surface
outer peripheral
throttle
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Toru Yukimoto
徹 雪本
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Daikin Industries Ltd
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Daikin Industries Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide an expansion valve capable of reducing discontinuous refrigerant passing noise generated following passing of gas-liquid two-phase refrigerant flow through a throttle portion, and vibration noise caused by pressure fluctuation without impairing its reliability, and to provided a freezing apparatus capable of reducing refrigerant passing noise at an expansion valve inlet side by using such an expansion valve. <P>SOLUTION: This expansion valve has a structure having a valve main body 1, a refrigerant flow passage 2 formed inside of the valve main body 1, a valve element 3 mounted in the valve main body 1, a first throttle portion 4 formed on the refrigerant flow passage 2, and a second throttle portion 5 formed at an upstream side of the first throttle portion in the refrigerant flow passage 2. At least an opening of the first throttle portion 4 is variable and may be completely closable. The second throttle portion 5 is set not be completely closed. The second throttle portion 5 has a tapered face on at least an outer peripheral face of the second valve element portion 14 or an inner peripheral face of the second valve hole 9, further a groove portion 15 extending in the moving direction of the valve element 3, is formed on one of the outer peripheral face of the second valve element portion 14 and the inner peripheral face of the second valve hole 9, and a plurality of approximately independent passages 16 are formed therebetween. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、膨張弁及び冷凍装置に関し、より詳細には、空気調和装置等の冷凍装置に用いられる膨張弁の冷媒通過音を低下させる技術に関する。   The present invention relates to an expansion valve and a refrigeration apparatus, and more particularly to a technique for reducing refrigerant passing sound of an expansion valve used in a refrigeration apparatus such as an air conditioner.

図１１は、従来のセパレート型空気調和機の基本的な冷媒回路を示したものである。この図１１に示すように、従来の冷房専用セパレート型空気調和機の冷媒回路は、圧縮機１０１、室外コイル１０２、膨張弁１０３、室内コイル１０４が順次接続された循環回路に形成されている。また、圧縮機１０１及び室外コイル１０２は室外ユニット１０５に収納され、膨張弁１０３及び室内コイル１０４は室内ユニット１０６に収納されている。膨張弁１０３には、例えば図１２に示すような電動膨張弁が用いられている。   FIG. 11 shows a basic refrigerant circuit of a conventional separate type air conditioner. As shown in FIG. 11, the refrigerant circuit of the conventional cooling-only separate type air conditioner is formed in a circulation circuit in which a compressor 101, an outdoor coil 102, an expansion valve 103, and an indoor coil 104 are sequentially connected. The compressor 101 and the outdoor coil 102 are housed in the outdoor unit 105, and the expansion valve 103 and the indoor coil 104 are housed in the indoor unit 106. For the expansion valve 103, for example, an electric expansion valve as shown in FIG. 12 is used.

この電動膨張弁は、弁本体１１１内に冷媒流通路１１２が形成され、この冷媒流通路１１２を流れ方向に仕切る仕切壁１１３を備えている。また、弁本体１１１内には弁体１１４が収納されるとともに、仕切壁１１３には弁孔１１５が形成されている。そして、この弁体１１４をパルスモータ（図示せず）により駆動して、弁体１１４の先端に形成された先細の第１弁体部１１６を弁孔１１５に対し進退させることにより、弁本体１１１内に弁孔１１５の開度を調整する絞り部１１８が形成されている。   This electric expansion valve has a refrigerant flow passage 112 formed in the valve body 111, and includes a partition wall 113 that partitions the refrigerant flow passage 112 in the flow direction. In addition, a valve body 114 is accommodated in the valve main body 111, and a valve hole 115 is formed in the partition wall 113. Then, the valve body 114 is driven by a pulse motor (not shown), and the tapered first valve body portion 116 formed at the tip of the valve body 114 is moved forward and backward with respect to the valve hole 115, whereby the valve body 111. A throttle part 118 for adjusting the opening of the valve hole 115 is formed therein.

ここで、上記冷房専用セパレート型空気調和機における冷房運転サイクルを図１１に従って説明する。なお、この図１１における実線矢印は、冷房運転サイクル時の冷媒の流れ方向を示す。   Here, the cooling operation cycle in the cooling-only separate type air conditioner will be described with reference to FIG. In addition, the solid line arrow in this FIG. 11 shows the flow direction of the refrigerant | coolant at the time of a cooling operation cycle.

圧縮機１０１で圧縮された高圧ガス冷媒は、室外コイル１０２に搬送され、外気と熱交換して凝縮液化する。この高圧液冷媒は、液管１０７を介して膨張弁１０３に搬送され、膨張弁１０３の入口ポート１１１ａから弁本体１１１内に吸入される。弁本体１１１内に吸入された冷媒は、絞り部１１８で減圧され、出口ポート１１１ｂを介して室内コイル１０４に送られる。そして、室内コイル１０４に送られた冷媒が、室内空気と熱交換して蒸発気化し、低圧ガス冷媒となって圧縮機１０１に帰還する。   The high-pressure gas refrigerant compressed by the compressor 101 is conveyed to the outdoor coil 102 and heat-exchanged with the outside air to be condensed and liquefied. The high-pressure liquid refrigerant is conveyed to the expansion valve 103 via the liquid pipe 107 and is sucked into the valve main body 111 from the inlet port 111 a of the expansion valve 103. The refrigerant sucked into the valve body 111 is depressurized by the throttle unit 118 and sent to the indoor coil 104 via the outlet port 111b. Then, the refrigerant sent to the indoor coil 104 evaporates by exchanging heat with the indoor air, and returns to the compressor 101 as a low-pressure gas refrigerant.

以上のように動作する冷房専用セパレート型空気調和機の冷房運転サイクルにおいては、一般的に、据付条件や運転条件の変化などにより、室外コイル１０２から膨張弁１０３までの液管１０７内で気泡が発生することがある。また、この気泡が大きく成長すると、冷媒流れの中に大きな気泡が断続的に存在するスラグ流やプラグ流となる。このようなスラグ流やプラグ流が発生すると、絞り部を通過する際に液冷媒とガス冷媒とが交互に流れる不連続状態となって圧力変動を発生する。その結果、液冷媒とガス冷媒が交互に絞り部を通過することに伴う不連続な冷媒流動音、いわゆる「チュルチュル」音と、気液２相冷媒流が絞り部を通過することに伴う冷媒流の圧力変動に起因する振動音とを発生していた。   In the cooling operation cycle of the separate type air conditioner for cooling that operates as described above, generally, bubbles are generated in the liquid pipe 107 from the outdoor coil 102 to the expansion valve 103 due to changes in installation conditions and operation conditions. May occur. Further, when the bubbles grow large, a slag flow or a plug flow in which large bubbles are intermittently present in the refrigerant flow. When such a slag flow or a plug flow is generated, a pressure fluctuation occurs due to a discontinuous state in which the liquid refrigerant and the gas refrigerant alternately flow when passing through the throttle portion. As a result, a discontinuous refrigerant flow sound that accompanies the passage of liquid refrigerant and gas refrigerant alternately through the throttle portion, the so-called “church” sound, and the refrigerant flow that accompanies the gas-liquid two-phase refrigerant flow through the throttle portion. And vibration noise caused by pressure fluctuations.

このような問題点に対し、絞り部入口側に細い通路の集合体を設けて気泡を細分化して気液が混合した状態とすることにより、絞り部における冷媒流れを連続化する方法（以下従来Ａ方法という）が知られている。その具体例として、特許文献１の第１実施例のように絞り部入口側に多孔体を設けたもの、特許文献１の第２実施例のように絞り部入口側に多数の極細管を設けたものがある。また、特許文献２の実施例５〜７のように絞り部入口側に細径管を束ねたハニカムパイプを設けたもの、特許文献２の実施例８〜１０のように絞り部入口側にモレキュラシーブスを設けたものなどを掲げることができる。また、絞り部に至るまでの冷媒流れをスムーズにするように入口側の流路の形状を変化させ、絞り部で急激な圧力変化を受けないようにした方法（以下従来Ｂ方法という）が知られている。その具体例としては、特許文献１の第１〜第５実施例及び特許文献２の実施例１〜１０のように弁孔をなすオリフィスの入口側内径を段階的にあるいはテーパ状に縮小させるもの、特許文献１の第４実施例のように弁孔をなすオリフィスの入口側内径をテーパ状に縮小させるとともにネジ切り溝を設けたものなどを掲げることができる。また、絞り部を２段階として２段階の絞り部間に中間圧力を発生させることにより、冷媒流動エネルギを分散させる方法（以下従来Ｃ方法という）が知られている。その具体例としては特許文献３を掲げることができる。また、絞り部に複数の冷媒通路を設けることにより冷媒の脈動を連続化しようとした方法（以下従来Ｄ方法という）が知られている。その具体例としては特許文献４を掲げることができる。
特開平７−１４６０３２号公報 特開平１１−３２５６５８号公報 特開平５−３２２３８１号公報 特開平５−２８８２８６号公報 In order to solve such problems, a method of making the refrigerant flow continuous in the throttle section by providing a collection of narrow passages on the inlet side of the throttle section to subdivide the bubbles into a gas-liquid mixed state (hereinafter, conventional) A method) is known. As a specific example thereof, a porous body is provided on the inlet side of the throttle part as in the first embodiment of Patent Document 1, and a number of ultrathin tubes are provided on the inlet side of the throttle part as in the second example of Patent Document 1. There is something. Further, a honeycomb pipe in which small diameter tubes are bundled on the inlet side of the throttle part as in Examples 5 to 7 of Patent Document 2, and a molecular sieve on the inlet side of the throttle part as in Examples 8 to 10 of Patent Document 2. It is possible to list things with a service. Also known is a method (hereinafter referred to as the conventional method B) in which the shape of the flow path on the inlet side is changed so as to smooth the refrigerant flow up to the constricted portion so that it does not receive a sudden pressure change at the constricted portion. It has been. As specific examples, the inlet side inner diameter of the orifice forming the valve hole is reduced stepwise or in a tapered manner as in the first to fifth embodiments of Patent Document 1 and Examples 1 to 10 of Patent Document 2. In addition, as in the fourth embodiment of Patent Document 1, the inlet side inner diameter of the orifice forming the valve hole can be reduced in a taper shape and a threaded groove can be provided. Further, there is known a method of dispersing refrigerant flow energy (hereinafter referred to as a conventional C method) by generating an intermediate pressure between two throttle portions with two throttle portions. As a specific example, Patent Document 3 can be listed. Further, there is known a method (hereinafter referred to as a conventional method D) which attempts to make the pulsation of the refrigerant continuous by providing a plurality of refrigerant passages in the throttle portion. As a specific example, Patent Document 4 can be listed.
JP-A-7-146032 Japanese Patent Laid-Open No. 11-325658 JP-A-5-322381 Japanese Patent Laid-Open No. 5-288286

しかしながら、従来Ａ方法は、大きな気泡を含んだ気液２相流の冷媒流を多数の細い通路を通過させることにより、気泡を細分化するものであって、細い通路に不純物が堆積しやすく、ごみ詰まりが生じやすい。また、多孔質体や、ハニカムパイプや、極細管や、モレキュラシーブスは、機械強度が弱く変形しやすいという問題もある。このため、従来Ａ方法は電動膨張弁の信頼性を維持することが困難であった。   However, the conventional method A is to subdivide the bubbles by passing a gas-liquid two-phase refrigerant flow containing large bubbles through a large number of thin passages, and impurities are likely to accumulate in the thin passages. Prone to clogging. In addition, porous bodies, honeycomb pipes, ultrathin tubes, and molecular sieves also have a problem that they are weak in mechanical strength and easily deformed. For this reason, it has been difficult for the conventional method A to maintain the reliability of the electric expansion valve.

また、従来Ｂ方法は、絞り部入口側の流路形状を変化させるだけでは、冷媒中に含まれた気泡を細分化して液冷媒に均一に混在することができず、絞り部における圧力変動を十分に低減することができなかった。   Further, in the conventional method B, it is not possible to subdivide bubbles contained in the refrigerant and mix them uniformly in the liquid refrigerant simply by changing the shape of the flow path on the inlet side of the throttle portion. It could not be reduced sufficiently.

また、従来Ｃ方法は、２段階に形成された絞り部間の圧力を中間圧力としているだけでは、減圧時に発生する運動エネルギを低減することはできるが、気液２相流時の流量変動を抑制する効果が小さい。このため、低騒音化しているものの「チュルチュル」音を回避することが困難であった。また、この従来Ｃ方法では、全閉時に２段の各絞り部を同時に全閉状態とすることが製作技術上困難であるので、全閉近傍状態においては両絞り部間を中間圧力に維持することが困難であった。   In addition, the conventional C method can reduce the kinetic energy generated at the time of pressure reduction only by setting the pressure between the throttle portions formed in two stages to an intermediate pressure, but the flow fluctuation during the gas-liquid two-phase flow can be reduced. Suppressive effect is small. For this reason, it is difficult to avoid the “church” sound although the noise is reduced. In addition, in this conventional C method, it is difficult in manufacturing technology to simultaneously make the two stages of the throttles fully closed when fully closed, so that the intermediate pressure is maintained between the throttles in the vicinity of the fully closed state. It was difficult.

また、従来Ｄ方法は、絞り部における全流路面積が大きくなり、冷媒流量制御における分解能が荒くなる。また、これを避けるために流路を微小にするとごみ詰まりあるいは噛み込みが生じるという問題があった。   Further, in the conventional method D, the total flow path area in the throttle portion becomes large, and the resolution in the refrigerant flow rate control becomes rough. In addition, if the flow path is made minute to avoid this, there is a problem that clogging or biting occurs.

本発明は、上記従来技術に存在する問題点に着目してなされたものであって、信頼性を損ねることなく、気液２相冷媒流が絞り部を通過することに伴う不連続な冷媒流動音と気液２相冷媒流が絞り部を通過することに伴う圧力変動に起因する振動音とを低減した膨張弁を提供することを目的とする。また、本発明は、この膨張弁を用いることにより膨張弁における冷媒通過音を低減した冷凍装置を提供することを目的とする。   The present invention has been made paying attention to the problems existing in the above-described conventional technology, and the discontinuous refrigerant flow accompanying the passage of the gas-liquid two-phase refrigerant flow through the throttle portion without impairing the reliability. An object of the present invention is to provide an expansion valve that reduces noise and vibration noise caused by pressure fluctuations caused by the passage of a gas-liquid two-phase refrigerant flow through a throttle. Another object of the present invention is to provide a refrigeration apparatus that uses this expansion valve to reduce refrigerant passing noise in the expansion valve.

本発明の第１の課題解決手段に係る膨張弁は、弁本体と、弁本体内部に形成された冷媒流通路と、弁本体内に収納された弁体と、冷媒流通路に形成された第１絞り部と、冷媒流通路における第１絞り部の上流側に形成された第２絞り部とを有する。また、弁本体は、冷媒流通路における冷媒の流れを仕切る第１仕切壁と、冷媒流通路の第１仕切壁の上流側における冷媒の流れを仕切る第２仕切壁とを備えている。さらに、第１仕切壁には第１弁孔が形成され、第２仕切壁には第２弁孔が形成されている。また、弁体は、外周面がテーパ状に形成され、かつ、このテーパ状の外周面が第１弁孔の弁座に当接する第１弁体部と外周面が第２弁孔の内周面に対向する第２弁体部とを備えた棒状部材からなる。第１絞り部は、第１弁孔の弁座に対し第１弁体部を進退させることにより、第１弁孔と第１弁体部との間に形成されるものであって、全閉可能かつ開度可変に形成されている。第２絞り部は、相互に対向する第２弁孔の内周面と弁体の第２弁体部の外周面との何れか一方に、弁体の進退方向に延びる複数の溝部が形成されたものである。そして、第２絞り部は、この複数の溝部とこの溝部に対向する第２弁孔の内周面又は第２弁体部の外周面とにより、複数の略独立の通路が形成されたものである。さらに、第２絞り部における第２弁孔の内周面又は第２弁体部の外周面の少なくとも何れか一方が、弁体の中心軸に対し傾斜するテーパ面に形成されている。第１の課題解決手段に係る膨張弁は、以上の構成を特徴とする。   An expansion valve according to a first problem-solving means of the present invention includes a valve main body, a refrigerant flow passage formed inside the valve main body, a valve body housed in the valve main body, and a first formed in the refrigerant flow passage. 1 throttle part and the 2nd throttle part formed in the upstream of the 1st throttle part in a refrigerant flow passage. The valve body includes a first partition wall that partitions the refrigerant flow in the refrigerant flow passage and a second partition wall that partitions the refrigerant flow on the upstream side of the first partition wall of the refrigerant flow passage. Further, a first valve hole is formed in the first partition wall, and a second valve hole is formed in the second partition wall. Further, the valve body has an outer peripheral surface formed in a tapered shape, and the outer peripheral surface of the first valve body portion and the outer peripheral surface of the second valve hole are in contact with the valve seat of the first valve hole. It consists of a rod-shaped member provided with the 2nd valve body part which opposes a surface. The first restrictor is formed between the first valve hole and the first valve body part by moving the first valve body part forward and backward with respect to the valve seat of the first valve hole, and is fully closed. The opening is variable and possible. The second throttle portion has a plurality of grooves extending in the advancing and retreating direction of the valve body on either the inner peripheral surface of the second valve hole facing each other or the outer peripheral surface of the second valve body portion of the valve body. It is a thing. The second throttle portion has a plurality of substantially independent passages formed by the plurality of groove portions and the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion facing the groove portions. is there. Further, at least one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion in the second throttle portion is formed as a tapered surface inclined with respect to the central axis of the valve body. The expansion valve according to the first problem solving means is characterized by the above configuration.

上記第１の課題解決手段に係る膨張弁によれば、第２絞り部から第１絞り部へ冷媒を流通させることにより、第１絞り部における絞り量を少なくし、第１絞り部を通過する冷媒の運動エネルギを少なくしている。これにより、第１絞り部における圧力変動を低減している。ここにおいて、第２絞り部は、第２弁体部と第２弁孔との間に形成された複数の略独立の通路により形成されているので、第１絞り部入口側においてスラグ流あるいはプラグ流における音を発生する圧力変動エネルギを分散して音発生エネルギの集中を排除することができる。また、この複数の独立の通路により気泡の細分化が行われる。この結果、第１の課題解決手段に係る膨張弁によれば、液冷媒とガス冷媒が交互に第１絞り部を通過することに伴う不連続な冷媒流動音、いわゆる「チュルチュル」音、及び冷媒流の圧力変動に起因する振動音が低減される。   According to the expansion valve according to the first problem solving means, the amount of throttling in the first throttling portion is reduced by passing the refrigerant from the second throttling portion to the first throttling portion, and passes through the first throttling portion. Reducing the kinetic energy of the refrigerant. Thereby, the pressure fluctuation in the first throttle part is reduced. Here, since the second throttle part is formed by a plurality of substantially independent passages formed between the second valve body part and the second valve hole, a slag flow or a plug is formed on the inlet side of the first throttle part. It is possible to disperse the pressure fluctuation energy that generates sound in the flow to eliminate concentration of sound generation energy. Further, the bubbles are subdivided by the plurality of independent passages. As a result, according to the expansion valve according to the first problem-solving means, the discontinuous refrigerant flow sound, the so-called “church sound”, and the refrigerant that accompany the liquid refrigerant and the gas refrigerant alternately passing through the first throttle portion, and the refrigerant Vibration noise caused by flow pressure fluctuations is reduced.

また、第１の課題解決手段に係る膨張弁において、複数の略独立の通路は、第２弁孔の内周面又は第２弁体部の外周面の何れか一方に弁体の進退方向に延びる複数の溝部を形成したものである。このため、弁体の進退により溝部と第２弁孔の内周面又は第２弁体部の外周面の重なり長さを変化させることができるとともに、第１絞り部の冷媒流通抵抗と第２絞り部の冷媒流通抵抗とを同時に変化させることができる。したがって、第１の課題解決手段に係る膨張弁によれば、膨張弁の負荷の変動に対し、第１絞り部と第２絞り部との冷媒流通抵抗の比を適正範囲に保持することが容易となり、幅広い運転範囲に対し安定的に膨張弁入口側の冷媒通過音を低減することができる。   Further, in the expansion valve according to the first problem solving means, the plurality of substantially independent passages are provided in either the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion in the advance / retreat direction of the valve body. A plurality of extending grooves are formed. For this reason, the overlap length of the groove portion and the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion can be changed by the advancement and retreat of the valve body, and the refrigerant flow resistance and the second restriction portion of the first throttle portion are changed. The refrigerant flow resistance of the throttle portion can be changed at the same time. Therefore, according to the expansion valve according to the first problem solving means, it is easy to maintain the ratio of the refrigerant flow resistance between the first throttle part and the second throttle part within an appropriate range with respect to fluctuations in the load of the expansion valve. Thus, the refrigerant passing sound at the inlet side of the expansion valve can be stably reduced over a wide operating range.

また、第１の課題解決手段に係る膨張弁においては、前記第２弁孔の内周面及び第２弁体部の外周面の少なくとも何れか一方がテーパ面に形成されている。このため、第２弁孔の内周面と第２弁体部の外周面との間にゴミが噛み込み、弁体の動作不良が起こるのを回避することができる。この間隙は、第２絞り部を最大絞り時に必要な最小寸法の間隙に設定されるものであって、通常弁体を進退させるのに支障を生じない程度の最小寸法とされる。また、第２弁孔の内周面及び第２弁体部の外周面をともに弁体の中心線と平行なストレートな面に形成したものでは、両面間の間隙は、弁体の進退位置に関係なく常に一定となる。このため、両面間の間隙に、冷媒流中に含まれるゴミが一端噛み込むと外れなくなり、ゴミが堆積して終には弁体の動作不良を招く恐れがある。ところが、上述のように、両面の何れか一方をテーパ面に形成した場合には、弁体を進退させて第２絞り部を開閉することにより、両面間の間隙が大小変化する。したがって、第１の課題解決手段に係る膨張弁によれば、第２絞り部を開いたときに、一旦噛み込んだゴミを流して除去することができ、弁体の動作不良を回避することができる。   In the expansion valve according to the first problem solving means, at least one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion is formed as a tapered surface. For this reason, it can be avoided that dust is caught between the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion, resulting in malfunction of the valve body. This gap is set to a minimum dimension required for the second throttle portion when the throttle is maximum, and is normally set to a minimum dimension that does not hinder the advancement and retraction of the valve body. In addition, in the case where both the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body part are formed on a straight surface parallel to the center line of the valve body, the gap between both surfaces is at the advanced / retracted position of the valve body. Regardless of whether it is constant or not. For this reason, if the dust contained in the refrigerant flow bites into the gap between both surfaces, it will not come off, and the dust will accumulate and eventually cause a malfunction of the valve body. However, as described above, when either one of the both surfaces is formed into a tapered surface, the gap between the both surfaces changes in size by moving the valve body forward and backward to open and close the second throttle portion. Therefore, according to the expansion valve according to the first problem solving means, when the second throttle part is opened, the dust that has been bitten can be removed by flowing, and malfunction of the valve element can be avoided. it can.

また、第１の課題解決手段に係る膨張弁においては、第１絞り部を全閉可能としているので、第１絞り部を全閉するまで必要な絞り量を確保することができる。また、従来Ａ方法のように第１絞り部の上流側で冷媒流の速度を低下させて細い通路に流すようなことがないので、ごみ詰まりの問題が発生しない。   Further, in the expansion valve according to the first problem solving means, since the first throttle portion can be fully closed, a necessary throttle amount can be ensured until the first throttle portion is fully closed. Further, unlike the conventional method A, the speed of the refrigerant flow is not reduced on the upstream side of the first throttle portion so as to flow through a narrow passage, so that the problem of clogging does not occur.

また、上記複数の略独立の通路は第２弁体部の外周面又は第２弁孔の内周面に上下方向に形成しているので、容易に製作することができる。
次に、本発明の第２の課題解決手段に係る膨張弁は、第１の課題解決手段の膨張弁と比較して、第１弁体部を第１弁孔に対向させて開度可変とした点、すなわち、第１絞り部を全閉可能としていない点で、本発明の第１の課題解決手段に係る膨張弁と相違する。したがって、第１の課題解決手段と同様に、第２絞り部から第１絞り部へ冷媒を流通させることにより、第１絞り部における圧力変動を低減することができる。また、複数の略独立の通路により形成される第２絞り部において音発生エネルギの集中を排除することにより、不連続な冷媒流動音及び冷媒流の圧力変動に起因する振動音が低減することができる。また、弁体の進退により、第１絞り部の冷媒流通抵抗と第２絞り部の冷媒流通抵抗とを同時に変化させることができる。また、第２弁孔の内周面及び第２弁体部の外周面の少なくとも何れか一方をテーパ面に形成しているので、第２弁孔の内周面と第２弁体部の外周面との間にゴミが噛み込み、弁体の動作不良が起こるのを回避することができる。 Further, the plurality of substantially independent passages are formed in the vertical direction on the outer peripheral surface of the second valve body part or the inner peripheral surface of the second valve hole, and therefore can be easily manufactured.
Next, in the expansion valve according to the second problem solving means of the present invention, the opening degree is variable by making the first valve body portion face the first valve hole as compared with the expansion valve of the first problem solving means. This is different from the expansion valve according to the first problem solving means of the present invention in that the first throttle part cannot be fully closed. Therefore, similarly to the first problem solving means, the pressure fluctuation in the first throttle portion can be reduced by circulating the refrigerant from the second throttle portion to the first throttle portion. Further, by eliminating the concentration of sound generation energy in the second throttle portion formed by a plurality of substantially independent passages, discontinuous refrigerant flow noise and vibration noise caused by refrigerant flow pressure fluctuations can be reduced. it can. Further, the refrigerant flow resistance of the first throttle part and the refrigerant flow resistance of the second throttle part can be changed simultaneously by the advancement and retreat of the valve body. In addition, since at least one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion is formed as a tapered surface, the inner peripheral surface of the second valve hole and the outer periphery of the second valve body portion It is possible to avoid the occurrence of a malfunction of the valve body due to dust being caught between the surfaces.

また、このような第１及び第２の課題解決手段に係る膨張弁において、複数の溝部を等間隔に形成することが好ましい。このようにすると、複数の独立の通路を等間隔に形成することができる。これにより、複数の独立の通路に対する冷媒流の分散を均等に行うことができるとともに、エネルギ分散効果を最大限に発揮させることができる。   In the expansion valve according to the first and second problem solving means, it is preferable to form a plurality of groove portions at equal intervals. In this way, a plurality of independent passages can be formed at equal intervals. Thereby, while being able to perform dispersion | distribution of the refrigerant | coolant flow equally with respect to a several independent channel | path, the energy dispersion | distribution effect can be exhibited to the maximum.

また、第２弁孔の内周面及び第２弁体部の外周面をともに互いに平行なテーパ面に形成してもよい。仮に、第２弁孔の内周面及び第２弁体部の外周面の一方のみがテーパ面であったり、テーパ角度が異なったりしていると、第２絞り部の開度を大きくしたときに両面間の間隙が大きくなり、複数の溝部による冷媒流分散効果が低下することが考えられる。これに対し上述のように第２弁孔の内周面及び第２弁体部の外周面の双方を互いに平行なテーパ面に形成すると、第２絞り部の開度調節時の第２弁孔の内周面と第２弁体部の外周面との間の間隙の変化を少なくすることができる。したがって、第２絞り部の弁開度に関係なく複数の独立の通路による冷媒分散が適切に行われ、冷媒通過音の低減効果を発揮させることができる。   Moreover, you may form both the internal peripheral surface of a 2nd valve hole, and the outer peripheral surface of a 2nd valve body part in a mutually parallel taper surface. If only one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion is a tapered surface or the taper angle is different, the opening degree of the second throttle portion is increased. In addition, it is considered that the gap between both surfaces becomes large and the refrigerant flow dispersion effect by the plurality of grooves is reduced. On the other hand, when both the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion are formed in parallel taper surfaces as described above, the second valve hole at the time of adjusting the opening degree of the second throttle portion. The change in the gap between the inner circumferential surface of the first valve body and the outer circumferential surface of the second valve body portion can be reduced. Therefore, refrigerant dispersion by a plurality of independent passages is appropriately performed regardless of the valve opening degree of the second throttle part, and the effect of reducing the refrigerant passing sound can be exhibited.

また、上記第１の課題解決手段及び第２の課題解決手段に係る膨張弁において、次のように構成してもよい。前記弁体は、前記棒状部材の先端部に第１弁体部が形成され、前記棒状部材の中間部に第２弁体部が形成されたものとする。また、第２弁体部の外周面及び第２弁孔の内周面は弁体の先端部に向かって先細のテーパ面に形成する。このように構成すると、第２絞り部を構成する第２弁体部の外周面及び第２弁孔の内周面を、弁体の軸方向に長くすることができるとともに、これら面の直径を大きくすることができる。したがって、溝部を長くすることができるとともに、溝部の形状、本数などの設計上の制約を少なくすることができる。   The expansion valve according to the first problem solving means and the second problem solving means may be configured as follows. The said valve body shall have the 1st valve body part formed in the front-end | tip part of the said rod-shaped member, and the 2nd valve body part was formed in the intermediate part of the said rod-shaped member. Further, the outer peripheral surface of the second valve body part and the inner peripheral surface of the second valve hole are formed in a tapered surface that tapers toward the tip part of the valve body. If comprised in this way, while the outer peripheral surface of the 2nd valve body part which comprises a 2nd throttle part, and the internal peripheral surface of a 2nd valve hole can be lengthened to the axial direction of a valve body, the diameter of these surfaces is made. Can be bigger. Therefore, the groove portion can be lengthened and design restrictions such as the shape and number of the groove portions can be reduced.

また、前記複数の溝部を、第２弁体部の外周面を構成するテーパ面に形成してもよい。このように構成すると、棒状部材の外周面に溝部を加工することができるので、溝部の加工作業が容易になる。   Moreover, you may form the said some groove part in the taper surface which comprises the outer peripheral surface of a 2nd valve body part. If comprised in this way, since a groove part can be processed into the outer peripheral surface of a rod-shaped member, the process operation of a groove part becomes easy.

また、前記第２弁体部の外周面を構成するテーパ面の上流側端部は、第２絞り部の最小から最大の何れの開度においても第２弁孔内に位置するように構成することが好ましい。このように構成することにより、次のような作用効果を奏することができる。第２弁体部の外周面を構成するテーパ面が第２弁孔の上流側に突出していると、複数の溝部により形成される通路で気泡が細分化される前に、第２弁孔の上流側に突出している第２弁体部の外周面を構成するテーパ面で冷媒流が乱される。しかし、この乱れは気泡の細分化には寄与せずに冷媒流れを乱すため、新たな騒音発生の要因を形成することになる。したがって、第２弁体部の外周面を構成するテーパ面が第２弁孔の上流側に突出しないように形成することにより、より一層冷媒通過音を軽減することができる。   Further, the upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion is configured to be located in the second valve hole at any opening degree from the minimum to the maximum of the second throttle portion. It is preferable. By comprising in this way, the following effects can be obtained. If the taper surface constituting the outer peripheral surface of the second valve body portion protrudes upstream of the second valve hole, before the bubbles are subdivided in the passage formed by the plurality of groove portions, the second valve hole The refrigerant flow is disturbed by a tapered surface that constitutes the outer peripheral surface of the second valve body portion projecting upstream. However, since this disturbance does not contribute to the fragmentation of bubbles and disturbs the refrigerant flow, a new noise generation factor is formed. Therefore, by forming the tapered surface constituting the outer peripheral surface of the second valve body portion so as not to protrude to the upstream side of the second valve hole, it is possible to further reduce the refrigerant passing sound.

また、第２絞り部から第１弁孔に至る冷媒通路における第１弁孔の入口側部に拡大空間部を形成する。そして、第２絞り部の最小から最大の何れの開度においても、第２弁体部の外周面を構成するテーパ面の下流側端部が拡大空間部内に位置するように構成することが好ましい。第２絞り部から第１弁孔に至る冷媒通路において、第１弁孔の入口側部に拡大空間部を形成することにより、第２絞り部通過後の冷媒流が拡大部で乱されて、気泡の細分化がさらに進められる。特に、この場合において、第２弁体部の外周面を構成するテーパ面の下流側端部が第２弁孔内に位置するように形成されている場合は、第２弁孔から拡大空間部に流出する際の流れが急激に変動するため抵抗が大きくなり、新たな騒音発生要因を発生することになる。しかしながら、本発明では、第２弁体部の外周面を構成するテーパ面の下流側端部を拡大空間部内に位置するように構成しているので、溝部で整流された冷媒を拡大空間部内にスムーズに流入させることができる。この結果、拡大空間内で２相流を掻き乱して気泡を細分化することができ、冷媒通過音をより一層軽減することができる。   In addition, an enlarged space portion is formed at the inlet side portion of the first valve hole in the refrigerant passage extending from the second throttle portion to the first valve hole. And it is preferable to comprise so that the downstream end part of the taper surface which comprises the outer peripheral surface of a 2nd valve body part may be located in an expansion space part in any opening degree from the minimum of a 2nd aperture | diaphragm | squeeze part. . In the refrigerant passage from the second throttle part to the first valve hole, by forming an enlarged space part at the inlet side part of the first valve hole, the refrigerant flow after passing through the second throttle part is disturbed by the enlarged part, Bubble fragmentation is further advanced. In particular, in this case, when the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion is formed in the second valve hole, the enlarged space portion extends from the second valve hole. Since the flow at the time of outflow fluctuates rapidly, the resistance increases and a new noise generation factor is generated. However, in the present invention, since the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion is positioned in the enlarged space portion, the refrigerant rectified in the groove portion is placed in the enlarged space portion. It can flow smoothly. As a result, the two-phase flow can be disturbed in the expansion space to subdivide the bubbles, and the refrigerant passing sound can be further reduced.

また、第１絞り部及び第２絞り部の何れの開度においても、第１絞り部入口側における第１弁体部と第１弁孔との間隙を、前記第２絞り部における第２弁体部と第２弁孔との最小間隙より小さく形成することが好ましい。ここで、第１絞り部入口側における第１弁体部と第１弁孔との間隙とは、第１弁体部のテーパ面に垂直な方向で測ったこのテーパ面から第１弁孔の入口側角部までの距離をいう。また、第２絞り部における第２弁体部と第２弁孔との最小間隙とは、第２弁体部のテーパ面に垂直な方向で測ったこのテーパ面から第２弁孔のテーパ面までの距離のうちの最小距離をいう。この最小距離となる位置は、第２弁体部のテーパ面のテーパ角度と第２弁孔のテーパ面のテーパ角度と比較してどちらが大きいかにより異なってくる。すなわち、第２弁体部のテーパ面のテーパ角度が第２弁孔のテーパ面のテーパ角度より大きい場合は、第２弁体部のテーパ面の上流側端部の位置であり、小さい場合は第２弁孔の下流側端部の位置であり、同一の場合はいずれの位置でも同一となる。このようにすれば、第１絞り部の絞り効果を第２絞り部の絞り効果より大きくし、第１絞り部を主絞り部として作用させることができるとともに、第２絞り部を設けることに起因するゴミ詰まりの確率が高くなることもない。   Further, at any opening degree of the first throttle part and the second throttle part, the gap between the first valve body part and the first valve hole on the inlet side of the first throttle part is defined as the second valve in the second throttle part. It is preferable to form it smaller than the minimum gap between the body part and the second valve hole. Here, the gap between the first valve body part and the first valve hole on the inlet side of the first throttle part is the taper surface measured in the direction perpendicular to the taper surface of the first valve body part. The distance to the entrance corner. Further, the minimum gap between the second valve body portion and the second valve hole in the second throttle portion is a taper surface of the second valve hole measured from the taper surface measured in a direction perpendicular to the taper surface of the second valve body portion. The minimum distance among the distances up to. The position of the minimum distance differs depending on which is greater than the taper angle of the taper surface of the second valve body part and the taper angle of the taper surface of the second valve hole. That is, when the taper angle of the taper surface of the second valve body part is larger than the taper angle of the taper surface of the second valve hole, it is the position of the upstream end of the taper surface of the second valve body part. This is the position of the downstream end of the second valve hole, and in the same case, it is the same at any position. In this way, the aperture effect of the first aperture section can be made larger than the aperture effect of the second aperture section, and the first aperture section can act as the main aperture section and the second aperture section is provided. The probability of clogging garbage will not increase.

また、前記第２弁体部の外周面を成すテーパ面及び第２弁孔の内周面を成すテーパ面は、同一のテーパ角度に形成され、さらに、前記第１弁体部の外周面を構成するテーパ面のテーパ角度は、第２弁孔の内周面を成すテーパ面のテーパ角度より大きくすることが好ましい。このようにすれば、弁体の進退に伴う第１絞り部の絞り効果の変化を第２絞り部のそれより大きくすることができる。   The tapered surface forming the outer peripheral surface of the second valve body portion and the tapered surface forming the inner peripheral surface of the second valve hole are formed at the same taper angle, and further, the outer peripheral surface of the first valve body portion is The taper angle of the taper surface to be formed is preferably larger than the taper angle of the taper surface forming the inner peripheral surface of the second valve hole. In this way, it is possible to make the change in the throttling effect of the first throttling portion accompanying the advancement and retraction of the valve body larger than that of the second throttling portion.

また、この場合における第２弁孔の内周面を成すテーパ面のテーパ角度は、略５度〜略６０度とすることが好ましい。下限を略５度としたのは、第２絞り部が全開に向かうときに、複数の溝部のネジ山とこのネジ山に対向する第２弁孔の内周面との間隙に噛み込んだゴミを除去可能とする下限の値である。また、上限を略６０度としたのは、複数の溝部の必要長さから割り出された十分条件値である。   In this case, the taper angle of the tapered surface forming the inner peripheral surface of the second valve hole is preferably about 5 degrees to about 60 degrees. The lower limit is set to approximately 5 degrees when the second throttle portion is fully opened, and the dust caught in the gap between the threads of the plurality of grooves and the inner peripheral surface of the second valve hole facing the threads. This is the lower limit value that makes it possible to remove. The upper limit of about 60 degrees is a sufficient condition value calculated from the required lengths of the plurality of grooves.

また、前記弁体における前記第２弁体部の上流側端部に連結される連結部の直径を、第２弁体部を構成するテーパ面における最大外周部の直径より小さくすることが好ましい。このように構成すれば、弁本体内部に流入する冷媒流がこの連結棒により阻害されて、第２絞り部に流入する前に乱されることが軽減されるので、冷媒通過音を大きくする要因を排除することができる。   Moreover, it is preferable to make the diameter of the connection part connected with the upstream edge part of the said 2nd valve body part in the said valve body smaller than the diameter of the largest outer peripheral part in the taper surface which comprises a 2nd valve body part. According to this structure, the refrigerant flow flowing into the valve body is obstructed by the connecting rod and is disturbed before flowing into the second throttle portion. Can be eliminated.

また、前記第２弁体部の外周面の上流側端部と前記弁体における前記第２弁体部の上流側端部に連結される連結部と間に、第２弁体部の外周面の上流側端部から前記連結部の外周面に向かってテーパ状に縮径する第２異径接合部を形成することが好ましい。このようにすると、弁本体内部に流入した冷媒流が第２絞り部に流入するまでの乱れがより少なくなる。したがって、冷媒通過音を大きくする要因をさらに排除することができる。   In addition, the outer peripheral surface of the second valve body portion between the upstream end portion of the outer peripheral surface of the second valve body portion and the connecting portion connected to the upstream end portion of the second valve body portion in the valve body. It is preferable to form the 2nd different diameter joint part which diameter-reduces in a taper shape toward the outer peripheral surface of the said connection part from the upstream edge part. If it does in this way, the disturbance until the refrigerant | coolant flow which flowed in the inside of a valve main body flows in into a 2nd throttle part will become less. Therefore, it is possible to further eliminate the factor that increases the refrigerant passing sound.

また、前記第２弁体部の外周面の下流側端部と第１弁体部の外周面の上流側端部との間に、第２弁体部の外周面の下流側端部から前記第１弁体部の外周面の上流側端部に向かってテーパ状に縮径する第１異径接合部を形成する。さらに、この第１異径接合部のテーパ角度を前記第１弁体部のテーパ状外周面のテーパ角度より大きくすることが好ましい。このような第１異径接合部を形成することにより、弁体の長さを長くすることなく、第１弁孔の大きさ及び第２弁孔の大きさをそれぞれに適した直径に形成することができる。   Further, between the downstream end portion of the outer peripheral surface of the second valve body portion and the upstream end portion of the outer peripheral surface of the first valve body portion, from the downstream end portion of the outer peripheral surface of the second valve body portion, A first different-diameter joining portion that is tapered toward the upstream end portion of the outer peripheral surface of the first valve body portion is formed. Furthermore, it is preferable that the taper angle of the first different diameter joint portion is larger than the taper angle of the tapered outer peripheral surface of the first valve body portion. By forming such a first different diameter joint portion, the size of the first valve hole and the size of the second valve hole are formed to have appropriate diameters without increasing the length of the valve body. be able to.

また、本発明に係る冷凍装置は、上記膨張弁を用いたことを特徴とする。この冷凍装置では膨張弁における冷媒通過音を低減し静粛な運転を行うことができる。   Moreover, the refrigeration apparatus according to the present invention uses the above expansion valve. In this refrigeration apparatus, it is possible to reduce the refrigerant passing sound in the expansion valve and perform a quiet operation.

本発明によれば、第１絞り部の上流側に第２絞り部を設けることにより、第１絞り部における圧力変動を低減することができる。また、第２絞り部において音を発生するエネルギが分散される。また、第２絞り部における複数の独立の通路により気泡の細分化が行われる。このような作用が総合され、液冷媒とガス冷媒が交互に第１絞り部を通過することに伴う不連続な冷媒流動音、いわゆる「チュルチュル」音、及び冷媒流の圧力変動に起因する振動音が低減される。また、複数の略独立の通路が第２弁孔の内周面又は第２弁体部の外周面の何れか一方に弁体の進退方向に延びる複数の溝部から形成されているので、第１絞り部の冷媒流通抵抗と第２絞り部の冷媒流通抵抗とを同時に変化させることができ、幅広い運転範囲に対し安定的に膨張弁入口側の冷媒通過音を低減することができる。第２弁孔の内周面及び第２弁体部の外周面の少なくとも何れか一方をテーパ面に形成しているので、弁体の動作不良を回避することができる。また、このような膨張弁を利用した冷凍装置では膨張弁における冷媒通過音を低減し静粛な運転を行うことができる。   According to the present invention, it is possible to reduce the pressure fluctuation in the first throttle portion by providing the second throttle portion on the upstream side of the first throttle portion. In addition, the energy for generating sound is dispersed in the second diaphragm. Further, the bubbles are subdivided by a plurality of independent passages in the second throttle part. These actions are combined, and the discontinuous refrigerant flow sound that accompanies the passage of the liquid refrigerant and the gas refrigerant alternately through the first throttle part, the so-called “church” sound, and the vibration sound caused by the pressure fluctuation of the refrigerant flow Is reduced. Further, the plurality of substantially independent passages are formed on the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion from a plurality of groove portions extending in the advance / retreat direction of the valve body. The refrigerant flow resistance of the throttle part and the refrigerant flow resistance of the second throttle part can be changed at the same time, and the refrigerant passing sound on the expansion valve inlet side can be stably reduced over a wide operating range. Since at least one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion is formed as a tapered surface, it is possible to avoid malfunction of the valve body. Moreover, in the refrigeration apparatus using such an expansion valve, it is possible to reduce the refrigerant passing sound in the expansion valve and perform a quiet operation.

以下この発明を具体化した各実施の形態について、図面に基づいて説明する。なお、これら説明において上下左右方向をいうときは、各実施の形態に係る膨張弁の縦断面図における上下左右方向をいうものとする。また、これら縦断面図における白抜き矢印は冷媒の流れ方向を示すものとする。また、各実施の形態の説明においては、パルスモータなどの弁体駆動部については、図示及びその説明を省略する。   Embodiments of the present invention will be described below with reference to the drawings. In these descriptions, the vertical and horizontal directions refer to the vertical and horizontal directions in the longitudinal sectional view of the expansion valve according to each embodiment. Moreover, the white arrow in these longitudinal cross-sectional views shall show the flow direction of a refrigerant | coolant. In the description of each embodiment, the illustration and description of a valve body drive unit such as a pulse motor are omitted.

（実施の形態１）
以下に、この発明を具体化した実施の形態１に係る膨張弁を図１及び図２に基づいて説明する。図１は実施の形態１に係る膨張弁の縦断面図であり、図２は同図におけるＡ−Ａ矢視断面図である。 (Embodiment 1)
Hereinafter, an expansion valve according to Embodiment 1 embodying the present invention will be described with reference to FIGS. 1 and 2. 1 is a longitudinal sectional view of an expansion valve according to Embodiment 1, and FIG. 2 is a sectional view taken along the line AA in FIG.

実施の形態１に係る膨張弁は、例えば前述の図９に示したような冷媒回路に使用するものである。
この膨張弁は、図１に示すように、弁本体１と、弁本体１内に形成された冷媒流通路２と、弁本体１内に収納された弁体３とを備えている。さらに、この膨張弁では、弁本体１の内部に第１絞り部４と第２絞り部５とを形成するために、第１仕切壁６と第２仕切壁７とが設けられている。第１仕切壁６は、冷媒流通路２の中間部で冷媒流れを仕切るように水平方向に形成された壁高さの大きい仕切壁である。第２仕切壁７は、冷媒流通路２の出口側で冷媒流れを仕切るように水平方向に形成された壁高さの小さい仕切壁である。そして、第１仕切壁６には孔径の大きい第１弁孔８が形成され、第２仕切壁７には孔径の小さい第２弁孔９が形成されている。 The expansion valve according to Embodiment 1 is used, for example, in the refrigerant circuit as shown in FIG.
As shown in FIG. 1, the expansion valve includes a valve body 1, a refrigerant flow passage 2 formed in the valve body 1, and a valve body 3 accommodated in the valve body 1. Further, in this expansion valve, a first partition wall 6 and a second partition wall 7 are provided in order to form the first throttle portion 4 and the second throttle portion 5 inside the valve body 1. The first partition wall 6 is a partition wall having a large wall height that is formed in the horizontal direction so as to partition the refrigerant flow at an intermediate portion of the refrigerant flow passage 2. The second partition wall 7 is a partition wall having a small wall height formed in the horizontal direction so as to partition the refrigerant flow on the outlet side of the refrigerant flow passage 2. A first valve hole 8 having a large hole diameter is formed in the first partition wall 6, and a second valve hole 9 having a small hole diameter is formed in the second partition wall 7.

弁本体１は、軸心を上下方向として略円筒状に形成され、内部には上下方向の冷媒流通路２が形成されている。また、弁本体１、冷媒流通路２に繋がる出入口として入口ポート１ａと出口ポート１ｂの二つのポートを備えている。入口ポート１ａは弁本体１の下部に設けられ、出口ポート１ｂは弁本体１の側壁に設けられている。したがって、冷媒は、弁本体１内において下方から上方に流れるように構成されている。なお、入口ポート１ａには室外コイルと膨張弁とを接続する液管１０が接続され、出口ポート１ｂには膨張弁と室内コイルとを連絡する配管１１が接続されている。   The valve main body 1 is formed in a substantially cylindrical shape with an axial center as a vertical direction, and a vertical refrigerant flow passage 2 is formed therein. Further, two ports, an inlet port 1a and an outlet port 1b, are provided as inlets and outlets connected to the valve body 1 and the refrigerant flow passage 2. The inlet port 1 a is provided in the lower part of the valve body 1, and the outlet port 1 b is provided in the side wall of the valve body 1. Therefore, the refrigerant is configured to flow from below to above in the valve body 1. A liquid pipe 10 that connects the outdoor coil and the expansion valve is connected to the inlet port 1a, and a pipe 11 that connects the expansion valve and the indoor coil is connected to the outlet port 1b.

弁体３は、冷媒流通路２と同心に配した略円柱体の棒状部材から形成されている。また、弁体３は、上部に連結部１２、中間部に第１弁体部１３、下部に第２弁体部１４を備えている。第１弁体部１３は、連結部１２の下方に連続して形成されたものであって、下方向に先細のテーパ面を外周面としている。また、第２弁体部１４は、第１弁体部１３の下方に連続して形成されたものであって、下方向に先細のテーパ面を外周面としている。弁体３の中心線に対する外周面のテーパ角度は、第１弁体部１３のテーパ面の方が大きくなっている。そして、この弁体３は、図示しないパルスモータを駆動源として上下に駆動制御されるように構成されている。   The valve body 3 is formed of a substantially cylindrical rod-shaped member that is arranged concentrically with the refrigerant flow passage 2. Further, the valve body 3 includes a connecting portion 12 at an upper portion, a first valve body portion 13 at an intermediate portion, and a second valve body portion 14 at a lower portion. The 1st valve body part 13 is continuously formed under the connection part 12, Comprising: The taper surface tapered in the downward direction is made into the outer peripheral surface. Moreover, the 2nd valve body part 14 is continuously formed below the 1st valve body part 13, Comprising: The taper taper surface is made into the outer peripheral surface in the downward direction. The taper angle of the outer peripheral surface with respect to the center line of the valve body 3 is larger on the taper surface of the first valve body portion 13. The valve body 3 is configured to be driven up and down using a pulse motor (not shown) as a drive source.

第１絞り部４は、第１弁孔８に対し弁体３の第１弁体部１３を上下方向に進退させることにより、第１弁体部１３の外周面であるテーパ面と弁座（第１弁孔８の上端角部）との間に開度可変、かつ全閉可能な絞りを形成したものである。   The first throttle portion 4 moves the first valve body portion 13 of the valve body 3 up and down in the vertical direction with respect to the first valve hole 8, thereby forming a tapered surface and a valve seat (the outer peripheral surface of the first valve body portion 13). A throttle that is variable in opening and can be fully closed is formed between the first valve hole 8 and the upper end corner of the first valve hole 8.

また、第２絞り部５は、第２弁体部１４のテーパ状をなす外周面を第２弁孔９の内周面に対向させて配置し、第２弁体部１４の外周面と第２弁孔９の内周面との間に複数の略独立の通路１６を形成したものであって、第１絞り部４の上流側に形成されている。また、第２弁孔９は、図１及び図２からよく分かるように、第２弁孔９の表面部に複数の（この場合４個の）独立した溝部１５が略等間隔に形成されている。この溝部１５は断面形状が略３角形に形成されている。これにより、第２弁孔９と第２弁体部１４との間には複数の通路１６（この場合４個）が形成される。これにより、第２絞り部５を形成する通路は、断面積が一定の、前述の複数の略独立の通路１６が形成されている。   The second throttle portion 5 is arranged with the outer peripheral surface forming the taper shape of the second valve body portion 14 facing the inner peripheral surface of the second valve hole 9, and the second throttle body portion 5 and the outer peripheral surface of the second valve body portion 14 are A plurality of substantially independent passages 16 are formed between the inner surface of the two valve holes 9 and are formed on the upstream side of the first throttle portion 4. Further, as can be seen from FIGS. 1 and 2, the second valve hole 9 has a plurality of (in this case, four) independent grooves 15 formed at substantially equal intervals on the surface of the second valve hole 9. Yes. The groove 15 has a substantially triangular shape in cross section. Thereby, a plurality of passages 16 (four in this case) are formed between the second valve hole 9 and the second valve body portion 14. Thus, the plurality of substantially independent passages 16 having a constant cross-sectional area are formed in the passages forming the second throttle portion 5.

また、この実施の形態においては、弁体３を軸方向に進退制御することにより、溝部１５と第２弁体部１４との重なり長さ（すなわち通路１６の長さ）が、第１絞り部４の弁開度とともに変化するように第２弁体部１４の上下方向の寸法が設定されている。このような構成により、この実施の形態においては、第１絞り部４と第２絞り部５とは、冷媒流通抵抗が同時に増減するようにそれぞれ冷媒流通抵抗可変に構成されている。   Further, in this embodiment, the valve body 3 is controlled to advance and retreat in the axial direction, whereby the overlapping length of the groove portion 15 and the second valve body portion 14 (that is, the length of the passage 16) is the first throttle portion. The vertical dimension of the second valve body portion 14 is set so as to change with the valve opening of 4. With such a configuration, in this embodiment, the first throttle unit 4 and the second throttle unit 5 are each configured to have a variable refrigerant flow resistance so that the refrigerant flow resistance increases and decreases simultaneously.

実施の形態１の膨張弁は、以上のごとく形成されているので、次のような作用効果を奏する。
入口ポート１ａから流入した液冷媒は、第２絞り部５にて減圧され、第１絞り部４においてさらに大きく減圧される。第１絞り部４で減圧された冷媒は出口ポート１ｂから配管系に流出する。 Since the expansion valve of the first embodiment is formed as described above, the following operational effects can be obtained.
The liquid refrigerant flowing in from the inlet port 1a is depressurized by the second throttle unit 5 and further depressurized by the first throttle unit 4. The refrigerant decompressed by the first throttle 4 flows out from the outlet port 1b to the piping system.

また、入口ポート１ａからスラグ流あるいはプラグ流が流入してきた場合、第２絞り部５から第１絞り部４へ冷媒を流通させることにより、第１絞り部４における絞り量を少なくし、第１絞り部４を通過する冷媒の運動エネルギを少なくしている。これにより、第１絞り部４における圧力変動を低減することができる。特に、第２絞り部５は、第２弁体部１４と第２弁孔９との間に形成された複数の略独立の通路１６により形成されているので、第１絞り部４入口側においてスラグ流あるいはプラグ流における音を発生する圧力変動エネルギを分散して音発生エネルギの集中を排除することができる。また、この複数の独立の通路１６を通過することにより気泡の細分化が行われる。この結果、液冷媒とガス冷媒が交互に第１絞り部４を通過することに起因する不連続な冷媒流動音、いわゆる「チュルチュル」音、及び冷媒流の圧力変動に起因する振動音が低減される。   Further, when a slag flow or a plug flow flows in from the inlet port 1a, the amount of throttle in the first throttle unit 4 is reduced by flowing the refrigerant from the second throttle unit 5 to the first throttle unit 4, and the first throttle unit 4 is reduced. The kinetic energy of the refrigerant passing through the throttle unit 4 is reduced. Thereby, the pressure fluctuation in the 1st aperture | diaphragm | squeeze part 4 can be reduced. In particular, since the second throttle portion 5 is formed by a plurality of substantially independent passages 16 formed between the second valve body portion 14 and the second valve hole 9, on the inlet side of the first throttle portion 4 It is possible to disperse the pressure fluctuation energy that generates the sound in the slag flow or the plug flow to eliminate the concentration of the sound generation energy. Further, the bubbles are subdivided by passing through the plurality of independent passages 16. As a result, discontinuous refrigerant flow noise caused by alternately passing liquid refrigerant and gas refrigerant through the first throttle 4, so-called “church” noise, and vibration noise caused by pressure fluctuations in the refrigerant flow are reduced. The

また、複数の略独立の通路１６は、第２弁孔９の内周面に弁体３の進退方向に延びる複数の溝部１５を形成して構成されているので、弁体３の進退により、溝部１５と第２弁体部１４の外周面との進退方向における重なり長さが変化する。これにより、第１絞り部４の冷媒流通抵抗と第２絞り部５の冷媒流通抵抗とを同時に変化させることができる。したがって、膨張弁の負荷の変動に対し、第１絞り部４と第２絞り部５との冷媒流通抵抗の比を適正範囲に保持することが容易となり、幅広い運転範囲に対し安定的に膨張弁の冷媒通過音を低減することができる。   The plurality of substantially independent passages 16 are formed by forming a plurality of groove portions 15 extending in the advancing / retreating direction of the valve body 3 on the inner peripheral surface of the second valve hole 9. The overlap length in the advancing / retreating direction of the groove portion 15 and the outer peripheral surface of the second valve body portion 14 changes. Thereby, the refrigerant | coolant circulation resistance of the 1st aperture | diaphragm | squeeze part 4 and the refrigerant | coolant circulation resistance of the 2nd aperture | diaphragm | squeeze part 5 can be changed simultaneously. Therefore, it becomes easy to maintain the ratio of the refrigerant flow resistance between the first throttle part 4 and the second throttle part 5 in an appropriate range with respect to fluctuations in the load of the expansion valve, and the expansion valve is stable over a wide operating range. The refrigerant passing noise can be reduced.

また、第２弁孔９の内周面及び第２弁体部１４の外周面をテーパ面に形成しているので、第２弁孔９の内周面と第２弁体部１４の外周面との間にゴミが噛み込み、弁体３の動作不良が起こるのを回避することができる。この間隙は、第２絞り部５を最も絞るときに必要な最小寸法の間隙に設定されるものであって、通常の設計では、弁体３を進退させるのに支障を生じない最小寸法となる。また、第２弁孔９の内周面及び第２弁体部１４の外周面を共に弁体３の中心線と平行なストレートな面に形成したものでは、両面間の間隙は、弁体３の進退位置に関係なく常に一定となる。このため、両面間の間隙に冷媒流中に含まれるゴミが一端噛み込むと、外れなくなり、ゴミが堆積して終には弁体３の動作不良を招く恐れがある。ところが、上述のように、両面をテーパ面に形成しているので、弁体３を進退させて第２絞り部５の開度を変化させることにより、両面間の間隙が大小変化する。したがって、第２絞り部５を開いたときに、一旦噛み込んだゴミを流して除去することができ、弁体３の動作不良を回避することができる。   Further, since the inner peripheral surface of the second valve hole 9 and the outer peripheral surface of the second valve body portion 14 are formed as tapered surfaces, the inner peripheral surface of the second valve hole 9 and the outer peripheral surface of the second valve body portion 14 are formed. It is possible to avoid the occurrence of a malfunction of the valve body 3 due to dust biting between the two. The gap is set to a minimum dimension required when the second throttle portion 5 is most narrowed. In a normal design, the gap is a minimum dimension that does not hinder the valve body 3 from moving forward and backward. . In the case where both the inner peripheral surface of the second valve hole 9 and the outer peripheral surface of the second valve body portion 14 are formed on a straight surface parallel to the center line of the valve body 3, the gap between both surfaces is the valve body 3. Regardless of the forward / backward position, it is always constant. For this reason, if the dust contained in the refrigerant flow bites into the gap between both surfaces, it will not come off, and the dust may accumulate and eventually cause a malfunction of the valve body 3. However, since both surfaces are formed as tapered surfaces as described above, the gap between the both surfaces changes by moving the valve body 3 forward and backward to change the opening degree of the second throttle portion 5. Therefore, when the second throttle portion 5 is opened, the dust that has been bitten can be removed by flowing, and malfunction of the valve body 3 can be avoided.

また、第２弁孔９の内周面及び第２弁体部１４の外周面の双方を互いに平行なテーパ面にしているので、第２絞り部５の開度により第２弁孔９の内周面と第２弁体部１４の外周面との間の間隙の変化を少なくすることができる。したがって、第２絞り部５の弁開度に関係なく複数の独立の通路１６による冷媒分散が適切に行われ、冷媒通過音の低減効果を発揮させることができる。また、複数の溝部１５を等間隔に形成しているので、複数の独立の通路１６が等間隔に形成される。これにより、複数の独立の通路に対する冷媒流分散が均等に行われてエネルギ分散効果を最大限に発揮させることができる。   In addition, since both the inner peripheral surface of the second valve hole 9 and the outer peripheral surface of the second valve body portion 14 are tapered surfaces parallel to each other, the inner diameter of the second valve hole 9 depends on the opening of the second throttle portion 5. A change in the gap between the peripheral surface and the outer peripheral surface of the second valve body portion 14 can be reduced. Therefore, refrigerant dispersion by the plurality of independent passages 16 is appropriately performed regardless of the valve opening degree of the second throttle portion 5, and the effect of reducing the refrigerant passing sound can be exhibited. Moreover, since the several groove part 15 is formed at equal intervals, the several independent channel | path 16 is formed at equal intervals. Thereby, the refrigerant | coolant flow dispersion | distribution with respect to a several independent channel | path is performed uniformly, and an energy dispersion | distribution effect can be exhibited to the maximum.

また、複数の略独立の通路１６は、第２弁孔９の内周面に上下方向に形成されているので、容易に製作することができる。
また、第１絞り部４を全閉可能としているので、第１絞り部４を全閉するまで必要な絞り量を確保することができる。また、従来Ａ方法のように第１絞り部４の上流側で冷媒流の速度を低下させて細い通路に流すようなことがないので、ごみ詰まりの問題が発生しない。 Moreover, since the several substantially independent channel | path 16 is formed in the up-down direction in the internal peripheral surface of the 2nd valve hole 9, it can be manufactured easily.
In addition, since the first throttle unit 4 can be fully closed, a necessary throttle amount can be ensured until the first throttle unit 4 is fully closed. Further, unlike the conventional method A, the speed of the refrigerant flow is not reduced on the upstream side of the first restricting portion 4 so as to flow into a narrow passage, so that the problem of clogging does not occur.

また、この複数の略独立の通路１６を、第２弁孔９の内周面に複数の溝部１５を略等間隔に設けた構造としているので、製作が容易である。例えば、弁体３側に複数の突条を形成しても略独立の通路を形成することは可能であるが、その場合より製作が容易に行える。   In addition, since the plurality of substantially independent passages 16 have a structure in which a plurality of groove portions 15 are provided at substantially equal intervals on the inner peripheral surface of the second valve hole 9, manufacturing is easy. For example, even if a plurality of protrusions are formed on the valve body 3 side, it is possible to form a substantially independent passage, but manufacture is easier than that.

また、実施の形態１の膨張弁は、弁本体１内の冷媒流通路２を第１及び第２仕切壁６、７で仕切り、第１及び第２仕切壁６、７に設けた第１弁孔８及び第２弁孔９に対し一つの弁体３を駆動している。また、第１弁孔８と第１弁体部１３との間に全閉かつ開度可変の第１絞り部４を形成するとともに、第２弁孔９と第１弁体部１３との間に複数の略独立の通路１６を備えた第２絞り部５を形成している。したがって、実施の形態１の膨張弁は、簡素化された構成で２段階の絞り部を備えた膨張弁を形成することができる。   The expansion valve of the first embodiment is a first valve provided in the first and second partition walls 6 and 7 by partitioning the refrigerant flow passage 2 in the valve body 1 by the first and second partition walls 6 and 7. One valve element 3 is driven with respect to the hole 8 and the second valve hole 9. Further, the first throttle part 4 that is fully closed and variable in opening is formed between the first valve hole 8 and the first valve body part 13, and between the second valve hole 9 and the first valve body part 13. A second throttle portion 5 having a plurality of substantially independent passages 16 is formed. Therefore, the expansion valve of Embodiment 1 can form an expansion valve having a two-stage throttle portion with a simplified configuration.

（実施の形態２）
以下に、この発明を具体化した実施の形態２に係る膨張弁を図３及び図４に基づいて説明する。図３は実施の形態２に係る膨張弁の縦断面図であり、図４は同図におけるＢ−Ｂ矢視断面図である。 (Embodiment 2)
Hereinafter, an expansion valve according to a second embodiment embodying the present invention will be described with reference to FIGS. FIG. 3 is a longitudinal sectional view of the expansion valve according to Embodiment 2, and FIG. 4 is a sectional view taken along the line BB in FIG.

実施の形態２に係る膨張弁は、例えば前述の図９に示したような冷媒回路に使用するものであって、図３に示すように、弁本体２１と、弁本体２１内に上下方向に形成された冷媒流通路２２と、弁本体２１内に収納された弁体２３とを備えている。さらに、この膨張弁では、弁本体２１の内部に第１絞り部２４と第２絞り部２５とを形成するために、第１仕切壁２６と第２仕切壁２７とが設けられている。第１仕切壁２６は、冷媒流通路２２の出口側部で冷媒流れを仕切るように水平方向に形成された仕切壁である。第２仕切壁２７は、冷媒流通路２の中間部で冷媒流れを仕切るように水平方向に形成された壁高さの大きい仕切壁である。そして、第１仕切壁２６には第１弁孔２８が形成され、第２仕切壁２７には第２弁孔２９が形成されている。   The expansion valve according to Embodiment 2 is used, for example, in the refrigerant circuit as shown in FIG. 9 described above. As shown in FIG. 3, the valve body 21 and the valve body 21 are vertically arranged. A formed refrigerant flow passage 22 and a valve body 23 housed in the valve body 21 are provided. Further, in this expansion valve, a first partition wall 26 and a second partition wall 27 are provided in order to form the first throttle portion 24 and the second throttle portion 25 inside the valve body 21. The first partition wall 26 is a partition wall formed in the horizontal direction so as to partition the refrigerant flow at the outlet side portion of the refrigerant flow passage 22. The second partition wall 27 is a partition wall having a large wall height that is formed in the horizontal direction so as to partition the refrigerant flow at an intermediate portion of the refrigerant flow passage 2. A first valve hole 28 is formed in the first partition wall 26, and a second valve hole 29 is formed in the second partition wall 27.

弁本体２１は、軸心を上下方向として略円筒状に形成され、内部には上下方向の冷媒流通路２２が形成されている。また、弁本体２１は、冷媒流通路２２に繋がる出入口として入口ポート２１ａと出口ポート２１ｂの二つのポートを備えている。入口ポート２１ａは弁本体２１の側部に設けられ、出口ポート２１ｂは弁本体２１の下部に設けられている。したがって、冷媒は、実施の形態１の場合と異なり弁本体２１内において側方から下方に流れるように構成されている。なお、入口ポート２１ａには室外コイルと膨張弁とを接続する液管３０が接続され、出口ポート２１ｂには膨張弁と室内コイルとを連絡する配管３１が接続されている。   The valve main body 21 is formed in a substantially cylindrical shape with the axis as the vertical direction, and a vertical refrigerant flow passage 22 is formed inside. The valve body 21 includes two ports, an inlet port 21a and an outlet port 21b, as inlets / outlets connected to the refrigerant flow passage 22. The inlet port 21 a is provided on the side of the valve body 21, and the outlet port 21 b is provided on the lower part of the valve body 21. Therefore, unlike the case of the first embodiment, the refrigerant is configured to flow downward from the side in the valve main body 21. A liquid pipe 30 that connects the outdoor coil and the expansion valve is connected to the inlet port 21a, and a pipe 31 that connects the expansion valve and the indoor coil is connected to the outlet port 21b.

弁体２３は、冷媒流通路２２と同心に配した略円柱体の棒状部材から形成されている。また、弁体２３は、上部に円柱状の連結部３２、中間部に第２弁体部３４、下部に第１弁体部３３を備えている。第２弁体部１４は、連結部３２の下方に連続して形成されたものであって、下方向に先細のテーパ面を外周面としている。また、第１弁体部３３は、第２弁体部３４の下方に連続して形成されたものであって、下方向に先細のテーパ面を外周面としている。そして、この弁体２３は図示しないパルスモータを駆動源として上下に駆動制御されるように構成されている。   The valve body 23 is formed of a substantially cylindrical rod-shaped member arranged concentrically with the refrigerant flow passage 22. Further, the valve body 23 includes a columnar connecting portion 32 at the upper part, a second valve body part 34 at the intermediate part, and a first valve body part 33 at the lower part. The 2nd valve body part 14 is continuously formed under the connection part 32, Comprising: The taper surface tapered in the downward direction is made into the outer peripheral surface. Moreover, the 1st valve body part 33 is continuously formed under the 2nd valve body part 34, Comprising: The taper surface tapered in the downward direction is made into the outer peripheral surface. The valve body 23 is configured to be driven up and down using a pulse motor (not shown) as a drive source.

第１絞り部２４は、第１弁孔２８に対し弁体２３の第１弁体部３３を上下方向に進退させることにより、第１弁体部３３の外周面であるテーパ面と弁座（第１弁孔２８の上端角部）との間に開度可変、かつ全閉可能な絞りを形成したものである。   The first throttle portion 24 moves the first valve body portion 33 of the valve body 23 up and down in the vertical direction with respect to the first valve hole 28, so that the taper surface and the valve seat (the outer peripheral surface of the first valve body portion 33). A throttle that is variable in opening and can be fully closed is formed between the first valve hole 28 and the upper end corner of the first valve hole 28.

また、第２絞り部２５は、第２弁体部３４のテーパ状をなす外周面を第２弁孔２９の内周面に対向させて配置し、第２弁体部３４の外周面と第２弁孔２９の内周面との間に複数の略独立の通路３６を形成したものである。この第２絞り部２５は、第１絞り部２４の上流側に形成されている。また、第２絞り部２５は、その冷媒流通抵抗を第１絞り部２４の冷媒流通抵抗より小さくしている。さらに、第２弁孔２９は、図３及び図４からよく分かるように、第２弁孔２９の表面部に複数の（この場合４個の）独立した溝部３５が略等間隔に形成されている。この溝部３５は一定幅、一定深さである。これにより、第２弁孔２９と連結部３２との間には前述の複数の（この場合４個の）通路３６が形成されている。また、第２弁孔２９の孔径を、弁体２３の連結部３２が進退させるのに必要な最小寸法程度としている。これにより、第２絞り部２５を形成する通路は、断面積が一定の複数の略独立の通路３６から形成されたものとなる。   The second restrictor 25 is disposed with the outer peripheral surface forming the taper shape of the second valve body portion 34 facing the inner peripheral surface of the second valve hole 29, and A plurality of substantially independent passages 36 are formed between the inner surface of the two valve holes 29. The second throttle portion 25 is formed on the upstream side of the first throttle portion 24. Further, the second throttle unit 25 has a refrigerant flow resistance smaller than that of the first throttle unit 24. Further, as can be clearly understood from FIGS. 3 and 4, the second valve hole 29 has a plurality of (in this case, four) independent groove portions 35 formed at substantially equal intervals on the surface portion of the second valve hole 29. Yes. The groove 35 has a constant width and a constant depth. Thus, the plurality of (in this case, four) passages 36 are formed between the second valve hole 29 and the connecting portion 32. Further, the hole diameter of the second valve hole 29 is set to about the minimum dimension necessary for the connecting portion 32 of the valve body 23 to advance and retract. As a result, the passage forming the second throttle portion 25 is formed by a plurality of substantially independent passages 36 having a constant cross-sectional area.

また、この実施の形態においては、弁体２３を軸方向に進退制御することにより、溝部３５と第２弁体部３４との重なり長さ（すなわち通路３６の長さ）が、第１絞り部２４の弁開度とともに変化するように第２弁体部３４の上下方向の寸法が設定されている。このような構成により、この実施の形態においては、第１絞り部２４と第２絞り部２５とは、冷媒流通抵抗が同時に増減するようにそれぞれ冷媒流通抵抗可変に構成されている。   Further, in this embodiment, the valve body 23 is controlled to advance and retreat in the axial direction, so that the overlapping length of the groove 35 and the second valve body 34 (that is, the length of the passage 36) is the first throttle portion. The vertical dimension of the second valve body 34 is set so as to change with the valve opening of 24. With such a configuration, in this embodiment, the first throttle portion 24 and the second throttle portion 25 are each configured to be capable of varying the refrigerant flow resistance so that the refrigerant flow resistance increases and decreases simultaneously.

実施の形態２の膨張弁は、以上のごとく形成されているので、次のような作用効果を奏する。
入口ポート２１ａから流入してきた液冷媒は、第２絞り部２５にて減圧され、第１絞り部２４においてさらに大きく減圧される。第１絞り部４で減圧された冷媒は出口ポート２１ｂから配管系に流出する。 Since the expansion valve of the second embodiment is formed as described above, the following operational effects can be obtained.
The liquid refrigerant flowing in from the inlet port 21 a is depressurized by the second throttling portion 25 and further depressurized by the first throttling portion 24. The refrigerant decompressed by the first throttle 4 flows out from the outlet port 21b to the piping system.

また、入口ポート２１ａからスラグ流あるいはプラグ流が流入してきた場合、第２絞り部２５から第１絞り部２４へ冷媒を流通させることにより、第１絞り部２４における絞り量を少なくし、第１絞り部２４を通過する冷媒の運動エネルギを少なくしている。これにより、第１絞り部４における圧力変動を低減することができる。特に、第２絞り部２５は、第２弁体部３４と第２弁孔２９との間に形成された複数の略独立の通路３６により形成されている。このため、第１絞り部２４入口側においてスラグ流あるいはプラグ流における音を発生する圧力変動エネルギを分散して音発生エネルギの集中を排除することができる。また、この複数の独立の通路３６により気泡の細分化が行われる。この結果、液冷媒とガス冷媒が交互に第１絞り部２４を通過することに伴う不連続な冷媒流動音、いわゆる「チュルチュル」音、及び冷媒流の圧力変動に起因する振動音が低減される。   In addition, when a slag flow or a plug flow flows in from the inlet port 21a, the amount of throttle in the first throttle unit 24 is reduced by circulating the refrigerant from the second throttle unit 25 to the first throttle unit 24, and the first The kinetic energy of the refrigerant passing through the throttle unit 24 is reduced. Thereby, the pressure fluctuation in the 1st aperture | diaphragm | squeeze part 4 can be reduced. In particular, the second throttle portion 25 is formed by a plurality of substantially independent passages 36 formed between the second valve body portion 34 and the second valve hole 29. For this reason, it is possible to disperse the pressure fluctuation energy that generates sound in the slag flow or the plug flow on the inlet side of the first throttle section 24, thereby eliminating the concentration of the sound generation energy. Further, the bubbles are subdivided by the plurality of independent passages 36. As a result, the discontinuous refrigerant flow sound that accompanies the passage of the liquid refrigerant and the gas refrigerant alternately through the first throttle portion 24, the so-called "church" sound, and the vibration noise caused by the pressure fluctuation of the refrigerant flow are reduced. .

また、複数の略独立の通路３６は、第２弁孔２９の内周面に、弁体３の進退方向に延びる複数の溝部３５を形成して構成されているので、弁体３の進退により、溝部３５と第２弁体部３４の外周面との進退方向における重なり長さが変化する。これにより、第１絞り部２４の冷媒流通抵抗と第２絞り部２５の冷媒流通抵抗とを同時に変化させることができる。したがって、膨張弁の負荷の変動に対し、第１絞り部２４と第２絞り部２５との冷媒流通抵抗の比を適正範囲に保持することが容易になるとともに、幅広い運転範囲に対し安定的に膨張弁入口側の冷媒通過音を低減することができる。   Further, the plurality of substantially independent passages 36 are formed by forming a plurality of groove portions 35 extending in the advance / retreat direction of the valve body 3 on the inner peripheral surface of the second valve hole 29. The overlapping length of the groove portion 35 and the outer peripheral surface of the second valve body portion 34 in the advance / retreat direction changes. Thereby, the refrigerant | coolant circulation resistance of the 1st aperture | diaphragm | squeeze part 24 and the refrigerant | coolant circulation resistance of the 2nd aperture | diaphragm | squeeze part 25 can be changed simultaneously. Therefore, it becomes easy to maintain the ratio of the refrigerant flow resistance between the first throttle portion 24 and the second throttle portion 25 within an appropriate range against fluctuations in the load of the expansion valve, and stably over a wide operating range. Refrigerant passage noise on the inlet side of the expansion valve can be reduced.

また、第２弁孔２９の内周面及び第２弁体部３４の外周面をテーパ面に形成しているので、第２弁孔２９の内周面と第２弁体部３４の外周面との間にゴミが噛み込み、弁体２３の動作不良が起こるのを回避することができる。この間隙は、第２絞り部２５を最も絞るときに必要な最小寸法の間隙に設定されるものであって、通常の設計では、弁体２３を進退させるのに支障を生じない最小寸法となる。また、第２弁孔２９の内周面及び第２弁体部３４の外周面を共に弁体２３の中心線と平行なストレートな面に形成したものでは、両面間の間隙は、弁体２３の進退位置に関係なく常に一定となる。このため、両面間の間隙に冷媒流中に含まれるゴミが一端噛み込むと、外れなくなり、ゴミが堆積して終には弁体３の動作不良を招く恐れがある。ところが、上述のように、両面をテーパ面に形成しているので、弁体３を進退させて第２絞り部５の開度を変化させることにより、両面間の間隙が大小変化する。したがって、第２絞り部２５を開いたときに、一旦噛み込んだゴミを流して除去することができ、弁体２３の動作不良を回避することができる。   Further, since the inner peripheral surface of the second valve hole 29 and the outer peripheral surface of the second valve body portion 34 are formed as tapered surfaces, the inner peripheral surface of the second valve hole 29 and the outer peripheral surface of the second valve body portion 34 are formed. It is possible to avoid the occurrence of a malfunction of the valve body 23 due to dust being caught between the two. The gap is set to a minimum dimension required when the second throttle portion 25 is most narrowed. In a normal design, the gap is a minimum dimension that does not hinder the valve body 23 from moving forward and backward. . Further, in the case where both the inner peripheral surface of the second valve hole 29 and the outer peripheral surface of the second valve body portion 34 are formed on a straight surface parallel to the center line of the valve body 23, the gap between both surfaces is the valve body 23. Regardless of the forward / backward position, it is always constant. For this reason, if the dust contained in the refrigerant flow bites into the gap between both surfaces, it will not come off, and the dust may accumulate and eventually cause a malfunction of the valve body 3. However, since both surfaces are formed as tapered surfaces as described above, the gap between the both surfaces changes by moving the valve body 3 forward and backward to change the opening degree of the second throttle portion 5. Therefore, when the second throttle portion 25 is opened, the dust that has been bitten can be removed by flowing, and malfunction of the valve body 23 can be avoided.

また、第２弁孔２９の内周面及び第２弁体部３４の外周面の双方を互いに平行なテーパ面にしているので、第２絞り部２５の開度により第２弁孔２９の内周面と第２弁体部３４の外周面との間の間隙の変化を少なくすることができる。したがって、第２絞り部２５の弁開度に関係なく複数の独立の通路３６による冷媒分散が適切に行われ、冷媒通過音の低減効果を発揮させることができる。また、複数の溝部３５を等間隔に形成しているので、複数の独立の通路３６が等間隔に形成される。これにより、複数の独立の通路に対する冷媒流分散が均等に行われてエネルギ分散効果を最大限に発揮させることができる。   In addition, since both the inner peripheral surface of the second valve hole 29 and the outer peripheral surface of the second valve body portion 34 are tapered surfaces parallel to each other, the inside of the second valve hole 29 is controlled by the opening degree of the second throttle portion 25. The change in the gap between the peripheral surface and the outer peripheral surface of the second valve body portion 34 can be reduced. Therefore, refrigerant dispersion by the plurality of independent passages 36 is appropriately performed regardless of the valve opening degree of the second throttle portion 25, and the effect of reducing the refrigerant passing sound can be exhibited. Further, since the plurality of groove portions 35 are formed at equal intervals, a plurality of independent passages 36 are formed at equal intervals. Thereby, the refrigerant | coolant flow dispersion | distribution with respect to a several independent channel | path is performed uniformly, and an energy dispersion | distribution effect can be exhibited to the maximum.

弁体２３は、棒状部材の先端部に第１弁体部３３が形成され、棒状部材の中間部に第２弁体部３４が形成されたものとする。また、第２弁体部３４の外周面及び第２弁孔２９の内周面は弁体２３の先端部に向かって先細のテーパ面に形成されている。このため、第２絞り部２５を構成する第２弁体部３４の外周面及び第２弁孔２９の内周面を、弁体２３の軸方向に長くすることができるとともに、これら面の直径を大きくすることができる。したがって、溝部３５を長くすることができるとともに、溝部３５の形状、本数などの設計上の制約を少なくすることができる。   In the valve body 23, it is assumed that a first valve body portion 33 is formed at a distal end portion of a rod-shaped member and a second valve body portion 34 is formed at an intermediate portion of the rod-shaped member. Further, the outer peripheral surface of the second valve body portion 34 and the inner peripheral surface of the second valve hole 29 are formed in a tapered surface that tapers toward the distal end portion of the valve body 23. For this reason, while the outer peripheral surface of the 2nd valve body part 34 which comprises the 2nd aperture | diaphragm | squeeze part 25, and the internal peripheral surface of the 2nd valve hole 29 can be lengthened to the axial direction of the valve body 23, the diameter of these surfaces Can be increased. Therefore, the groove portion 35 can be lengthened and design restrictions such as the shape and number of the groove portions 35 can be reduced.

また、複数の略独立の通路３６は、第２弁孔２９の内周面に上下方向に形成されているので、容易に製作することができる。
また、第１絞り部２４を全閉可能としているので、第１絞り部２４を全閉するまで必要な絞り量を確保することができる。また、従来Ａ方法のように第１絞り部４の上流側で冷媒流の速度を低下させて細い通路に流すようなことがないので、ごみ詰まりの問題が発生しない。 Further, since the plurality of substantially independent passages 36 are formed in the vertical direction on the inner peripheral surface of the second valve hole 29, they can be easily manufactured.
In addition, since the first diaphragm 24 can be fully closed, a necessary diaphragm amount can be ensured until the first diaphragm 24 is fully closed. Further, unlike the conventional method A, the speed of the refrigerant flow is not reduced on the upstream side of the first restricting portion 4 so as to flow into a narrow passage, so that the problem of clogging does not occur.

また、この複数の略独立の通路３６を、第２弁孔２９の内周面に複数の溝部３５を略等間隔に設けた構造としているので、製作が容易である。例えば、弁体２３側に複数の突条を形成しても略独立の通路を形成することは可能であるが、その場合より製作が容易に行える。   Further, since the plurality of substantially independent passages 36 have a structure in which the plurality of groove portions 35 are provided at substantially equal intervals on the inner peripheral surface of the second valve hole 29, the manufacture is easy. For example, even if a plurality of protrusions are formed on the valve body 23 side, it is possible to form a substantially independent passage, but manufacture is easier than that.

また、実施の形態２の膨張弁は、弁本体２１内の冷媒流通路２２を第１及び第２仕切壁２６、２７で仕切り、第１及び第２仕切壁２６、２７に設けた第１弁孔２８及び第２弁孔２９に対し一つの弁体２３を駆動している。また、第１弁孔２８と第１弁体部３３との間に全閉かつ開度可変の第１絞り部２４を形成するとともに、第２弁孔２９と第２弁体部３４との間に複数の略独立の通路３６を備えた第２絞り部２５を形成している。したがって、実施の形態２の膨張弁は、簡素化された構成で２段階の絞り部を備えた膨張弁を形成することができる。   In addition, the expansion valve of the second embodiment includes a first valve provided in the first and second partition walls 26 and 27 by partitioning the refrigerant flow passage 22 in the valve body 21 by the first and second partition walls 26 and 27. One valve element 23 is driven with respect to the hole 28 and the second valve hole 29. In addition, a first throttle part 24 that is fully closed and has a variable opening is formed between the first valve hole 28 and the first valve body part 33, and between the second valve hole 29 and the second valve body part 34. The second throttle portion 25 having a plurality of substantially independent passages 36 is formed. Therefore, the expansion valve according to the second embodiment can form an expansion valve including a two-stage throttle portion with a simplified configuration.

（実施の形態３）
次に実施の形態３について、図５に基づき説明する。図５は実施の形態３に係る膨張弁の要部縦断面図である。なお、図５において実施の形態１と同一の部分には同一の符号を付し、その説明を省略する。 (Embodiment 3)
Next, Embodiment 3 will be described with reference to FIG. FIG. 5 is a longitudinal sectional view of an essential part of the expansion valve according to the third embodiment. In FIG. 5, the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

実施の形態３は、実施の形態１において第２弁体部１４を変形したものである。すなわち、実施の形態１においては、第２弁体部１４は第１弁体部１３の下方に連続して形成されたものであって、下方向に先細のテーパ面を外周面としていたが、実施の形態３においては第２弁体部４４の外周面を弁体３の中心軸に平行なストレートな面に形成したものである。このように、実施の形態３では、第２弁体部４４の外周面を上下方向にまっすぐ延びるストレートな面とし、第２弁孔９の内周面を実施の形態１と同一のテーパ面にしている。   The third embodiment is obtained by modifying the second valve body portion 14 in the first embodiment. That is, in the first embodiment, the second valve body portion 14 is formed continuously below the first valve body portion 13 and has a tapering tapered surface in the downward direction as an outer peripheral surface. In the third embodiment, the outer peripheral surface of the second valve body portion 44 is formed on a straight surface parallel to the central axis of the valve body 3. As described above, in the third embodiment, the outer peripheral surface of the second valve body portion 44 is a straight surface extending straight in the vertical direction, and the inner peripheral surface of the second valve hole 9 is the same tapered surface as in the first embodiment. ing.

したがって、実施の形態１の場合と同様に、弁体３を進退させて第２絞り部５を開閉することにより、両面間の間隙が大小変化する。例えば、第２絞り部５を開いたときに、この間隙が大きくなる。したがって、複数の独立の通路１６相互間における第２弁体部４４の外周面と第２弁孔９の内周面との間の間隙に噛み込んだゴミは、この間隙が大きくなったときに冷媒流により洗い流される。これにより、弁体３の動作不良を回避することができる。ただし、この実施の形態３の場合は、実施の形態１の場合と異なり、対向する第２弁体部４４の外周面と第２弁孔９の内周面のうちの第２弁孔９の内周面のみをテーパ面としている。このため、第２絞り部５の開度を大きくした場合に、両面間の間隙が大きくなって複数の独立の通路１６の独立性が無くなる可能性があり、冷媒流分散効果が発揮されない場合があり得る。   Therefore, as in the case of the first embodiment, by opening and closing the valve body 3 to open and close the second throttle portion 5, the gap between both surfaces changes in size. For example, when the second diaphragm 5 is opened, this gap becomes large. Therefore, the dust caught in the gap between the outer peripheral surface of the second valve body portion 44 and the inner peripheral surface of the second valve hole 9 between the plurality of independent passages 16 is increased when this gap is increased. Washed away by refrigerant flow. Thereby, the malfunctioning of the valve body 3 can be avoided. However, in the case of the third embodiment, unlike the case of the first embodiment, the second valve hole 9 out of the outer peripheral surface of the second valve body portion 44 and the inner peripheral surface of the second valve hole 9 facing each other. Only the inner peripheral surface is a tapered surface. For this reason, when the opening degree of the 2nd aperture | diaphragm | squeeze part 5 is enlarged, the clearance gap between both surfaces may become large and the independence of several independent channel | paths 16 may be lose | eliminated, and a refrigerant | coolant flow dispersion | distribution effect may not be exhibited. possible.

（実施の形態４）
次に実施の形態４について、図６に基づき説明する。図６は実施の形態４に係る膨張弁の要部縦断面図である。なお、図６において実施の形態２と同一の部分には同一の符号を付し、その説明を省略する。 (Embodiment 4)
Next, the fourth embodiment will be described with reference to FIG. FIG. 6 is a longitudinal sectional view of a main part of an expansion valve according to the fourth embodiment. In FIG. 6, the same parts as those of the second embodiment are denoted by the same reference numerals, and the description thereof is omitted.

実施の形態４は、実施の形態２において第２弁孔２９の内周面を変形したものである。すなわち、実施の形態２においては、第２弁孔２９の内周面を弁体２３の中心軸に対し傾斜する、下方向に先細のテーパ面に形成されていたが、実施の形態４においては、第２弁孔５９の内周面を弁体３の中心軸に平行なストレートな面に形成したものである。これに伴い、図６に示すように、溝部５５及び複数の略独立の通路５６は弁体３の中心軸に平行に形成される。このように、実施の形態４では、第２弁孔５９の内周面を上下方向にまっすぐに延びるストレートな面とし、第２弁体部３４の外周面を実施の形態２と同一のテーパ面にしている。   In the fourth embodiment, the inner peripheral surface of the second valve hole 29 is modified in the second embodiment. That is, in the second embodiment, the inner peripheral surface of the second valve hole 29 is formed as a tapered surface that is inclined downward with respect to the central axis of the valve body 23, but in the fourth embodiment, The inner peripheral surface of the second valve hole 59 is formed on a straight surface parallel to the central axis of the valve body 3. Accordingly, as shown in FIG. 6, the groove portion 55 and the plurality of substantially independent passages 56 are formed in parallel to the central axis of the valve body 3. As described above, in the fourth embodiment, the inner peripheral surface of the second valve hole 59 is a straight surface that extends straight in the vertical direction, and the outer peripheral surface of the second valve body portion 34 is the same tapered surface as in the second embodiment. I have to.

したがって、実施の形態２の場合と同様に、弁体３を進退させて第２絞り部５を開閉することにより、両面間の間隙が大小変化する。このため、複数の独立の通路１６間における第２弁体部１４の外周面と第２弁孔５９の内周面との間の間隙に噛み込んだゴミは、第２絞り部５を開いたときに、この間隙が大きくなることにより、冷媒流により洗い流すことができ、弁体３の動作不良を回避することができる。ただし、この実施の形態４の場合は、実施の形態２の場合と異なり、対向する第２弁体部１４の外周面と第２弁孔５９の内周面のうちの第２弁体部１４の外周面のみがテーパ面である。このため、第２絞り部５の開度を大きくした場合に、両面間の間隙が大きくなって複数の独立の通路５６の独立性が無くなる可能性があり、冷媒流分散効果が発揮されない場合があり得る。   Therefore, as in the case of the second embodiment, by opening and closing the second throttle portion 5 by moving the valve body 3 back and forth, the gap between both surfaces changes in size. Therefore, the dust caught in the gap between the outer peripheral surface of the second valve body portion 14 and the inner peripheral surface of the second valve hole 59 between the plurality of independent passages 16 opened the second throttle portion 5. Sometimes, the gap becomes large, so that it can be washed away by the refrigerant flow, and malfunction of the valve body 3 can be avoided. However, in the case of the fourth embodiment, unlike the case of the second embodiment, the second valve body portion 14 of the outer peripheral surface of the second valve body portion 14 and the inner peripheral surface of the second valve hole 59 facing each other. Only the outer peripheral surface is a tapered surface. For this reason, when the opening degree of the 2nd aperture | diaphragm | squeeze part 5 is enlarged, the clearance gap between both surfaces may become large and the independence of several independent channel | paths 56 may be lose | eliminated, and a refrigerant | coolant flow dispersion | distribution effect may not be exhibited. possible.

（実施の形態５）
次に実施の形態５について、図７及び図８に基づき説明する。図７は実施の形態５に係る膨張弁の要部縦断面図であり、図８は図７におけるＣ−Ｃ矢視断面図である。なお、図７及び図８において実施の形態２と同一又は相当の部分には同一の符号を付し、その説明を省略する。 (Embodiment 5)
Next, the fifth embodiment will be described with reference to FIGS. FIG. 7 is a longitudinal sectional view of an essential part of the expansion valve according to the fifth embodiment, and FIG. 8 is a sectional view taken along the line CC in FIG. 7 and 8, the same or corresponding parts as those in the second embodiment are denoted by the same reference numerals, and the description thereof is omitted.

実施の形態５は、実施の形態２において第２絞り部２５を構成する複数の略独立の通路３６を変更したものである。すなわち、実施の形態２における略独立の通路３６は、第２弁孔２９の内周面に、進退方向に延びる複数の溝部３５を形成し、この複数の溝部３５の開口部を第２弁体部３４の外周面に対向させたて構成したものである。これに対し、実施の形態５においては、第２弁体部６４の外周面を成すテーパ面に複数の溝部６５を形成し、第２弁孔６９の内周面を溝のないテーパ面としている。そして、この溝部６５の開口部を第２弁孔６９のテーパ面で覆うことにより、複数の略独立の通路６６を構成している。   In the fifth embodiment, a plurality of substantially independent passages 36 constituting the second throttle portion 25 in the second embodiment are changed. That is, the substantially independent passage 36 in the second embodiment forms a plurality of groove portions 35 extending in the advancing and retreating direction on the inner peripheral surface of the second valve hole 29, and the openings of the plurality of groove portions 35 serve as the second valve body. It is configured to face the outer peripheral surface of the portion 34. On the other hand, in the fifth embodiment, a plurality of groove portions 65 are formed on the tapered surface forming the outer peripheral surface of the second valve body portion 64, and the inner peripheral surface of the second valve hole 69 is a tapered surface having no groove. . A plurality of substantially independent passages 66 are formed by covering the opening of the groove 65 with the tapered surface of the second valve hole 69.

本実施の形態ではこのように構成することにより、実施の形態２と同様の効果を奏することができる。また、本実施の形態では第２弁体部６４の外周面に、弁体２３の進退方向に延びる複数の溝部６５を形成するので、実施の形態２の場合に比し溝部の加工が容易である。   In this embodiment, by configuring in this way, the same effects as those of the second embodiment can be obtained. Further, in the present embodiment, since the plurality of groove portions 65 extending in the advance / retreat direction of the valve body 23 are formed on the outer peripheral surface of the second valve body portion 64, the processing of the groove portion is easier than in the case of the second embodiment. is there.

（実施の形態６）
次に、この発明を具体化した実施の形態６に係る膨張弁を図９及び図１０に基づいて説明する。なお、図９は実施の形態６に係る膨張弁の要部縦断面図であって、最大開度の状態を示す。図１０は、図９におけるＤ−Ｄ断面図である。また、この図面には実施の形態５における構成要素と同一又は相当する要素については同一の符号を付し、その説明を省略する。 (Embodiment 6)
Next, an expansion valve according to a sixth embodiment embodying the present invention will be described with reference to FIGS. In addition, FIG. 9 is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 6, Comprising: The state of a maximum opening degree is shown. 10 is a cross-sectional view taken along the line DD in FIG. Also, in this drawing, the same or corresponding elements as those in the fifth embodiment are denoted by the same reference numerals, and the description thereof is omitted.

実施の形態６は、実施の形態５と同様に、第２弁体部６４の外周面を成すテーパ面に複数の溝部６５を形成し、第２弁孔６９の内周面を溝のないテーパ面としている（図９参照）。また、この溝部６５の開口部を第２弁孔６９のテーパ面で覆うことにより、複数の略独立の通路６６構成している（図９参照）。一方、この実施の形態６に係る膨張弁は、次の点で実施の形態５と異なる。すなわち、本実施の形態６では、第２絞り部２５から第１弁孔２８に至る冷媒通路における第１弁孔２８の入口側部に拡大空間部７１が形成されている。また、第１絞り部２４、第２絞り部２５及び連結部３２などの詳細が以下に述べるように異なる。   In the sixth embodiment, similarly to the fifth embodiment, a plurality of groove portions 65 are formed on the tapered surface forming the outer peripheral surface of the second valve body portion 64, and the inner peripheral surface of the second valve hole 69 is tapered without a groove. Surface (see FIG. 9). Further, a plurality of substantially independent passages 66 are formed by covering the opening of the groove 65 with the tapered surface of the second valve hole 69 (see FIG. 9). On the other hand, the expansion valve according to the sixth embodiment is different from the fifth embodiment in the following points. That is, in the sixth embodiment, the enlarged space portion 71 is formed on the inlet side portion of the first valve hole 28 in the refrigerant passage extending from the second throttle portion 25 to the first valve hole 28. Further, the details of the first diaphragm portion 24, the second diaphragm portion 25, the connecting portion 32, and the like are different as described below.

この実施の形態６においては、図９に示すように、第２弁体部６４の外周面に形成されているテーパ面のテーパ角度α１と、第２弁孔９を形成するテーパ面のテーパ角度α２とが同一角度に形成されている。なお、第２弁孔９を形成するテーパ面のテーパ角度α２は、略５度〜略６０度に形成されている。テーパ角度α２の下限を５度とするのは、第２絞り部２５が全開に向かうときに、第２弁体部６４の外周面に形成されているテーパ面とこのテーパ面に対向する第２弁孔９の内周面との間隙に噛み込んだゴミを除去可能とする下限の値である。また、上限を略６０度としたのは、複数の溝部６５部分の必要長さから割り出された十分条件値である。なお、この実施の形態では、テーパ角度α１及びテーパ角度α２は約２５度である。   In the sixth embodiment, as shown in FIG. 9, the taper angle α1 of the taper surface formed on the outer peripheral surface of the second valve body portion 64 and the taper angle of the taper surface forming the second valve hole 9. α2 is formed at the same angle. The taper angle α2 of the tapered surface forming the second valve hole 9 is formed to be approximately 5 degrees to approximately 60 degrees. The lower limit of the taper angle α2 is set to 5 degrees because, when the second throttle portion 25 is fully opened, the taper surface formed on the outer peripheral surface of the second valve body portion 64 and the second surface facing this taper surface. This is the lower limit value that enables removal of dust caught in the gap with the inner peripheral surface of the valve hole 9. The upper limit of about 60 degrees is a sufficient condition value calculated from the required length of the plurality of groove portions 65. In this embodiment, the taper angle α1 and the taper angle α2 are about 25 degrees.

また、複数の溝部６５を形成する第２弁体部６４の外周面を構成するテーパ面の上流側端部は、図９に示すように、第２絞り部２５の最小開度の状態から最大開度（図９の状態）の何れにおいても、第２弁孔９内に位置するように構成されている。ここで、第２絞り部２５の最小開度の状態とは、図示していないが、図９において、第１弁体部３３の外周面に形成されるテーパ面が第１弁孔２８の弁座、すなわち第１弁孔２８の上端角部に当接するように、弁体２３を下降させた状態をいう。換言すると、第２弁体部６４の外周面を構成するテーパ面の上流側端部の位置Ｘ１は、第２絞り部２５の最小から最大の何れの開度においても、第２弁孔９の上流側端部の位置Ｙ１より下方となるように形成されている。   Further, as shown in FIG. 9, the upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 forming the plurality of groove portions 65 is maximized from the state of the minimum opening of the second throttle portion 25. It is configured to be located in the second valve hole 9 at any opening degree (state of FIG. 9). Here, the state of the minimum opening of the second throttle portion 25 is not shown, but in FIG. 9, the tapered surface formed on the outer peripheral surface of the first valve body portion 33 is the valve of the first valve hole 28. This means a state in which the valve body 23 is lowered so as to contact the seat, that is, the upper end corner of the first valve hole 28. In other words, the position X1 of the upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 is the position of the second valve hole 9 at any opening degree from the minimum to the maximum of the second throttle portion 25. It is formed to be below the position Y1 of the upstream end.

また、第２弁体部６４の外周面を構成するテーパ面の上流側端部は、第２異径接合部７３を介して連結部３２に連結されている。連結部３２の直径ｄ２は、第２弁体部６４の外周面を構成するテーパ面における最大外周部の直径ｄ１より小さく形成されている。このように、第２異径接合部７３は、第２弁体部６４の外周面を構成するテーパ面における最大外周部を、連結部３２へテーパ状に滑らかに接続するものである。すなわち、第２弁体部６４の外周面を構成するテーパ面における最大外周部から連結部３２の外周部に向かってテーパ状に縮径する形状に形成されている。   Further, the upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 is connected to the connecting portion 32 via the second different diameter joint portion 73. The diameter d2 of the connecting portion 32 is formed smaller than the diameter d1 of the maximum outer peripheral portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64. As described above, the second different diameter joint portion 73 smoothly connects the maximum outer peripheral portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 to the connecting portion 32 in a tapered shape. That is, the second valve body portion 64 is formed in a shape that decreases in diameter from a maximum outer peripheral portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 toward the outer peripheral portion of the connecting portion 32.

また、第２弁体部６４の外周面を構成するテーパ面の下流側端部は、第２絞り部２５の最小開度から最大開度（図９の状態）の何れにおいても拡大空間部７１内に位置するように構成されている。すなわち、第２弁体部６４の外周面を構成するテーパ面の下流側端部の位置Ｘ２は、第２絞り部２５の最小から最大の何れの開度においても、第２弁孔９の下流側端部の位置Ｙ２の位置より下方となるように形成されている。   Further, the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 has an enlarged space portion 71 in any of the minimum opening and the maximum opening (state of FIG. 9) of the second throttle portion 25. It is comprised so that it may be located in. That is, the position X2 of the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 is downstream of the second valve hole 9 at any opening degree from the minimum to the maximum of the second throttle portion 25. It is formed so as to be lower than the position Y2 of the side end.

また、第１弁体部３３は、実施の形態５の場合と同様に、外周面が下流側に向かって縮径するテーパ面に形成されている。また、このテーパ面のテーパ角度β１は、前述の第２弁孔９の内周面を成すテーパ面のテーパ角度α２より大きく形成されている。また、第２弁体部６４の外周面を構成するテーパ面の下流側端部と第１弁体部３３のテーパ状外周面の上流側端部との間に、第２弁体部６４の外周面を構成するテーパ面の下流側端部から第１弁体部３３のテーパ状の外周面に向かってテーパ状に縮径する第１異径接合部７２が形成されている。また、この第１異径接合部７２のテーパ角度β２は、第１弁体部３３のテーパ面のテーパ角度β１より大きく形成されている（図９参照）。   Moreover, the 1st valve body part 33 is formed in the taper surface to which an outer peripheral surface reduces in diameter toward the downstream similarly to the case of Embodiment 5. Further, the taper angle β1 of the taper surface is formed larger than the taper angle α2 of the taper surface forming the inner peripheral surface of the second valve hole 9 described above. Further, between the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 and the upstream end portion of the tapered outer peripheral surface of the first valve body portion 33, A first different-diameter joint portion 72 that is tapered in diameter toward the tapered outer peripheral surface of the first valve body portion 33 from the downstream end portion of the tapered surface constituting the outer peripheral surface is formed. Further, the taper angle β2 of the first different diameter joint portion 72 is formed larger than the taper angle β1 of the taper surface of the first valve body portion 33 (see FIG. 9).

また、第１絞り部２４入口側における第１弁体部３３と第１弁孔８との間隙Ｓ１を、第２絞り部２５における第２弁体部６４と第２弁孔９との最小間隙Ｓ２より小さくしている。ここで、第１絞り部２４入口側における第１弁体部３３と第１弁孔８との間隙Ｓ１とは、図９に図示するように、第１弁体部３３のテーパ面に垂直な方向で測ったこのテーパ面から第１弁孔８の入口側角部までの距離をいう。また、第２絞り部２５における第２弁体部６４と第２弁孔９との最小間隙Ｓ２とは、第２弁体部６４のテーパ面に垂直な方向で測ったこのテーパ面から第２弁孔９のテーパ面までの距離のうちの最小距離をいう。この最小距離となる位置は、第２弁体部６４のテーパ面のテーパ角度α１と第２弁孔９のテーパ面のテーパ角度α２と比較してどちらが大きいかにより異なってくる。しかし、この実施の形態では両者同一角であるので、図９に図示するように、第２弁体部６４の上流側端部の位置Ｘ１から第２弁孔９の下流側端部の位置Ｘ２の何れの位置で測っても同一となる。   Further, the gap S1 between the first valve body portion 33 and the first valve hole 8 on the inlet side of the first throttle portion 24 is the minimum gap between the second valve body portion 64 and the second valve hole 9 in the second throttle portion 25. It is smaller than S2. Here, the gap S1 between the first valve body portion 33 and the first valve hole 8 on the inlet side of the first throttle portion 24 is perpendicular to the tapered surface of the first valve body portion 33 as shown in FIG. The distance from the tapered surface measured in the direction to the inlet side corner of the first valve hole 8 is said. Further, the minimum gap S2 between the second valve body portion 64 and the second valve hole 9 in the second throttle portion 25 is a second from the taper surface measured in the direction perpendicular to the taper surface of the second valve body portion 64. The minimum distance of the distance to the taper surface of the valve hole 9 is said. The position of the minimum distance differs depending on which is greater than the taper angle α1 of the tapered surface of the second valve body 64 and the taper angle α2 of the tapered surface of the second valve hole 9. However, in this embodiment, since they are the same angle, as shown in FIG. 9, the position X2 of the downstream end of the second valve hole 9 from the position X1 of the upstream end of the second valve body 64 is shown. It is the same even if measured at any of the positions.

実施の形態６に係る膨張弁は以上のように構成されているので、実施の形態５の効果に加えて、次のような効果を奏することができる。
第２弁体部６４の外周面を構成するテーパ面が第２弁孔９の上流側に突出していると、第２絞り部２５における略独立の複数の通路３６で気泡が細分化される前に、第２弁孔９の上流側に突出している複数の溝部６５を形成する第２弁体部６４の外周面を構成するテーパ面で冷媒流が乱される。これは、気泡細分化前に新たな冷媒通過音を発生する要因になる。しかし、この実施の形態に係る膨張弁では、第２弁体部６４の外周面を構成するテーパ面の上流側端部が、第２絞り部２５の最小から最大の何れの開度においても第２弁孔９内に位置しているので、このような乱れを解消することができる。 Since the expansion valve according to the sixth embodiment is configured as described above, in addition to the effects of the fifth embodiment, the following effects can be achieved.
When the tapered surface constituting the outer peripheral surface of the second valve body portion 64 protrudes to the upstream side of the second valve hole 9, before the bubbles are subdivided by the plurality of substantially independent passages 36 in the second throttle portion 25. In addition, the refrigerant flow is disturbed by the tapered surface constituting the outer peripheral surface of the second valve body portion 64 that forms the plurality of groove portions 65 protruding upstream of the second valve hole 9. This becomes a factor that generates a new refrigerant passing sound before bubble fragmentation. However, in the expansion valve according to this embodiment, the upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 has the second opening at any opening from the minimum to the maximum. Since it is located in the two valve holes 9, such disturbance can be eliminated.

また、第２弁体部６４の外周面を構成するテーパ面の下流側端部が第２弁孔９内に位置するように形成されている場合は、第２弁孔９から拡大空間部７１に流出する際の流れが急激に変動するため抵抗が大きくなり、新たな騒音発生要因を発生することになる。しかし、この実施の形態に係る膨張弁では、複数の溝部６５の下流側端部を、第２絞り部２５の最小から最大の何れの開度においても拡大空間部７１内に位置するように構成しているので、複数の独立の通路３６で整流されている冷媒を拡大空間部７１内にスムーズに流入させることができる。この結果、拡大空間７１内で２相流を掻き乱すことにより気泡を細分化することができ、冷媒通過音をより一層軽減することができる。   Further, when the downstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion 64 is formed in the second valve hole 9, the enlarged space portion 71 extends from the second valve hole 9. Since the flow at the time of outflow fluctuates rapidly, the resistance increases and a new noise generation factor is generated. However, the expansion valve according to this embodiment is configured such that the downstream end portions of the plurality of groove portions 65 are located in the enlarged space portion 71 at any opening degree from the minimum to the maximum of the second throttle portion 25. Therefore, the refrigerant rectified by the plurality of independent passages 36 can smoothly flow into the enlarged space 71. As a result, the bubbles can be subdivided by disturbing the two-phase flow in the enlarged space 71, and the refrigerant passing sound can be further reduced.

また、第１絞り部２４の入口側における第１弁体部３３と第１弁孔２８との間隙Ｓ１を、第２絞り部２５の出口側における第２弁体部６４と第２弁孔６９との最小間隙Ｓ２より小さくしているので、第１絞り部２４の絞り効果を第２絞り部２５の絞り効果より大きくすることができる。したがって、第１絞り部２４を主絞り部とし、第２絞り部２５を気泡細分化効果に最適なものとして設計することができるとともに、第２絞り部２５を設けることに起因するゴミ詰まりの確率が高くなることもない。   Further, the gap S1 between the first valve body portion 33 and the first valve hole 28 on the inlet side of the first throttle portion 24 is defined as the second valve body portion 64 and the second valve hole 69 on the outlet side of the second throttle portion 25. Therefore, the aperture effect of the first aperture section 24 can be made larger than the aperture effect of the second aperture section 25. Therefore, it is possible to design the first throttle portion 24 as the main throttle portion and the second throttle portion 25 as the optimum one for the bubble subdividing effect, and the probability of dust clogging due to the provision of the second throttle portion 25. Does not increase.

また、第２弁体部６４の外周面を構成するテーパ面のテーパ角度α１と第２弁孔６９の内周面を成すテーパ面のテーパ角度α２とを同一に形成するとともに、第１弁体部３３の外周面を構成するテーパ面のテーパ角度β１を第２弁孔６９の内周面を成すテーパ面のテーパ角度α２より大きくしているので、弁体２３の進退に伴う第１絞り部２４の絞り効果の変化を第２絞り部２５のそれより大きくすることができる。   Further, the taper angle α1 of the taper surface constituting the outer peripheral surface of the second valve body portion 64 and the taper angle α2 of the taper surface forming the inner peripheral surface of the second valve hole 69 are formed identically, and the first valve body Since the taper angle β1 of the taper surface constituting the outer peripheral surface of the portion 33 is larger than the taper angle α2 of the taper surface forming the inner peripheral surface of the second valve hole 69, the first throttle portion associated with the advancement and retreat of the valve body 23 The change of the aperture effect of 24 can be made larger than that of the second aperture portion 25.

また、この実施の形態に係る膨張弁では、第２弁孔６９の内周面を成すテーパ面のテーパ角度α２は、略５度〜略６０度としている。第２弁体部の外周面を構成するテーパ面とこのテーパ面に対向する第２弁孔６９の内周面との間隙に噛み込んだゴミを除去することが可能である。また、複数の溝部６５部分の必要な長さを取ることが容易である。   Further, in the expansion valve according to this embodiment, the taper angle α2 of the taper surface forming the inner peripheral surface of the second valve hole 69 is approximately 5 degrees to approximately 60 degrees. It is possible to remove dust caught in the gap between the tapered surface constituting the outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole 69 facing the tapered surface. Moreover, it is easy to take the required length of the plurality of groove portions 65.

また、弁体２３における第２弁体部６４の外周面の上流側端部の上流側端部に連結される連結部３２の直径ｄ２を、前記第２弁体部６４の外周面を構成するテーパにおける最大外周部の直径ｄ１より小さくしているので、弁本体２１の内部に流入する冷媒流がこの連結部３２により阻害されて、第２絞り部２５に流入する前に乱されることが軽減される。したがって、冷媒通過音を大きくする要因を排除することができる。   Moreover, the diameter d2 of the connection part 32 connected with the upstream edge part of the upstream edge part of the outer peripheral surface of the 2nd valve body part 64 in the valve body 23 comprises the outer peripheral surface of the said 2nd valve body part 64. Since the diameter is smaller than the diameter d1 of the maximum outer peripheral portion of the taper, the refrigerant flow flowing into the valve body 21 is obstructed by the connecting portion 32 and disturbed before flowing into the second throttle portion 25. It is reduced. Therefore, it is possible to eliminate a factor that increases the refrigerant passing sound.

また、連結部３２と第２弁体部６４の外周面の上流側端部との間には、第２弁体部６４の外周面を構成するテーパにおける最大外周部から連結部３２の外周部に向かってテーパ状に縮径する第２異径接合部７３を形成しているので、弁本体２１内部に流入した冷媒流が第２絞り部２５に流入するまでの乱れがより少なくなる。したがって、冷媒通過音を大きくする要因をさらに排除することができる。   Further, between the connecting portion 32 and the upstream end portion of the outer peripheral surface of the second valve body portion 64, the outer peripheral portion of the connecting portion 32 from the maximum outer peripheral portion in the taper constituting the outer peripheral surface of the second valve body portion 64. Since the second different diameter joint portion 73 that decreases in a taper shape is formed, disturbance until the refrigerant flow that has flowed into the valve main body 21 flows into the second throttle portion 25 is further reduced. Therefore, it is possible to further eliminate the factor that increases the refrigerant passing sound.

（９）第２弁体部６４の外周面の下流側端部と第１弁体部３３のテーパ状外周面の上部との間に、第２弁体部６４の外周面の下流側端部から第１弁体部３３のテーパ状外周面に向かってテーパ状に縮径する第１異径接合部７２を形成している。また、第１異径接合部７２のテーパ角度β２を、第１弁体部３３のテーパ状外周面のテーパ角度β１より大きくしている。このように構成することにより、第１弁孔２８の大きさ及び第２弁孔６９大きさをそれぞれに適した大きさに容易に設計することができる。   (9) The downstream end portion of the outer peripheral surface of the second valve body portion 64 between the downstream end portion of the outer peripheral surface of the second valve body portion 64 and the upper portion of the tapered outer peripheral surface of the first valve body portion 33. A first different-diameter joint portion 72 that decreases in diameter toward the tapered outer peripheral surface of the first valve body portion 33 is formed. Further, the taper angle β2 of the first different diameter joint portion 72 is made larger than the taper angle β1 of the tapered outer peripheral surface of the first valve body portion 33. By configuring in this way, the size of the first valve hole 28 and the size of the second valve hole 69 can be easily designed to be suitable for each.

（変形例）
この発明は、次のように変更して具体化することもできる。
（１）上記各実施の形態においては、図９に示したような１台の室外ユニット１０５に対し１台の室内ユニット１０６を用いる冷媒回路に用いる例を取り上げて説明したが、本膨張弁は、１台の室外ユニットに対し複数台の室内ユニットを接続する所謂マルチ型エアコンに使用できることは勿論である。また、マルチ型エアコンでは、膨張弁入り口側の運転条件の変化が大きく、大きな気泡の混入する機会が多くなる。したがって、本発明の膨張弁は、マルチ型エアコンに用いられると、より顕著にその効果を発揮することができる。 (Modification)
The present invention can also be embodied with the following modifications.
(1) In each of the above-described embodiments, an example in which a refrigerant circuit using one indoor unit 106 is used for one outdoor unit 105 as shown in FIG. 9 has been described. Of course, it can be used for a so-called multi-type air conditioner in which a plurality of indoor units are connected to one outdoor unit. In the multi-type air conditioner, the operating condition on the inlet side of the expansion valve changes greatly, and the opportunity for large bubbles to enter increases. Therefore, when the expansion valve of the present invention is used in a multi-type air conditioner, the effect can be exhibited more remarkably.

（２）各実施の形態においては、第１絞り部４、２４は、全閉するものについてのみ説明しているが、この第１絞り部４、２４は、全閉しない範囲で使用してもよい。また、機構的に全閉しないように構成されているものとしてもよい。   (2) In each embodiment, only the first throttle portions 4 and 24 are described as being fully closed. However, the first throttle portions 4 and 24 may be used within a range where they are not fully closed. Good. Moreover, it is good also as what is comprised so that it may not fully close mechanically.

（３）実施の形態１〜６における第２絞り部５、２５の複数の独立の通路１６、３６、６６を構成する溝部１５、３５、６５の形状は、図２及び図４のように断面が略３角形状に拘るものではなく、円形、長円形、楕円形、コの字型など適宜の形状としてもよい。また、弁体３、２３の進退方向において、溝部１５、３５、６５の断面積を変えることにより、複数の独立の通路１６、３６、６６の断面積を変化させるようにしてもよい。また、弁体３、２３の進退方向において、溝部１５、３５、６５の数を変えることにより、複数の独立の通路１６、３６、６６の断面積を変化させるようにしてもよい。   (3) The shape of the groove parts 15, 35, 65 constituting the plurality of independent passages 16, 36, 66 of the second throttle parts 5, 25 in the first to sixth embodiments is a cross section as shown in FIGS. However, the shape is not limited to a substantially triangular shape, and may be an appropriate shape such as a circle, an oval, an ellipse, or a U-shape. Further, the cross-sectional areas of the plurality of independent passages 16, 36, 66 may be changed by changing the cross-sectional areas of the groove portions 15, 35, 65 in the advancing / retreating direction of the valve bodies 3, 23. Further, the cross-sectional areas of the plurality of independent passages 16, 36, 66 may be changed by changing the number of the groove portions 15, 35, 65 in the advance / retreat direction of the valve bodies 3, 23.

（４）実施の形態４で第２弁孔５９の内面を中心軸に平行なストレートな面に形成したのと同様に、実施の形態１において、第２弁孔９内周面を弁体３の中心軸に平行なストレートな面に形成されたものに変更してもよい。また、実施の形態３で第２弁体部３４の外周面を弁体３の中心軸に平行なストレートな面に形成したのと同様に、実施の形態２におい、第２弁体部３４の外周面を弁体３の中心軸に平行なストレートな面に形成したものに変更してもよい。   (4) In the fourth embodiment, the inner surface of the second valve hole 59 in the first embodiment is formed as a straight surface parallel to the central axis. You may change into what was formed in the straight surface parallel to the central axis of. Similarly to the second embodiment, the outer peripheral surface of the second valve body portion 34 is formed as a straight surface parallel to the central axis of the valve body 3. The outer peripheral surface may be changed to a straight surface parallel to the central axis of the valve body 3.

（５）実施の形態１、２、５及び６において、第２弁体部１４、３４、６４の外周面と第２弁孔９、２９、６９の内周面をそれぞれテーパ面とするとともに、これらテーパ面を平行となるように形成しているが、これに限定されるものでなくテーパ面のテーパ角度を異なったものとすることもできる。   (5) In the first, second, fifth, and sixth embodiments, the outer peripheral surface of the second valve body portions 14, 34, and 64 and the inner peripheral surface of the second valve holes 9, 29, and 69 are respectively tapered surfaces. These tapered surfaces are formed so as to be parallel, but the present invention is not limited to this, and the taper angles of the tapered surfaces may be different.

（６）実施の形態１、３及び４において、上記実施の形態５と同様に、第２弁孔９、２９、５９に溝部１５、５５、を形成しないで、第２弁体部１４、３４、４４の外周面に、弁体３、２３の進行方向に延びる複数の溝部を形成するようにしてもよい。このようにすると、実施の形態５の場合と同様に、溝部を容易に加工することができる。   (6) In the first, third, and fourth embodiments, as in the fifth embodiment, the second valve body portions 14 and 34 are formed without forming the groove portions 15 and 55 in the second valve holes 9, 29, and 59. , 44 may be formed with a plurality of grooves extending in the traveling direction of the valve bodies 3, 23. In this way, the groove can be easily processed as in the case of the fifth embodiment.

（７）実施の形態６において、溝部６５を第２弁孔６９の内周面を構成するテーパ面に加工するようにしてもよい。このようにしても、実施の形態６の場合と同様に膨張弁における冷媒通過音を低減することができる。   (7) In the sixth embodiment, the groove 65 may be processed into a tapered surface constituting the inner peripheral surface of the second valve hole 69. Even if it does in this way, the refrigerant | coolant passage sound in an expansion valve can be reduced similarly to the case of Embodiment 6. FIG.

（８）実施の形態６において、第２弁体部６４のテーパ面のテーパ角度α１と第２弁孔９のテーパ面のテーパ角度α２とを異ならせるようにしてもよい。なお、第２弁体部６４のテーパ面のテーパ角度α１を第２弁孔９のテーパ面のテーパ角度α２より大きくした場合は、前記最小間隙Ｓ２は第２弁体部６４のテーパ面の上流側端部の位置Ｘ１において測定することができる。逆に、第２弁体部６４のテーパ面のテーパ角度α１を第２弁孔９のテーパ面のテーパ角度α２より小さくした場合は、前記最小間隙Ｓ２は第２弁孔９の下流側端部の位置Ｙ２において測定することができる。   (8) In the sixth embodiment, the taper angle α1 of the taper surface of the second valve body portion 64 and the taper angle α2 of the taper surface of the second valve hole 9 may be different. When the taper angle α1 of the taper surface of the second valve body 64 is larger than the taper angle α2 of the taper surface of the second valve hole 9, the minimum gap S2 is upstream of the taper surface of the second valve body 64. It can be measured at the position X1 of the side end. On the contrary, when the taper angle α1 of the taper surface of the second valve body 64 is smaller than the taper angle α2 of the taper surface of the second valve hole 9, the minimum gap S2 is the downstream end of the second valve hole 9. Can be measured at the position Y2.

本発明の膨張弁は、空気調和装置、冷蔵庫、その他の冷凍装置における冷媒回路に使用される。空気調和装置は一体型、分離型、マルチ型など他用途に使用できる。   The expansion valve of the present invention is used in a refrigerant circuit in an air conditioner, a refrigerator, and other refrigeration apparatuses. The air conditioner can be used for other purposes such as an integrated type, a separate type, and a multi type.

本発明の実施の形態１に係る膨張弁の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 1 of this invention. 図１におけるＡ−Ａ矢視断面図である。It is AA arrow sectional drawing in FIG. 本発明の実施の形態２に係る膨張弁の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 2 of this invention. 図３におけるＢ−Ｂ矢視断面図である。It is a BB arrow sectional view in FIG. 本発明の実施の形態３に係る膨張弁の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 3 of this invention. 本発明の実施の形態４に係る膨張弁の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 4 of this invention. 本発明の実施の形態５に係る膨張弁の要部縦断面図である。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 5 of this invention. 図７におけるＣ−Ｃ矢視断面図である。It is CC sectional view taken on the line in FIG. 本発明の実施の形態６に係る膨張弁の要部縦断面図であって、最大開度の状態を示す。It is a principal part longitudinal cross-sectional view of the expansion valve which concerns on Embodiment 6 of this invention, Comprising: The state of a maximum opening degree is shown. 図９におけるＤ−Ｄ断面図である。It is DD sectional drawing in FIG. 従来の冷凍装置の基本的冷媒回路図であって、セパレート型空気調和機の基本的な冷媒回路を示す。It is a basic refrigerant circuit diagram of the conventional freezing apparatus, Comprising: The basic refrigerant circuit of a separate type air conditioner is shown. 同冷媒回路に使用される膨張弁の基本構造図である。It is a basic structure figure of the expansion valve used for the refrigerant circuit.

符号の説明Explanation of symbols

α１、α２、β１、β２ テーパ角度
ｄ１、ｄ２ 直径
Ｓ１ 間隙
Ｓ２ 最小間隙
Ｘ１、Ｘ２、Ｙ１、Ｙ２ 位置
１、２１ 弁本体
２、２２ 冷媒流通路
３、２３ 弁体
４、２４ 第１絞り部
５、２５ 第２絞り部
６、２６ 第１仕切壁
７、２７ 第２仕切壁
８、２８ 第１弁孔
９、２９、５９、６９ 第２弁孔
１２，３２ 連結部
１３、３３ 第１弁体部
１４、３４、４４ 、６４ 第２弁体部
１５、３５、５５、６５ 溝部
１６、３６、５６、６６ 通路
７１ 拡大空間部
７２ 第１異径接合部
７３ 第２異径接合部 α1, α2, β1, β2 Taper angle d1, d2 Diameter S1 Gap S2 Minimum gap X1, X2, Y1, Y2 Positions 1, 21 Valve body 2, 22 Refrigerant flow passage 3, 23 Valve body 4, 24 First throttle 5 , 25 Second restricting portion 6, 26 First partition wall 7, 27 Second partition wall 8, 28 First valve hole 9, 29, 59, 69 Second valve hole 12, 32 Connecting portion 13, 33 First valve body Portions 14, 34, 44, 64 Second valve body portions 15, 35, 55, 65 Groove portions 16, 36, 56, 66 Passage 71 Expansion space 72 First different diameter joint portion 73 Second different diameter joint portion

Claims (15)

弁本体と、弁本体内部に形成された冷媒流通路と、弁本体内に収納された弁体と、冷媒流通路に形成された第１絞り部と、冷媒流通路における第１絞り部の上流側に形成された第２絞り部とを有し、
弁本体は、冷媒流通路における冷媒の流れを仕切る第１仕切壁と、冷媒流通路の第１仕切壁の上流側における冷媒の流れを仕切る第２仕切壁とを備え、さらに、第１仕切壁には第１弁孔が形成され、第２仕切壁には第２弁孔が形成され、
弁体は、外周面がテーパ状に形成され、かつ、このテーパ状の外周面が第１弁孔の弁座に当接し得る第１弁体部と外周面が第２弁孔の内周面に対向する第２弁体部とを備えた棒状部材からなり、
第１絞り部は、第１弁孔の弁座に対し第１弁体部を進退させることにより、第１弁孔と第１弁体部との間に形成されるものであって、全閉可能かつ開度可変に形成され、
第２絞り部は、相互に対向する第２弁孔の内周面と弁体の第２弁体部の外周面との何れか一方に弁体の進退方向に延びる複数の溝部を形成し、この複数の溝部とこの溝部に対向する第２弁孔の内周面又は第２弁体部の外周面とにより、複数の略独立の通路が形成されたものであり、さらに、第２弁孔の内周面又は第２弁体部の外周面の少なくとも何れか一方が弁体の中心軸に対し傾斜するテーパ面に形成されてなることを特徴とする膨張弁。 A valve body; a refrigerant flow passage formed in the valve body; a valve body housed in the valve body; a first throttle portion formed in the refrigerant flow passage; and an upstream of the first throttle portion in the refrigerant flow passage. A second diaphragm formed on the side,
The valve body includes a first partition wall that partitions the refrigerant flow in the refrigerant flow passage, and a second partition wall that partitions the refrigerant flow on the upstream side of the first partition wall of the refrigerant flow passage. The first valve hole is formed in the second partition wall, the second valve hole is formed in the second partition wall,
The valve body has an outer peripheral surface formed in a tapered shape, and the outer peripheral surface of the first valve body and the outer peripheral surface of which the tapered outer peripheral surface can contact the valve seat of the first valve hole are the inner peripheral surface of the second valve hole. A rod-shaped member provided with a second valve body portion opposed to
The first restrictor is formed between the first valve hole and the first valve body part by moving the first valve body part forward and backward with respect to the valve seat of the first valve hole, and is fully closed. Possible and variable opening,
The second throttle portion forms a plurality of grooves extending in the advancing and retreating direction of the valve body on either one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion of the valve body, A plurality of substantially independent passages are formed by the plurality of groove portions and the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion facing the groove portions, and further, the second valve hole The expansion valve is characterized in that at least one of the inner peripheral surface and the outer peripheral surface of the second valve body portion is formed as a tapered surface inclined with respect to the central axis of the valve body. 弁本体と、弁本体内部に形成された冷媒流通路と、弁本体内に収納された弁体と、冷媒流通路に形成された第１絞り部と、冷媒流通路における第１絞り部の上流側に形成された第２絞り部とを有し、
弁本体は、冷媒流通路における冷媒の流れを仕切る第１仕切壁と、冷媒流通路の第１仕切壁の上流側における冷媒の流れを仕切る第２仕切壁とを備え、さらに、第１仕切壁には第１弁孔が形成され、第２仕切壁には第２弁孔が形成され、
弁体は、外周面がテーパ状に形成され、かつ、このテーパ状の外周面が第１弁孔に対向する第１弁体部と外周面が第２弁孔の内周面に対向する第２弁体部とを備えた棒状部材からなり、
第１絞り部は、第１弁孔の弁座に対し第１弁体部を進退させることにより、第１弁孔と第１弁体部との間に形成されるものであって、開度可変に形成され、
第２絞り部は、相互に対向する第２弁孔の内周面と弁体の第２弁体部の外周面との何れか一方に弁体の進退方向に延びる複数の溝部を形成し、この複数の溝部とこの溝部に対向する第２弁孔の内周面又は第２弁体部の外周面とにより、複数の略独立の通路が形成されたものであり、さらに、第２弁孔の内周面又は第２弁体部の外周面の少なくとも何れか一方が弁体の中心軸に対し傾斜するテーパ面に形成されてなることを特徴とする膨張弁。 A valve body; a refrigerant flow passage formed in the valve body; a valve body housed in the valve body; a first throttle portion formed in the refrigerant flow passage; and an upstream of the first throttle portion in the refrigerant flow passage. A second diaphragm formed on the side,
The valve body includes a first partition wall that partitions the refrigerant flow in the refrigerant flow passage, and a second partition wall that partitions the refrigerant flow on the upstream side of the first partition wall of the refrigerant flow passage. The first valve hole is formed in the second partition wall, the second valve hole is formed in the second partition wall,
The valve body has an outer peripheral surface formed in a taper shape, and a first valve body portion in which the tapered outer peripheral surface opposes the first valve hole and an outer peripheral surface in opposition to the inner peripheral surface of the second valve hole. It consists of a rod-shaped member with two valve bodies,
The first throttle portion is formed between the first valve hole and the first valve body portion by moving the first valve body portion forward and backward with respect to the valve seat of the first valve hole, and has an opening degree Variably formed,
The second throttle portion forms a plurality of grooves extending in the advancing and retreating direction of the valve body on either one of the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion of the valve body, A plurality of substantially independent passages are formed by the plurality of groove portions and the inner peripheral surface of the second valve hole or the outer peripheral surface of the second valve body portion facing the groove portions, and further, the second valve hole The expansion valve is characterized in that at least one of the inner peripheral surface and the outer peripheral surface of the second valve body portion is formed as a tapered surface inclined with respect to the central axis of the valve body. 前記複数の溝部が等間隔に形成されていることを特徴とする請求項１又は２記載の膨張弁。   The expansion valve according to claim 1 or 2, wherein the plurality of grooves are formed at equal intervals. 前記第２弁孔の内周面及び第２弁体部の外周面の双方を、互いに平行なテーパ面に形成したことを特徴とする請求項１〜３の何れか１項記載の膨張弁。   The expansion valve according to any one of claims 1 to 3, wherein both the inner peripheral surface of the second valve hole and the outer peripheral surface of the second valve body portion are formed as tapered surfaces parallel to each other. 前記弁体は、前記棒状部材の先端部に第１弁体部が形成され、前記棒状部材の中間部に第２弁体部が形成され、
第２弁体部の外周面及び第２弁孔の内周面は弁体の先端部に向かって先細のテーパ面に形成されていることを特徴とする請求項１〜４の何れか１項記載の膨張弁。 The valve body has a first valve body portion formed at a tip portion of the rod-shaped member, and a second valve body portion formed at an intermediate portion of the rod-shaped member,
The outer peripheral surface of the second valve body portion and the inner peripheral surface of the second valve hole are formed in a tapered surface tapered toward the tip end portion of the valve body. The expansion valve described. 前記複数の溝部は、第２弁体部の外周面を構成するテーパ面に形成されていることを特徴とする請求項１〜５の何れか１項記載の膨張弁。   The expansion valve according to any one of claims 1 to 5, wherein the plurality of groove portions are formed on a tapered surface constituting an outer peripheral surface of the second valve body portion. 前記第２弁体部の外周面を構成するテーパ面の上流側端部は、第２絞り部の最小から最大の何れの開度においても第２弁孔内に位置するように構成されていることを特徴とする請求項５又は６記載の膨張弁。   The upstream end portion of the tapered surface constituting the outer peripheral surface of the second valve body portion is configured to be located in the second valve hole at any opening degree from the minimum to the maximum of the second throttle portion. The expansion valve according to claim 5 or 6. 前記第２絞り部から第１弁孔に至る冷媒通路における第１弁孔の入口側部に拡大空間部を形成するとともに、第２絞り部の最小から最大の何れの開度においても、第２弁体部の外周面を構成するテーパ面の下流側端部が拡大空間部内に位置するように構成されていることを特徴とする請求項５〜７の何れか１項記載の膨張弁。   An enlarged space portion is formed at the inlet side portion of the first valve hole in the refrigerant passage extending from the second throttle portion to the first valve hole, and at any opening from the minimum to the maximum of the second throttle portion. The expansion valve according to any one of claims 5 to 7, wherein a downstream end portion of the tapered surface constituting the outer peripheral surface of the valve body portion is positioned in the enlarged space portion. 前記第１絞り部入口側における第１弁体部と第１弁孔との間隙は、第１絞り部及び第２絞り部の何れの開度においても、前記第２絞り部における第２弁体部と第２弁孔との最小間隙より小さいことを特徴とする請求項５〜８の何れか１項記載の膨張弁。   The gap between the first valve body part and the first valve hole on the inlet side of the first throttle part is the second valve body in the second throttle part at any opening degree of the first throttle part and the second throttle part. The expansion valve according to any one of claims 5 to 8, wherein the expansion valve is smaller than a minimum gap between the first portion and the second valve hole. 前記第２弁体部の外周面を成すテーパ面及び第２弁孔の内周面を成すテーパ面は、同一のテーパ角度に形成され、さらに、前記第１弁体部の外周面を構成するテーパ面のテーパ角度は、前記第２弁孔の内周面を成すテーパ面のテーパ角度より大きいことを特徴とする請求項５〜９の何れか１項記載の膨張弁。   The tapered surface forming the outer peripheral surface of the second valve body portion and the tapered surface forming the inner peripheral surface of the second valve hole are formed at the same taper angle, and further constitute the outer peripheral surface of the first valve body portion. The expansion valve according to any one of claims 5 to 9, wherein a taper angle of the taper surface is larger than a taper angle of a taper surface forming an inner peripheral surface of the second valve hole. 前記第２弁孔の内周面を成すテーパ面のテーパ角度は、略５度〜略６０度であることを特徴とする請求項１０記載の膨張弁。   The expansion valve according to claim 10, wherein a taper angle of a taper surface forming an inner peripheral surface of the second valve hole is approximately 5 degrees to approximately 60 degrees. 前記弁体における前記第２弁体部の上流側端部に連結される連結部の直径は、第２弁体部を構成するテーパ面における最大外周部の直径より小さいことを特徴とする請求項５〜１１の何れか１項記載の膨張弁。   The diameter of the connection part connected with the upstream edge part of the said 2nd valve body part in the said valve body is smaller than the diameter of the largest outer peripheral part in the taper surface which comprises a 2nd valve body part. The expansion valve according to any one of 5 to 11. 前記第２弁体部の外周面の上流側端部と前記弁体における前記第２弁体部の上流側端部に連結される連結部と間に、第２弁体部の外周面の上流側端部から前記連結部の外周面に向かってテーパ状に縮径する第２異径接合部が形成されていることを特徴とする請求項１２記載の膨張弁。   Upstream of the outer peripheral surface of the second valve body portion between the upstream end portion of the outer peripheral surface of the second valve body portion and the connecting portion connected to the upstream end portion of the second valve body portion in the valve body. The expansion valve according to claim 12, wherein a second different-diameter joint portion that is tapered in a tapered shape from a side end portion toward an outer peripheral surface of the connecting portion is formed. 前記第２弁体部の外周面の下流側端部と第１弁体部の外周面の上流側端部との間に、第２弁体部の外周面の下流側端部から前記第１弁体部の外周面の上流側端部に向かってテーパ状に縮径する第１異径接合部が形成され、第１異径接合部のテーパ角度が第１弁体部のテーパ状外周面のテーパ角度より大きいことを特徴とする請求項５〜１３の何れか１項に記載の膨張弁。   Between the downstream end portion of the outer peripheral surface of the second valve body portion and the upstream end portion of the outer peripheral surface of the first valve body portion, the first end from the downstream end portion of the outer peripheral surface of the second valve body portion. A first different-diameter joint that is tapered toward the upstream end of the outer peripheral surface of the valve body is formed, and the taper angle of the first different-diameter joint is a tapered outer peripheral surface of the first valve body. The expansion valve according to claim 5, wherein the expansion valve is larger than the taper angle. 請求項１〜１４の何れか１項に記載の膨張弁を使用してなる冷凍装置。   A refrigerating apparatus using the expansion valve according to any one of claims 1 to 14.
JP2005362503A 2005-02-28 2005-12-15 Expansion valve and freezing apparatus Pending JP2006266667A (en)

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