JP2008298307A - Refrigerating cycle - Google Patents

Refrigerating cycle Download PDF

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JP2008298307A
JP2008298307A JP2007141606A JP2007141606A JP2008298307A JP 2008298307 A JP2008298307 A JP 2008298307A JP 2007141606 A JP2007141606 A JP 2007141606A JP 2007141606 A JP2007141606 A JP 2007141606A JP 2008298307 A JP2008298307 A JP 2008298307A
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refrigerant
condensed water
refrigeration cycle
pressure side
side refrigerant
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Keiichi Tomaru
敬一 外丸
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Sanden Corp
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Sanden Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating cycle capable of inexpensively, surely and efficiently improving coefficient of refrigerating performance by effectively utilizing condensate water of low temperature generated in an evaporator. <P>SOLUTION: In this refrigerating cycle comprising a compressor 2, a radiator 3, an expander 4, an evaporator 5, and an internal heat exchanger 7 exchanging heat between a low pressure-side refrigerant flowing out from the evaporator 5 and distributed to the compressor 2, and a high pressure-side refrigerant flowing out from the radiator 3 and distributed to the expander 4, a high pressure-side refrigerant cooling means 12 is disposed to allow the condensate water as a cooling medium generated in the evaporator 5, to be kept into contact with a high pressure-side refrigerant pipe from the internal heat exchanger 7 to the expander 4. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、車両用空調装置等に好適な冷凍サイクルに関し、とくに、冷媒の超臨界作動域を有する場合に好適な冷凍サイクルに関する。   The present invention relates to a refrigeration cycle suitable for a vehicle air conditioner and the like, and more particularly to a refrigeration cycle suitable for a refrigerant having a supercritical operating range.

冷凍サイクルにおいては、例えば車両用空調装置に用いられる冷凍サイクルにおいては、環境問題への配慮の側面から、従来のフロン系に代わる冷媒が求められつつあり、代替冷媒として、超臨界作動域を有する冷媒、とくに二酸化炭素冷媒が提案されている（例えば、特許文献１）。二酸化炭素冷媒は無毒、不燃性であるが、臨界温度が低く（約31℃）、二酸化炭素冷媒を使用したサイクルでは、高圧側圧力が超臨界状態（約7.4MPa以上）になる遷臨界サイクル（超臨界冷凍サイクル）となる。このような冷凍サイクルでは、一般的に、フロンを使用したものと比較して冷凍成績係数（ＣＯＰ：Coefficient of Performance）が悪いため、これを向上させることが求められている。   In the refrigeration cycle, for example, in the refrigeration cycle used for vehicle air conditioners, refrigerants that replace conventional chlorofluorocarbons are being demanded from the viewpoint of consideration of environmental problems, and have a supercritical operating range as an alternative refrigerant. A refrigerant, particularly a carbon dioxide refrigerant has been proposed (for example, Patent Document 1). Carbon dioxide refrigerant is non-toxic and non-flammable, but the critical temperature is low (about 31 ℃), and in the cycle using carbon dioxide refrigerant, the high pressure side pressure becomes supercritical state (about 7.4MPa or more) Supercritical refrigeration cycle). In such a refrigeration cycle, since the refrigeration coefficient of performance (COP) is generally poorer than that using chlorofluorocarbon, it is required to improve this.

その一つの手法として、冷凍サイクル内に配置した内部熱交換器を用いて放熱器出口側の高圧側冷媒と蒸発器出口側の低圧側冷媒との間で熱交換する方法が知られている。これにより、高圧側冷媒温度を低減することができ、蒸発器入口側のエンタルピーを低減し、蒸発器における入口側と出口側との間のエンタルピー差を増大させることで、冷凍成績係数の向上を実現している。
特公平７−１８６０２号公報 As one of the methods, there is known a method of exchanging heat between a high-pressure side refrigerant on the radiator outlet side and a low-pressure side refrigerant on the evaporator outlet side using an internal heat exchanger arranged in the refrigeration cycle. This can reduce the high-pressure side refrigerant temperature, reduce the enthalpy on the evaporator inlet side, and increase the enthalpy difference between the inlet side and outlet side in the evaporator, thereby improving the refrigeration performance coefficient. Realized.
Japanese Patent Publication No. 7-18602

ところが、上記のような冷媒の超臨界作動域を有する冷凍サイクルにおいては、高負荷時に高圧側冷媒が超臨界状態となるため気液二層流にならず（凝縮せず）、蒸発器の上流側に配置される膨張器入口側のエンタルピーが外気温度に支配されてしまう。その結果、特定の温度（圧力）においては、特定の圧力（温度）点で冷凍成績係数の最大値を示す特性となるが、このような冷凍成績係数の最大値を狙うには、とくに、膨張器、さらには蒸発器へと導かれる冷媒を外気温度よりも低温の冷却媒体で冷却することが必要になる。しかし、特別な冷却媒体を準備し使用するのでは、冷凍サイクルの構造が複雑になるとともに、サイクル全体のコストが増加する。   However, in the refrigeration cycle having the supercritical operating range of the refrigerant as described above, the high-pressure side refrigerant is in a supercritical state at a high load, so that it does not become a gas-liquid two-layer flow (no condensation) and upstream of the evaporator. The enthalpy on the inlet side of the expander arranged on the side is dominated by the outside air temperature. As a result, at a specific temperature (pressure), the characteristic shows the maximum value of the refrigeration performance coefficient at a specific pressure (temperature) point. It is necessary to cool the refrigerant guided to the evaporator and further to the evaporator with a cooling medium having a temperature lower than the outside air temperature. However, if a special cooling medium is prepared and used, the structure of the refrigeration cycle becomes complicated and the cost of the entire cycle increases.

そこで本発明の課題は、冷凍サイクル内の蒸発器で発生する低温の凝縮水を有効利用することにより、冷凍成績係数の向上を安価にかつ確実にしかも効率よく実現可能な冷凍サイクルを提供することにある。   Accordingly, an object of the present invention is to provide a refrigeration cycle that can efficiently and efficiently realize improvement in the refrigeration performance coefficient by effectively using low-temperature condensed water generated by an evaporator in the refrigeration cycle. It is in.

上記課題を解決するために、本発明に係る冷凍サイクルは、冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を冷却する放熱器と、該放熱器により冷却された冷媒を減圧膨張させる膨張器と、該膨張器により減圧膨張された冷媒を蒸発させる蒸発器と、該蒸発器から流出され前記圧縮機へと送られる低圧側冷媒と前記放熱器から前記膨張器へと送られる高圧側冷媒との間で熱交換を行う内部熱交換器を備えた冷凍サイクルにおいて、前記蒸発器で発生する凝縮水を、前記内部熱交換器から前記膨張器までの高圧側冷媒の配管に冷却媒体として接触させる高圧側冷媒冷却手段を設けたことを特徴とするものからなる。   In order to solve the above problems, a refrigeration cycle according to the present invention includes a compressor that compresses a refrigerant, a radiator that cools the refrigerant compressed by the compressor, and decompresses and expands the refrigerant cooled by the radiator. An evaporator for evaporating the refrigerant decompressed and expanded by the expander, a low-pressure refrigerant that flows out from the evaporator and is sent to the compressor, and a high pressure that is sent from the radiator to the expander In a refrigeration cycle having an internal heat exchanger for exchanging heat with the side refrigerant, the condensate generated by the evaporator is supplied to the high-pressure side refrigerant piping from the internal heat exchanger to the expander as a cooling medium. The high-pressure side refrigerant cooling means for contacting is provided.

このような本発明に係る冷凍サイクルにおいては、冷凍サイクル内の蒸発器で発生する低温の凝縮水が冷媒を冷却するための冷却媒体として有効に利用され、とくに内部熱交換器から膨張器までの高圧側冷媒の配管に（膨張器直前の高圧側冷媒配管に）その低温の凝縮水が接触されることで、配管内を流れる高圧側冷媒が確実に効率よく冷却される。また、特別な冷却媒体ではなく冷凍サイクル内で発生した凝縮水が冷却媒体として使用されるので、冷凍サイクルの構造を大幅に複雑化することなく、安価に実施可能となる。高圧側冷媒は、膨張器前で外気温度よりもはるかに低温の蒸発器で発生した凝縮水によって冷却されるので、実質的に外気温度に左右されることなく所望の冷却が可能になる。そして、冷却された冷媒が、膨張器での減圧膨張後に蒸発器へと流入されるので、蒸発器入口側の冷媒温度が安定して低温化され、蒸発器入口側のエンタルピーが低減され、蒸発器における入口側と出口側との間のエンタルピー差が増大されて、冷凍サイクルの冷凍成績係数が向上される。   In such a refrigeration cycle according to the present invention, low-temperature condensed water generated in an evaporator in the refrigeration cycle is effectively used as a cooling medium for cooling the refrigerant, and particularly from the internal heat exchanger to the expander. By contacting the low-temperature condensed water with the high-pressure side refrigerant pipe (to the high-pressure side refrigerant pipe immediately before the expander), the high-pressure side refrigerant flowing in the pipe is reliably cooled efficiently. Further, since condensed water generated in the refrigeration cycle, not a special cooling medium, is used as the cooling medium, it can be implemented at low cost without greatly complicating the structure of the refrigeration cycle. Since the high-pressure side refrigerant is cooled by the condensed water generated in the evaporator at a temperature much lower than the outside air temperature before the expander, the desired cooling can be achieved substantially without being influenced by the outside air temperature. Then, since the cooled refrigerant flows into the evaporator after decompression expansion in the expander, the refrigerant temperature on the evaporator inlet side is stably lowered, the enthalpy on the evaporator inlet side is reduced, and evaporation The enthalpy difference between the inlet side and the outlet side in the vessel is increased and the refrigeration cycle coefficient of refrigeration cycle is improved.

この本発明に係る冷凍サイクルは、とくに使用冷媒が超臨界領域での作動域を有するものからなる場合に有効であり、とくに冷媒が二酸化炭素からなる場合に有効なものである。ただし、二酸化炭素以外の、超臨界領域での作動域を有する冷媒を使用する場合にも有効であることは言うまでもない。   This refrigeration cycle according to the present invention is particularly effective when the refrigerant used has an operating range in the supercritical region, and is particularly effective when the refrigerant consists of carbon dioxide. However, it goes without saying that the present invention is also effective when a refrigerant having an operating range in the supercritical region other than carbon dioxide is used.

上記高圧側冷媒冷却手段としては、種々の具体的な構成を採り得る。たとえば、蒸発器で発生する凝縮水を排出するドレンホースを、内部熱交換器から膨張器までの高圧側冷媒の配管に、内部を凝縮水が流下可能な形態で被せた高圧側冷媒冷却手段に構成することが可能である。また、蒸発器で発生する凝縮水を一旦貯留するチャンバを有し、該チャンバ内に内部熱交換器から膨張器までの高圧側冷媒の配管を通した高圧側冷媒冷却手段に構成することも可能である。   Various specific configurations may be adopted as the high-pressure side refrigerant cooling means. For example, the drain hose that discharges the condensed water generated in the evaporator is connected to the high-pressure side refrigerant cooling means that covers the inside of the high-pressure side refrigerant pipe from the internal heat exchanger to the expander so that the condensed water can flow down. It is possible to configure. It is also possible to configure a high-pressure side refrigerant cooling means having a chamber for temporarily storing the condensed water generated in the evaporator and passing a high-pressure side refrigerant pipe from the internal heat exchanger to the expander in the chamber. It is.

後者の構成の高圧側冷媒冷却手段の場合には、チャンバの底部に、冷媒の臨界温度を検知可能で、該冷媒の臨界温度を検知したときに開いてチャンバ内に貯留されていた凝縮水を排出可能な臨界温度検知開閉弁が設けられている構成とすることができる。このような構成では、貯留される凝縮水の温度が冷媒の臨界温度まで上昇すると、チャンバ外に排出され、その分新たな低温の凝縮水がチャンバ内に導入されるので、チャンバ内に貯留される凝縮水の温度は常時冷媒の臨界温度よりも低い温度とされ、確実に効率のよい冷媒の冷却が行われることになる。   In the case of the high-pressure side refrigerant cooling means of the latter configuration, the critical temperature of the refrigerant can be detected at the bottom of the chamber, and the condensed water that has been opened and stored in the chamber when the critical temperature of the refrigerant is detected. It can be set as the structure provided with the critical temperature detection opening / closing valve which can be discharged | emitted. In such a configuration, when the temperature of the stored condensed water rises to the critical temperature of the refrigerant, the condensed water is discharged out of the chamber, and new low-temperature condensed water is introduced into the chamber. The temperature of the condensed water is always lower than the critical temperature of the refrigerant, so that efficient cooling of the refrigerant is surely performed.

また、上記チャンバの底部に、チャンバ内に所定重量以上の凝縮水が貯留されたときに開いてチャンバ内の凝縮水を排出可能な凝縮水重量検知開閉弁が設けられている構成とすることもできる。このような構成では、チャンバ内には常時所定量の凝縮水が安定して貯留されるとともに、貯留されていた凝縮水が続いて導入されてくる熱交換前の低温の凝縮水に順次入れ代わることになるので、貯留凝縮水は低温状態に保たれ、高圧側冷媒との効率のよい熱交換が継続されることになる。   In addition, a condensate weight detection opening / closing valve may be provided at the bottom of the chamber that is open when condensed water of a predetermined weight or more is stored in the chamber and can discharge the condensate in the chamber. it can. In such a configuration, a predetermined amount of condensed water is constantly stably stored in the chamber, and the stored condensed water is successively replaced with low-temperature condensed water before heat exchange that is subsequently introduced. Therefore, the stored condensate is kept at a low temperature, and efficient heat exchange with the high-pressure side refrigerant is continued.

これら具体的な高圧側冷媒冷却手段の構成においては、凝縮水が接触される高圧側冷媒配管にローフィンチューブなどを使用すれば、凝縮水との熱交換効率がより高められ、さらに効率よく冷凍成績係数を向上させることが可能になる。   In these specific configurations of the high-pressure side refrigerant cooling means, if a low fin tube or the like is used for the high-pressure side refrigerant pipe in contact with the condensed water, the heat exchange efficiency with the condensed water can be further increased, and the refrigeration can be performed more efficiently. It is possible to improve the coefficient of performance.

本発明に係る冷凍サイクルは、とくに冷凍成績係数の向上の要求が高い車両用空調装置に用いられる冷凍サイクルとして好適なものである。   The refrigeration cycle according to the present invention is particularly suitable as a refrigeration cycle used in a vehicle air conditioner that is highly demanded to improve the refrigeration performance coefficient.

このように、本発明に係る冷凍サイクルによれば、冷凍サイクル内の蒸発器で発生する低温の凝縮水を冷却媒体として有効に利用した高圧側冷媒冷却手段により、膨張器直前の高圧側冷媒を確実に冷却できるようにしたので、簡単な構成でありながら蒸発器入口側の冷媒を低温化して蒸発器における入口側と出口側との間のエンタルピー差を増大させ、冷凍サイクルの冷凍成績係数を確実に効率よくしかも安価に向上することが可能になる。とくに二酸化炭素を代表とする超臨界領域での作動域を有する冷媒を使用する冷凍サイクルの冷凍成績係数を効果的に向上することが可能になる。   Thus, according to the refrigeration cycle according to the present invention, the high-pressure side refrigerant cooling means that effectively uses the low-temperature condensed water generated in the evaporator in the refrigeration cycle as the cooling medium, Since it was able to cool reliably, the refrigerant on the evaporator inlet side was cooled to increase the enthalpy difference between the inlet side and outlet side of the evaporator while having a simple configuration, and the refrigeration cycle coefficient of refrigeration was increased. It is possible to improve efficiently and inexpensively. In particular, it is possible to effectively improve the refrigeration performance coefficient of a refrigeration cycle that uses a refrigerant having an operating range in a supercritical region typified by carbon dioxide.

以下に、本発明の望ましい実施の形態について、図面を参照しながら説明する。
図１は、本発明の一実施態様に係る冷凍サイクルの回路構成を示しており、例えば車両用空調装置に用いられる二酸化炭素冷媒を使用した冷凍サイクルの回路構成の一例を示している。図１に示す冷凍サイクル１は、冷媒を圧縮する圧縮機２と、該圧縮機２により圧縮された冷媒を冷却する放熱器３（ガスクーラ）と、該放熱器３により冷却された冷媒を減圧膨張させる膨張器４（例えば、膨張弁）と、該膨張器４により減圧膨張された冷媒を蒸発させる蒸発器５と、該蒸発器５から流出した冷媒を気相冷媒と液相冷媒とに分離し分離された気相冷媒を内部熱交換器７の低圧側通路へ流出させるアキュームレータ６と、蒸発器５から流出されアキュームレータ６を通して圧縮機２へと送られる低圧側冷媒と上記放熱器３から膨張器４へと送られる高圧側冷媒との間で熱交換を行う内部熱交換器７を備えている。これら機器が、順次、配管を介して接続されており、図１における矢印が冷媒の流れ方向を示している。 Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
FIG. 1 shows a circuit configuration of a refrigeration cycle according to an embodiment of the present invention. For example, FIG. 1 shows an example of a circuit configuration of a refrigeration cycle using a carbon dioxide refrigerant used in a vehicle air conditioner. A refrigeration cycle 1 shown in FIG. 1 includes a compressor 2 that compresses refrigerant, a radiator 3 (gas cooler) that cools the refrigerant compressed by the compressor 2, and decompresses and expands the refrigerant cooled by the radiator 3. An expander 4 (for example, an expansion valve) to be evaporated, an evaporator 5 that evaporates the refrigerant decompressed and expanded by the expander 4, and a refrigerant that has flowed out of the evaporator 5 is separated into a gas phase refrigerant and a liquid phase refrigerant. An accumulator 6 that causes the separated vapor-phase refrigerant to flow out to the low-pressure side passage of the internal heat exchanger 7, a low-pressure side refrigerant that flows out from the evaporator 5 and is sent to the compressor 2 through the accumulator 6, and an expander from the radiator 3 4 is provided with an internal heat exchanger 7 that performs heat exchange with the high-pressure side refrigerant sent to 4. These devices are sequentially connected via a pipe, and the arrows in FIG. 1 indicate the flow direction of the refrigerant.

このような冷凍サイクル１においては、蒸発器５内における冷媒の蒸発により、周囲から熱が奪われるので、蒸発器５の外表面には低温の凝縮水が発生し、その凝縮水が蒸発器５の表面積当たりある量以上になると、蒸発器５の外表面を伝って流下することになる。一般に、この凝縮水は、受けトレイ８等によって集められ、そのドレン口９からドレンホース１０等を介して系外に排出されている。   In such a refrigeration cycle 1, heat is taken away from the surroundings due to the evaporation of the refrigerant in the evaporator 5, so low-temperature condensed water is generated on the outer surface of the evaporator 5, and the condensed water is converted into the evaporator 5. When the amount exceeds a certain amount per surface area, it flows down along the outer surface of the evaporator 5. Generally, this condensed water is collected by the receiving tray 8 etc., and is discharged | emitted out of the system from the drain port 9 via the drain hose 10 grade | etc.,.

本発明においては、この低温の凝縮水が冷却媒体として有効に利用され、該凝縮水が内部熱交換器７から膨張器４までの高圧側冷媒の配管１１に接触される高圧側冷媒冷却手段１２が構成される。   In the present invention, this low-temperature condensed water is effectively used as a cooling medium, and the condensed water is brought into contact with the high-pressure side refrigerant pipe 11 from the internal heat exchanger 7 to the expander 4. Is configured.

高圧側冷媒冷却手段１２は、具体的には、例えば図２や図３に示すように構成される。ただし、具体的な構造はこれらの実施例に限定されるものではない。図２に示す実施例では、蒸発器５で発生した凝縮水を排出するドレン口９に接続されたドレンホース１０が、膨張器４の手前の高圧側冷媒配管１１に、内部を凝縮水が流下可能な形態で被せられている。本実施例では、らせん状に延設された高圧側冷媒配管１１に沿うようにドレンホース１０が被せられ、ドレンホース１０内に導入された凝縮水が高圧側冷媒配管１１と接触することにより配管１１内を流れる冷媒と熱交換されて冷媒が冷却され、熱交換後の凝縮水１３は系外に排出される。ドレンホース１０内を通過された後の配管１１ａは膨張器４へと接続されている。   Specifically, the high-pressure side refrigerant cooling means 12 is configured as shown in FIGS. 2 and 3, for example. However, the specific structure is not limited to these examples. In the embodiment shown in FIG. 2, the drain hose 10 connected to the drain port 9 for discharging the condensed water generated in the evaporator 5 flows into the high-pressure side refrigerant pipe 11 in front of the expander 4. It is covered in a possible form. In the present embodiment, the drain hose 10 is covered along the high-pressure side refrigerant pipe 11 that extends in a spiral shape, and the condensed water introduced into the drain hose 10 comes into contact with the high-pressure side refrigerant pipe 11 to form a pipe. The heat exchange with the refrigerant flowing in the refrigerant 11 cools the refrigerant, and the condensed water 13 after the heat exchange is discharged out of the system. The pipe 11 a after being passed through the drain hose 10 is connected to the expander 4.

このような構成においては、単にドレンホース１０を所定長だけ高圧側冷媒配管１１に接触するように被せるだけで、好ましい高圧側冷媒冷却手段を構成することが可能になり、極めて簡単にかつ安価に本発明で目標とする構成が達成され、冷凍サイクルの冷凍成績係数が効果的に向上される。   In such a configuration, it is possible to configure a preferable high-pressure side refrigerant cooling means simply by covering the drain hose 10 so as to contact the high-pressure side refrigerant pipe 11 by a predetermined length, which is extremely simple and inexpensive. The target configuration of the present invention is achieved, and the refrigeration performance coefficient of the refrigeration cycle is effectively improved.

図３に示す実施例では、蒸発器５で発生しドレン口９、ドレンホース１０を介して導入されてきた凝縮水を一旦貯留するチャンバ２１（ドレンチャンバ）が設けられ、そのチャンバ２１内に高圧側冷媒配管１１が通されている。チャンバ２１通過後の配管１１ａは膨張器４へと接続されている。このような構成においても、チャンバ２１内に貯留された低温の凝縮水と高圧側冷媒配管１１が接触され、配管１１内を流れる冷媒と熱交換されて冷媒が冷却され、冷凍サイクルの冷凍成績係数が効果的に向上される。   In the embodiment shown in FIG. 3, a chamber 21 (drain chamber) that temporarily stores the condensed water generated in the evaporator 5 and introduced through the drain port 9 and the drain hose 10 is provided. A side refrigerant pipe 11 is passed. The pipe 11 a after passing through the chamber 21 is connected to the expander 4. Even in such a configuration, the low-temperature condensed water stored in the chamber 21 and the high-pressure side refrigerant pipe 11 are contacted, heat is exchanged with the refrigerant flowing in the pipe 11 to cool the refrigerant, and the refrigeration performance coefficient of the refrigeration cycle Is effectively improved.

この構成においては、配管１１内を流れる冷媒との熱交換により、チャンバ２１内に貯留されていた凝縮水の温度が徐々に上昇するので、高圧側冷媒との有効な熱交換を行うためには、とくに超臨界領域にある高圧側冷媒との有効な熱交換を行うためには、配管１１と接する凝縮水の温度は冷媒の臨界温度以下でなければならない。したがって、チャンバ２１の底部に、冷媒の臨界温度（二酸化炭素の場合は約３１℃）を検知可能で、冷媒の臨界温度を検知したときには開いてチャンバ２１内に貯留されていた凝縮水を排出可能な臨界温度検知開閉弁２２が設けられている。臨界温度検知開閉弁２２としては、例えば冷媒の臨界温度で開弁するバイメタル弁を使用できる。このような臨界温度検知開閉弁２２を設けておけば、その開閉作動により、チャンバ２１内に貯留されていた凝縮水の温度が冷媒の臨界温度にまで上昇すると開いて貯留されていた凝縮水の少なくとも一部が排出され、代わりに、より低温の新たな凝縮水がチャンバ２１内に導入、貯留されるので、チャンバ２１内に貯留される凝縮水の温度は常に冷媒の臨界温度よりも低い温度に保たれることになり、目標とする熱交換が常時有効に行われて、冷凍サイクルの冷凍成績係数が効果的に向上される。   In this configuration, since the temperature of the condensed water stored in the chamber 21 gradually increases due to heat exchange with the refrigerant flowing in the pipe 11, in order to perform effective heat exchange with the high-pressure side refrigerant, In particular, in order to perform effective heat exchange with the high-pressure side refrigerant in the supercritical region, the temperature of the condensed water in contact with the pipe 11 must be lower than the critical temperature of the refrigerant. Therefore, the critical temperature of the refrigerant (about 31 ° C. in the case of carbon dioxide) can be detected at the bottom of the chamber 21, and when the critical temperature of the refrigerant is detected, the condensed water stored in the chamber 21 can be discharged. A critical temperature detection opening / closing valve 22 is provided. As the critical temperature detection opening / closing valve 22, for example, a bimetal valve that opens at the critical temperature of the refrigerant can be used. If such a critical temperature detection opening / closing valve 22 is provided, when the temperature of the condensed water stored in the chamber 21 rises to the critical temperature of the refrigerant by the opening / closing operation, the condensed water stored open is stored. At least a part of the condensed water is discharged, and instead, new condensed water having a lower temperature is introduced and stored in the chamber 21, and therefore, the temperature of the condensed water stored in the chamber 21 is always lower than the critical temperature of the refrigerant. Therefore, the target heat exchange is always performed effectively, and the refrigeration performance coefficient of the refrigeration cycle is effectively improved.

また、チャンバ２１の底部に、チャンバ２１内に所定重量以上の凝縮水が貯留されたときに開いてチャンバ２１内の凝縮水を排出可能な凝縮水重量検知開閉弁２３を設けることもできる。このような構成では、チャンバ２１内には常時目標とする所定量の凝縮水が安定して貯留されることになり、順次チャンバ２１内から排出される凝縮水と入れ代わりに順次新たな低温の凝縮水が導入されてくる構成となる。チャンバ２１内に貯留される凝縮水が、熱交換前の低温の凝縮水に順次入れ代わることにより、貯留凝縮水は低温状態に保たれ、高圧側冷媒との効率のよい熱交換が継続されて、冷凍サイクルの冷凍成績係数が効果的に向上される。凝縮水重量検知開閉弁２３としては、例えば、所定レベルの水圧が加わったときに開くリード弁を使用できる。   Further, a condensed water weight detection opening / closing valve 23 that can be opened and discharged when the condensed water of a predetermined weight or more is stored in the chamber 21 can be provided at the bottom of the chamber 21. In such a configuration, a predetermined amount of condensed water that is always a target is stably stored in the chamber 21, and instead of the condensed water sequentially discharged from the chamber 21, new low-temperature condensation is sequentially added. The water is introduced. The condensate stored in the chamber 21 is sequentially replaced by low-temperature condensate before heat exchange, so that the stored condensate is kept at a low temperature, and efficient heat exchange with the high-pressure side refrigerant is continued. The refrigeration performance coefficient of the refrigeration cycle is effectively improved. As the condensed water weight detection on-off valve 23, for example, a reed valve that opens when a predetermined level of water pressure is applied can be used.

本発明に係る冷凍サイクルの構造は、とくに二酸化炭素冷媒を使用した冷凍サイクルに好適なものであり、中でも車両用空調装置の冷凍サイクルに好適なものである。   The structure of the refrigeration cycle according to the present invention is particularly suitable for a refrigeration cycle using a carbon dioxide refrigerant, and is particularly suitable for a refrigeration cycle of a vehicle air conditioner.

本発明の一実施態様に係る冷凍サイクルの回路構成図である。It is a circuit block diagram of the refrigerating cycle which concerns on one embodiment of this invention. 図１の冷凍サイクルにおける高圧側冷媒冷却手段の一例を示す概略側面図である。It is a schematic side view which shows an example of the high voltage | pressure side refrigerant | coolant cooling means in the refrigerating cycle of FIG. 図１の冷凍サイクルにおける高圧側冷媒冷却手段の別の例を示す概略縦断面図である。It is a schematic longitudinal cross-sectional view which shows another example of the high voltage | pressure side refrigerant | coolant cooling means in the refrigerating cycle of FIG.

符号の説明Explanation of symbols

１ 冷凍サイクル
２ 圧縮機
３ 放熱器
４ 膨張器
５ 蒸発器
６ アキュームレータ
７ 内部熱交換器
８ 受けトレイ
９ ドレン口
１０ ドレンホース
１１ 高圧側冷媒配管
１１ａ 膨張器へと接続される配管
１２ 高圧側冷媒冷却手段
１３ 熱交換後の凝縮水
２１ チャンバ
２２ 臨界温度検知開閉弁
２３ 凝縮水重量検知開閉弁 DESCRIPTION OF SYMBOLS 1 Refrigeration cycle 2 Compressor 3 Radiator 4 Expander 5 Evaporator 6 Accumulator 7 Internal heat exchanger 8 Receiving tray 9 Drain port 10 Drain hose 11 High pressure side refrigerant pipe 11a Pipe connected to expander 12 High pressure side refrigerant cooling Means 13 Condensate after heat exchange 21 Chamber 22 Critical temperature detection on / off valve 23 Condensate weight detection on / off valve

Claims (8)

冷媒を圧縮する圧縮機と、該圧縮機により圧縮された冷媒を冷却する放熱器と、該放熱器により冷却された冷媒を減圧膨張させる膨張器と、該膨張器により減圧膨張された冷媒を蒸発させる蒸発器と、該蒸発器から流出され前記圧縮機へと送られる低圧側冷媒と前記放熱器から前記膨張器へと送られる高圧側冷媒との間で熱交換を行う内部熱交換器を備えた冷凍サイクルにおいて、前記蒸発器で発生する凝縮水を、前記内部熱交換器から前記膨張器までの高圧側冷媒の配管に冷却媒体として接触させる高圧側冷媒冷却手段を設けたことを特徴とする冷凍サイクル。   A compressor that compresses the refrigerant; a radiator that cools the refrigerant compressed by the compressor; an expander that decompresses and expands the refrigerant cooled by the radiator; and evaporates the refrigerant decompressed and expanded by the expander And an internal heat exchanger that exchanges heat between the low-pressure side refrigerant that flows out of the evaporator and is sent to the compressor, and the high-pressure side refrigerant that is sent from the radiator to the expander. In the refrigeration cycle, the high-pressure side refrigerant cooling means for bringing the condensed water generated in the evaporator into contact with the high-pressure side refrigerant pipe from the internal heat exchanger to the expander as a cooling medium is provided. Refrigeration cycle. 前記冷媒が超臨界領域での作動域を有するものからなる、請求項１に記載の冷凍サイクル。   The refrigeration cycle according to claim 1, wherein the refrigerant has a working range in a supercritical region. 前記冷媒が二酸化炭素からなる、請求項２に記載の冷凍サイクル。   The refrigeration cycle according to claim 2, wherein the refrigerant is made of carbon dioxide. 前記高圧側冷媒冷却手段が、前記蒸発器で発生する凝縮水を排出するドレンホースを、前記内部熱交換器から前記膨張器までの高圧側冷媒の配管に、内部を凝縮水が流下可能な形態で被せた手段からなる、請求項１〜３のいずれかに記載の冷凍サイクル。   A configuration in which the high-pressure side refrigerant cooling means allows a drain hose for discharging condensed water generated in the evaporator to flow into the high-pressure side refrigerant pipe from the internal heat exchanger to the expander, and the condensed water can flow down inside. The refrigeration cycle according to any one of claims 1 to 3, comprising means covered with the above. 前記高圧側冷媒冷却手段が、前記蒸発器で発生する凝縮水を一旦貯留するチャンバを有し、該チャンバ内に前記内部熱交換器から前記膨張器までの高圧側冷媒の配管を通した手段からなる、請求項１〜３のいずれかに記載の冷凍サイクル。   The high-pressure side refrigerant cooling means has a chamber for temporarily storing condensed water generated in the evaporator, and a means for passing a high-pressure side refrigerant pipe from the internal heat exchanger to the expander in the chamber. The refrigeration cycle according to any one of claims 1 to 3. 前記チャンバの底部に、冷媒の臨界温度を検知可能で、該冷媒の臨界温度を検知したときに開いてチャンバ内に貯留されていた凝縮水を排出可能な臨界温度検知開閉弁が設けられている、請求項５に記載の冷凍サイクル。   A critical temperature detection opening / closing valve is provided at the bottom of the chamber, which can detect the critical temperature of the refrigerant and can open the condensed water stored in the chamber when the critical temperature of the refrigerant is detected. The refrigeration cycle according to claim 5. 前記チャンバの底部に、チャンバ内に所定重量以上の凝縮水が貯留されたときに開いてチャンバ内の凝縮水を排出可能な凝縮水重量検知開閉弁が設けられている、請求項５または６に記載の冷凍サイクル。   The condensed water weight detection opening / closing valve which is opened when condensed water of a predetermined weight or more is stored in the chamber and capable of discharging the condensed water in the chamber is provided at the bottom of the chamber. The refrigeration cycle described. 車両用空調装置に用いられる、請求項１〜７のいずれかに記載の冷凍サイクル。   The refrigeration cycle according to any one of claims 1 to 7, which is used in a vehicle air conditioner.
JP2007141606A 2007-05-29 2007-05-29 Refrigerating cycle Pending JP2008298307A (en)

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