JP2009264661A

JP2009264661A - Air conditioning system

Info

Publication number: JP2009264661A
Application number: JP2008114470A
Authority: JP
Inventors: Tsutomu Furukawa; 勉古川
Original assignee: Calsonic Kansei Corp
Current assignee: Marelli Corp
Priority date: 2008-04-24
Filing date: 2008-04-24
Publication date: 2009-11-12

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioning system that exhibits high heating performance during humidifying heating in a system capable of performing cooling operation and heating operation. <P>SOLUTION: This air conditioning system is equipped with an electric compressor 1, an outdoor capacitor 2, an indoor capacitor 3, a first expansion valve 6, a second expansion valve 7, an indoor evaporator 4, and an outdoor evaporator 5 connected in parallel to the indoor evaporator 4 and exchanging heat between a refrigerant made low in pressure by the second expansion valve 7 and the electric compressor 1. Switching can be performed between: a cooling circulation passage through which a high temperature high pressure refrigerant from the electric compressor 1 is lead to the outdoor capacitor 2, through the first expansion valve 6, and to the indoor evaporator 4; and a dehumidifying heating circulation passage through which the high temperature high pressure refrigerant from the electric compressor 1 is lead to the indoor capacitor 3, through the first expansion valve 6 and the second expansion valve 7, and to the indoor evaporator 4 and the outdoor evaporator 5. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、冷房運転と暖房運転が可能であり、除湿暖房が可能な空気調和システムに関する。 The present invention relates to an air conditioning system capable of cooling operation and heating operation and capable of dehumidifying heating.

この種の従来の空気調和システムとしては、特許文献１に開示されたものがある。この空気調和システム１００は、図１１に示すように、冷媒を圧縮して冷媒を高温高圧とするコンプレッサ１０１と、コンプレッサ１０１で高温高圧とされた冷媒を外気との間で熱交換させる室外コンデンサ１０２と、高温高圧の冷媒と室内に導く送風との間で熱交換させる室内コンデンサ１０３と、室内コンデンサ１０３で冷却された冷媒を減圧して低圧の冷媒とする第１減圧手段１０４と、低圧の冷媒と室内に導く送風との間で熱交換させる室内エバポレータ１０５と、コンプレッサ１０１で高温高圧とされた冷媒を室外コンデンサ１０２に供給するか、室外コンデンサ１０２をバイパスさせるバイパス経路１０６に導くか否かを選択できる三方弁１０７とを備えている。 A conventional air conditioning system of this type is disclosed in Patent Document 1. As shown in FIG. 11, the air conditioning system 100 includes a compressor 101 that compresses a refrigerant to make the refrigerant at a high temperature and a high pressure, and an outdoor capacitor 102 that exchanges heat between the refrigerant that has been heated to a high temperature and a high pressure by the compressor 101 with the outside air. And an indoor condenser 103 that exchanges heat between the high-temperature and high-pressure refrigerant and the air blown into the room, a first decompression means 104 that depressurizes the refrigerant cooled by the indoor condenser 103 to form a low-pressure refrigerant, and a low-pressure refrigerant Whether to supply heat to the indoor evaporator 105 that exchanges heat between the air and the air that is led into the room, and to the bypass condenser 106 that bypasses the outdoor condenser 102 or supplies the high-temperature and high-pressure refrigerant in the compressor 101 to the outdoor condenser 102. A three-way valve 107 that can be selected is provided.

冷房運転時には、三方弁１０７が室外コンデンサ１０２側を選択し、コンプレッサ１０１からの高温高圧の冷媒が室外コンデンサ１０２、室内コンデンサ１０３及び室内エバポレータ１０５を通る循環経路に切り替えられる。 During the cooling operation, the three-way valve 107 selects the outdoor condenser 102 side, and the high-temperature and high-pressure refrigerant from the compressor 101 is switched to a circulation path that passes through the outdoor condenser 102, the indoor condenser 103, and the indoor evaporator 105.

暖房運転時には、三方弁１０７がバイパス経路１０６側を選択し、コンプレッサ１０１からの高温高圧の冷媒が室内コンデンサ１０３と室内エバポレータ１０５のみを通る循環経路に切り替えられる。 During the heating operation, the three-way valve 107 selects the bypass path 106 side, and the high-temperature and high-pressure refrigerant from the compressor 101 is switched to a circulation path that passes only through the indoor condenser 103 and the indoor evaporator 105.

冷房運転では、室内に導かれる送風は、室内エバポレータ１０５と必要に応じて室内コンデンサ１０３を通過し、所望温度の冷風とされて室内に導かれる。そして、冷房運転における冷媒の熱の授受を見ると、冷媒の熱は室内コンデンサ１０３と室外コンデンサ１０２の双方で放熱するため、室内エバポレータ１０５では吸熱量が室内コンデンサ１０３より大きく、十分な冷房性能が期待できる。 In the cooling operation, the air blown into the room passes through the indoor evaporator 105 and the indoor condenser 103 as necessary, is cooled to a desired temperature, and is led into the room. Looking at the transfer of heat from the refrigerant in the cooling operation, the heat of the refrigerant is dissipated by both the indoor condenser 103 and the outdoor condenser 102. Therefore, the indoor evaporator 105 has a larger amount of heat absorption than the indoor condenser 103, and has sufficient cooling performance. I can expect.

暖房運転では、室内に導かれる送風は、室内エバポレータ１０５と必要に応じて室内コンデンサ１０３を通過し、所望温度の温風とされて室内に導かれる。室内に導かれる送風は、室内エバポレータ１０５を通過する際に凝縮水を発生するため、室内を除湿暖房することができる。 In the heating operation, the air blown into the room passes through the indoor evaporator 105 and the indoor condenser 103 as necessary, and is heated to a desired temperature and led into the room. The air blown into the room generates condensed water when passing through the room evaporator 105, so that the room can be dehumidified and heated.

一方、他の従来例としては、図１３に示すものが提案されている。図１３に示すように、この空気調和システム１１０は、冷媒を圧縮して冷媒を高温高圧の冷媒とするコンプレッサ１１１と、高温高圧の冷媒と室内に導く送風との間で熱交換させる室内コンデンサ１１２と、室内コンデンサ１１２の下流側の一方の分岐路に配置され、室内コンデンサ１１２で冷却された冷媒を減圧して低圧の冷媒とする第１膨張弁１１３と、第１膨張弁１１３で低圧とされた冷媒と室内に導く送風との間で熱交換させる室内エバポレータ１１４と、室内コンデンサ１１２の下流側の他方の分岐路に配置され、室内コンデンサ１１２で冷却された冷媒を減圧して低圧の冷媒とする第２膨張弁１１５と、第２膨張弁１１５で低圧とされた冷媒と室外空気との間で熱交換させる室外エバポレータ１１６と、室内エバポレータ１１４の出口側に介在され、室内エバポレータ１１４の出口側冷媒圧力が所定未満以下で閉塞し、所定圧力以上で開放する蒸発圧力調整弁１１７とを備えている。 On the other hand, as another conventional example, the one shown in FIG. 13 has been proposed. As shown in FIG. 13, the air conditioning system 110 includes an indoor condenser 112 that exchanges heat between a compressor 111 that compresses a refrigerant and uses the refrigerant as a high-temperature and high-pressure refrigerant, and a high-temperature and high-pressure refrigerant and air that is led into the room. The first expansion valve 113 is disposed in one branch path on the downstream side of the indoor condenser 112 and depressurizes the refrigerant cooled by the indoor condenser 112 to form a low pressure refrigerant, and the first expansion valve 113 reduces the pressure to a low pressure. The indoor evaporator 114 for exchanging heat between the refrigerant and the air blown into the room, and the other branch on the downstream side of the indoor condenser 112 are decompressed to reduce the pressure of the refrigerant cooled by the indoor condenser 112. The second expansion valve 115, the outdoor evaporator 116 for exchanging heat between the refrigerant whose pressure is reduced by the second expansion valve 115 and the outdoor air, and the indoor evaporator 114. Is interposed on the outlet side, the outlet side refrigerant pressure of the indoor evaporator 114 is closed in the following less than a predetermined, and a evaporation pressure adjusting valve 117 which opens at a predetermined pressure or more.

この空気調和システム１１０では、システム駆動開始時は、室内エバポレータ１１４の出口側冷媒温度が所定圧力未満以下であるため、冷媒が室内エバポレータ１１４側には流れずに、室外エバポレータ１１６側に流れる。室内に導かれる送風は、室内コンデンサ１１２を通過して温風とされ、温風が室内に導かれる。 In the air conditioning system 110, when the system is started, the refrigerant temperature on the outlet side of the indoor evaporator 114 is lower than a predetermined pressure, so that the refrigerant does not flow to the indoor evaporator 114 side but flows to the outdoor evaporator 116 side. The air blown into the room passes through the indoor condenser 112 and becomes hot air, and the hot air is led into the room.

システム駆動開始から時間が経過し、室内エバポレータ１１４の出口側冷媒温度が所定圧力以上となると、蒸発圧力調整弁１１７が開放し、冷媒が室内エバポレータ１１４と室外エバポレータ１１６の双方に流れる。室内に導かれる送風は、室内エバポレータ１１４と室内コンデンサ１１２を通過し、所望温度の温風とされて室内に導かれる。室内に導かれる送風は、室内エバポレータ１１４を通過する際に凝縮水を発生するため、室内を除湿暖房することができる。
特許公報第２７４５９９７号特開平７−２６６８６０号公報 When time elapses from the start of system operation and the outlet-side refrigerant temperature of the indoor evaporator 114 becomes equal to or higher than a predetermined pressure, the evaporation pressure adjusting valve 117 is opened, and the refrigerant flows to both the indoor evaporator 114 and the outdoor evaporator 116. The air blown into the room passes through the indoor evaporator 114 and the indoor condenser 112, becomes hot air at a desired temperature, and is led into the room. The air blown into the room generates condensed water when it passes through the room evaporator 114, so that the room can be dehumidified and heated.
Patent Publication No. 2745997 JP-A-7-266860

しかしながら、前者の従来例では、図１２に示すように、暖房運転における冷媒の熱の授受を見ると、冷媒の熱は室内コンデンサ１０３でのみ放熱し、室内エバポレータ１０５で吸熱するため、コンプレッサ１０１の動力に相当する熱量だけが暖房熱量となる。従って、除湿暖房できるものの暖房性能が低いという問題がある。 However, in the former conventional example, as shown in FIG. 12, when the heat of the refrigerant in the heating operation is seen, the heat of the refrigerant is radiated only by the indoor condenser 103 and is absorbed by the indoor evaporator 105. Only the amount of heat corresponding to power is the amount of heating heat. Accordingly, there is a problem that although the dehumidifying heating can be performed, the heating performance is low.

後者の従来例では、暖房運転と冷房運転の双方を行うことができず、しかも、暖房運転の初期は、除湿暖房ではないという問題がある。 In the latter conventional example, both the heating operation and the cooling operation cannot be performed, and there is a problem that the initial stage of the heating operation is not dehumidifying heating.

そこで、本発明は、冷房運転と暖房運転ができるシステムにあって、除湿暖房で、しかも、高い暖房性能を発揮する空気調和システムを提供することを目的とする。 Therefore, an object of the present invention is to provide an air-conditioning system that can perform cooling operation and heating operation, and that exhibits high heating performance with dehumidification heating.

上記目的を達成する請求項１の発明は、冷媒を圧縮して冷媒を高温高圧の冷媒とするコンプレッサと、高温高圧の冷媒と外気との間で熱交換させる室外コンデンサと、高温高圧の冷媒と室内に導く送風との間で熱交換させる室内コンデンサと、高圧の冷媒を減圧して低圧の冷媒とする減圧手段と、減圧手段で低圧とされた冷媒と室内に導く送風との間で熱交換させる室内エバポレータと、室内エバポレータと並列に接続され、且つ、減圧手段で低圧とされた冷媒とコンプレッサとの間で熱交換させる室外エバポレータと、コンプレッサからの高温高圧の冷媒が室外コンデンサに導かれた後に減圧手段を通って室内エバポレータに導かれる冷房用循環経路と、コンプレッサからの高温高圧の冷媒が室内コンデンサに導かれた後に減圧手段を通って室内エバポレータ及び室外エバポレータに導かれる除湿暖房用循環経路に切り替えできる第１切替手段とを備えたことを特徴とする。 The invention according to claim 1 that achieves the above object includes a compressor that compresses the refrigerant to make the refrigerant a high-temperature and high-pressure refrigerant, an outdoor condenser that exchanges heat between the high-temperature and high-pressure refrigerant and the outside air, and a high-temperature and high-pressure refrigerant. Heat exchange between the indoor condenser for exchanging heat with the air blown into the room, the pressure reducing means for depressurizing the high-pressure refrigerant into a low-pressure refrigerant, and the air blowing into the room with the refrigerant reduced in pressure by the pressure reducing means The indoor evaporator to be connected, the outdoor evaporator connected in parallel with the indoor evaporator and having a low pressure by the decompression means, and the heat exchange between the compressor and the high-temperature and high-pressure refrigerant from the compressor were led to the outdoor condenser A cooling circulation path that is later guided to the indoor evaporator through the decompression means, and a high-temperature and high-pressure refrigerant from the compressor is guided to the indoor condenser and then passed through the decompression means. Characterized by comprising a first switching means capable of switching to the dehumidification air-heating circulation path is guided to the indoor evaporator and the outdoor evaporator.

請求項２の発明は、請求項１記載の空気調和システムであって、コンプレッサからの高温高圧の冷媒を室外コンデンサに導く熱交換経路と、室外コンデンサを迂回するバイパス通路に導くバイパス経路とに切り替えできる第２切替手段を有することを特徴とする。 A second aspect of the present invention is the air conditioning system according to the first aspect, wherein the system is switched between a heat exchange path that guides the high-temperature and high-pressure refrigerant from the compressor to the outdoor condenser and a bypass path that leads to a bypass passage that bypasses the outdoor condenser. It has the 2nd switching means which can be characterized.

請求項３の発明は、請求項１又は請求項２記載の空気調和システムであって、減圧手段は、室内エバポレータ側の分岐路に設けられた第１減圧手段と、室外エバポレータ側の分岐路に設けられた第２減圧手段とを有することを特徴とする。 Invention of Claim 3 is an air conditioning system of Claim 1 or Claim 2, Comprising: A decompression means is the 1st decompression means provided in the branch path by the side of an indoor evaporator, and the branch path by the side of an outdoor evaporator. And a second decompression means provided.

請求項４の発明は、請求項３記載の空気調和システムであって、第１切替手段は、コンプレッサからの高温高圧の冷媒が室内コンデンサに導かれた後に減圧手段を通って室外エバポレータに導かれ、室内エバポレータに導かない非除湿暖房用循環経路に切り替えできることを特徴とする。 The invention according to claim 4 is the air conditioning system according to claim 3, wherein the first switching means is led to the outdoor evaporator through the pressure reducing means after the high-temperature and high-pressure refrigerant from the compressor is led to the indoor condenser. It is possible to switch to a circulation path for non-dehumidifying heating that is not led to the indoor evaporator.

請求項５の発明は、請求項１〜請求項４のいずれかに記載の空気調和システムであって、室外エバポレータは、コンプレッサに一体化されたことを特徴とする。 A fifth aspect of the present invention is the air conditioning system according to any one of the first to fourth aspects, wherein the outdoor evaporator is integrated with a compressor.

請求項６の発明は、請求項１〜請求項５のいずれかに記載の空気調和システムであって、室外エバポレータは、コンプレッサの外周を冷媒が通るよう構成されたことを特徴とする。 A sixth aspect of the present invention is the air conditioning system according to any one of the first to fifth aspects, wherein the outdoor evaporator is configured such that the refrigerant passes through the outer periphery of the compressor.

請求項７の発明は、請求項１〜請求項５のいずれかに記載の空気調和システムであって、室外エバポレータは、コンプレッサの内部を冷媒が通るよう構成されたことを特徴とする。 A seventh aspect of the present invention is the air conditioning system according to any one of the first to fifth aspects, wherein the outdoor evaporator is configured such that the refrigerant passes through the compressor.

請求項１の発明によれば、冷房運転では第１切替手段によって冷房用循環経路を選択する。すると、コンプレッサからの高温高圧の冷媒は、室外コンデンサに導かれて放熱し、減圧手段で減圧された後に室内エバポレータに導かれて吸熱する。これによって、室内に導かれる送風は、室内エバポレータを通過し、冷風とされて室内に導かれる。 According to the invention of claim 1, in the cooling operation, the cooling circulation path is selected by the first switching means. Then, the high-temperature and high-pressure refrigerant from the compressor is guided to the outdoor condenser to dissipate heat, and after being decompressed by the decompression means, is guided to the indoor evaporator to absorb heat. As a result, the air blown into the room passes through the indoor evaporator, is cooled, and is led into the room.

又、除湿暖房運転では第１切替手段によって除湿暖房用循環経路を選択する。すると、コンプレッサからの高温高圧の冷媒は、室内コンデンサに導かれて放熱し、減圧手段で減圧された後に室内エバポレータと室外エバポレータの双方に導かれて吸熱する。これによって、室内に導かれる送風は、室内エバポレータと室内コンデンサを通過し、温風とされて室内に導かれる。室内に導かれる送風は、室内エバポレータを通過する際に凝縮水を発生するため、室内を除湿暖房することができる。そして、除湿暖房運転では、冷媒は室内エバポレータのみならず室外エバポレータでも吸熱するため、コンプレッサの動力に相当する熱量と室外エバポレータの吸熱量に相当する熱量が暖房用熱量として利用可能である。しかも、室外エバポレータは外気に比べて十分に高温となるコンプレッサから吸熱するため、外気より吸熱させる場合に比べて吸熱性能が高い。以上より、冷房運転と暖房運転ができるシステムにあって、除湿暖房で、しかも、高い暖房性能を発揮することができる。 In the dehumidifying and heating operation, the dehumidifying and heating circulation path is selected by the first switching means. Then, the high-temperature and high-pressure refrigerant from the compressor is guided to the indoor condenser to dissipate heat, and after being decompressed by the decompression means, is guided to both the indoor evaporator and the outdoor evaporator to absorb heat. As a result, the air blown into the room passes through the indoor evaporator and the indoor condenser, becomes warm air, and is led into the room. The air blown into the room generates condensed water when passing through the indoor evaporator, so that the room can be dehumidified and heated. In the dehumidifying heating operation, since the refrigerant absorbs heat not only in the indoor evaporator but also in the outdoor evaporator, the heat amount corresponding to the power of the compressor and the heat amount corresponding to the heat absorption amount of the outdoor evaporator can be used as the heating heat amount. In addition, since the outdoor evaporator absorbs heat from the compressor that is sufficiently hotter than the outside air, the endothermic performance is higher than that when absorbing heat from the outside air. As mentioned above, in the system which can perform air_conditionaing | cooling operation and heating operation, it can demonstrate high heating performance by dehumidification heating.

請求項２の発明によれば、請求項１の発明の効果に加え、暖房運転では第２切替手段によってバイパス経路を選択する。すると、コンプレッサからの高温高圧の冷媒は、室外コンデンサには導かれずに室内コンデンサにのみ導かれ、室内コンデンサの放熱量がアップする。この室内コンデンサによる放熱量のアップ分だけ暖房性能が向上する。 According to the invention of claim 2, in addition to the effect of the invention of claim 1, the bypass path is selected by the second switching means in the heating operation. Then, the high-temperature and high-pressure refrigerant from the compressor is not led to the outdoor condenser but is led only to the indoor condenser, and the heat dissipation amount of the indoor condenser is increased. Heating performance is improved by an increase in the amount of heat released by the indoor condenser.

請求項３の発明によれば、請求項１又は請求項２の発明の効果に加え、第１減圧手段は、車室内温度に応じて室内エバポレータの出口側の冷媒蒸発温度を調整し、第２減圧手段は、冷却用冷媒の温度に応じて室外エバポレータの出口側の冷媒蒸発温度を調整できるため、室内温度と冷却用冷媒の温度が異なる場合でも一定の冷媒過熱度を維持する制御が可能である。 According to the invention of claim 3, in addition to the effect of the invention of claim 1 or 2, the first pressure reducing means adjusts the refrigerant evaporation temperature on the outlet side of the indoor evaporator according to the vehicle compartment temperature, Since the decompression means can adjust the refrigerant evaporation temperature on the outlet side of the outdoor evaporator according to the temperature of the cooling refrigerant, it can be controlled to maintain a constant degree of refrigerant superheat even when the indoor temperature and the temperature of the cooling refrigerant are different. is there.

請求項４の発明によれば、請求項３の発明の効果に加え、非除湿暖房運転では、室内に導かれる送風は、室内エバポレータで冷却されずに室内コンデンサで加熱されるため、暖房性能が大幅に向上する。 According to the invention of claim 4, in addition to the effect of the invention of claim 3, in the non-dehumidifying heating operation, the air blown into the room is heated by the indoor condenser without being cooled by the indoor evaporator. Greatly improved.

請求項５の発明によれば、請求項１〜請求項４の発明の効果に加え、システムの構成部品の増加、これに伴うコストアップを極力抑えることができると共に、車載性にも影響を与えない。 According to the invention of claim 5, in addition to the effects of the inventions of claims 1 to 4, an increase in the number of system components and the accompanying cost increase can be suppressed as much as possible, and the on-vehicle performance is also affected. Absent.

請求項５の発明によれば、請求項１〜請求項４の発明の効果に加え、室外エバポレータのコンプレッサへの組み付けが容易である。 According to the invention of claim 5, in addition to the effects of the inventions of claims 1 to 4, it is easy to assemble the outdoor evaporator to the compressor.

請求項６の発明によれば、請求項１〜請求項４の発明の効果に加え、冷媒がコンプレッサ内部の熱を効率良く吸熱できるため、室外エバポレータの吸熱性能が向上する。 According to the invention of claim 6, in addition to the effects of the inventions of claims 1 to 4, since the refrigerant can efficiently absorb the heat inside the compressor, the endothermic performance of the outdoor evaporator is improved.

以下、本発明の実施の形態を図面に基づいて説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.

（実施形態）
図１〜図７は本発明の空気調和システムを車両用空気調和システムに適用した一実施形態を示し、図１は車両用空気調和システムの概略構成図、図２は室外エバポレータを電動コンプレッサの外周に装着した状態を示す斜視図、図３は車両用空気調和システムの要部回路ブロック図、図４は冷房運転時の冷媒の流れを示す図、図５は除湿暖房運転時の冷媒の流れを示す図、図６は非除湿暖房運転時の冷媒の流れを示す図、図７はＰ−ｈ線上に本実施形態に係る冷凍サイクルの状態を示した図である。 (Embodiment)
1 to 7 show an embodiment in which the air conditioning system of the present invention is applied to an air conditioning system for a vehicle, FIG. 1 is a schematic configuration diagram of the air conditioning system for a vehicle, and FIG. 2 shows an outdoor evaporator as an outer periphery of an electric compressor. FIG. 3 is a main part circuit block diagram of the vehicle air conditioning system, FIG. 4 is a diagram showing a refrigerant flow during cooling operation, and FIG. 5 is a refrigerant flow during dehumidifying heating operation. FIG. 6 is a diagram showing a refrigerant flow during non-dehumidifying heating operation, and FIG. 7 is a diagram showing a state of the refrigeration cycle according to the present embodiment on the Ph line.

図１に示すように、車両用空気調和システムＡは、コンプレッサである電動コンプレッサ１と、室外コンデンサ２と、室内コンデンサ３と、室内エバポレータ４と、室外エバポレータ５と、減圧手段である第１膨張弁６及び第２膨張弁７と、第２切替手段である２つの三方弁８ａ，８ｂと、冷媒圧力調整手段９及び合流器１０とを備えている。 As shown in FIG. 1, the vehicle air conditioning system A includes an electric compressor 1 that is a compressor, an outdoor condenser 2, an indoor condenser 3, an indoor evaporator 4, an outdoor evaporator 5, and a first expansion that is a decompression unit. A valve 6 and a second expansion valve 7, two three-way valves 8a and 8b as second switching means, a refrigerant pressure adjusting means 9 and a merger 10 are provided.

電動コンプレッサ１は、冷媒を圧縮する圧縮機構部とこの圧縮機構部を駆動する電動モータと電動モータを駆動制御するモータ制御部とを内蔵する。そして、吸引した冷媒を圧縮機構部で圧縮し、高温高圧の冷媒として吐出する。冷媒は、二酸化炭素等の超臨界冷媒が使用されている。 The electric compressor 1 includes a compression mechanism unit that compresses the refrigerant, an electric motor that drives the compression mechanism unit, and a motor control unit that drives and controls the electric motor. The sucked refrigerant is compressed by the compression mechanism and discharged as a high-temperature and high-pressure refrigerant. As the refrigerant, a supercritical refrigerant such as carbon dioxide is used.

２つの三方弁８ａ，８ｂは、電動コンプレッサ１及び室外コンデンサ２の間と、室外コンデンサ２及び室内コンデンサ３間にそれぞれ配置されている。そして、２つの三方弁８ａ，８ｂは、電動コンプレッサ１からの高温高圧の冷媒を室外コンデンサ２に導く熱交換経路と、室外コンデンサ２をバイパスするバイパス通路１１に導くバイパス経路とを選択する。２つの三方弁８ａ，８ｂは、制御部１５によって制御される。 The two three-way valves 8a and 8b are disposed between the electric compressor 1 and the outdoor capacitor 2, and between the outdoor capacitor 2 and the indoor capacitor 3, respectively. The two three-way valves 8a and 8b select a heat exchange path that guides the high-temperature and high-pressure refrigerant from the electric compressor 1 to the outdoor condenser 2 and a bypass path that leads to the bypass passage 11 that bypasses the outdoor condenser 2. The two three-way valves 8a and 8b are controlled by the control unit 15.

室外コンデンサ２は、エンジンルーム内に配置され、高温高圧の冷媒と外気との間で熱交換させる。 The outdoor capacitor | condenser 2 is arrange | positioned in an engine room, and heat-exchanges between a high temperature / high pressure refrigerant | coolant and external air.

室内コンデンサ３は、送風を車室内に導く空調ダクト１２内に配置され、高温高圧の冷媒と送風との間で熱交換させる。室内コンデンサ３の下流通路は２つに分岐され、分岐された２つの通路はコンプレッサ１の手前で合流されている。一方の分岐通路に第１膨張弁６及び室内エバポレータ４が、他方の分岐通路に第２膨張弁７及び室外エバポレータ５が設けられている。 The indoor condenser 3 is disposed in the air conditioning duct 12 that guides the ventilation to the vehicle interior, and exchanges heat between the high-temperature and high-pressure refrigerant and the ventilation. The downstream passage of the indoor condenser 3 is branched into two, and the two branched passages are joined before the compressor 1. The first expansion valve 6 and the indoor evaporator 4 are provided in one branch passage, and the second expansion valve 7 and the outdoor evaporator 5 are provided in the other branch passage.

減圧手段は、第１減圧手段である第１膨張弁６と第２減圧手段である第２膨張弁７とから構成されている。第１膨張弁６は、上記したように、室内コンデンサ３の下流の一方の分岐路に配置されている。第１膨張弁６は、室内コンデンサ３より排出された高圧の冷媒を減圧する。 The decompression means comprises a first expansion valve 6 that is a first decompression means and a second expansion valve 7 that is a second decompression means. As described above, the first expansion valve 6 is disposed in one branch path downstream of the indoor condenser 3. The first expansion valve 6 decompresses the high-pressure refrigerant discharged from the indoor condenser 3.

第２膨張弁７は、上記したように、室内コンデンサ３の下流の他方の分岐路に配置されている。第２膨張弁７は、室内コンデンサ３より排出された高温の冷媒を減圧する。 As described above, the second expansion valve 7 is disposed in the other branch path downstream of the indoor condenser 3. The second expansion valve 7 decompresses the high-temperature refrigerant discharged from the indoor condenser 3.

又、第１膨張弁６及び第２膨張弁７は、第１切替手段を兼用している。つまり、第２膨張弁７の全閉位置では、室内コンデンサ３を通過した冷媒が他方の分岐通路に導かれない。又、第１膨張弁６の全閉位置では、室内コンデンサ３を通過した冷媒が一方の分岐通路に導かれない。つまり、第１膨張弁６と第２膨張弁７によって、室内コンデンサ３で冷却された冷媒を、室内エバポレータ４にのみ導く図４の冷房用循環経路と、室内エバポレータ４と室外エバポレータ５の双方に導く図５の除湿暖房用循環経路と、室外エバポレータ５にのみ導く図６の非除湿暖房用循環経路に切り替えできる。第１膨張弁６及び第２膨張弁７は、制御部１５によって制御される。 The first expansion valve 6 and the second expansion valve 7 also serve as first switching means. That is, at the fully closed position of the second expansion valve 7, the refrigerant that has passed through the indoor condenser 3 is not guided to the other branch passage. Further, in the fully closed position of the first expansion valve 6, the refrigerant that has passed through the indoor condenser 3 is not guided to one branch passage. That is, the refrigerant cooled by the indoor condenser 3 by the first expansion valve 6 and the second expansion valve 7 is guided to the cooling circulation path of FIG. 4 only to the indoor evaporator 4, and to both the indoor evaporator 4 and the outdoor evaporator 5. It is possible to switch between the dehumidifying and heating circulation path shown in FIG. 5 and the non-dehumidifying and heating circulation path shown in FIG. 6 led only to the outdoor evaporator 5. The first expansion valve 6 and the second expansion valve 7 are controlled by the control unit 15.

室内エバポレータ４は、空調ダクト１１内に配置され、第１膨張弁６で減圧された低温低圧の冷媒と送風との間で熱交換させる。空調ダクト１１内には、室内コンデンサ３を通過する送風と室内コンデンサ３をバイパスする送風との配風割合を調整できる配風ドア（図示せず）が設けられている。 The indoor evaporator 4 is disposed in the air conditioning duct 11 and exchanges heat between the low-temperature and low-pressure refrigerant decompressed by the first expansion valve 6 and the air. In the air conditioning duct 11, an air distribution door (not shown) capable of adjusting the air distribution ratio between the air passing through the indoor condenser 3 and the air passing through the indoor condenser 3 is provided.

室外エバポレータ５は、空調ダクト１１の外部で、且つ、電動コンプレッサ１より吸熱可能に配置されている。具体的には、室外エバポレータ５は、図２に詳しく示すように、電動コンプレッサ１の外周にほぼ密着された螺旋状パイプにて構成され、電動コンプレッサ１の外周に一体化されている。これにより、電動コンプレッサ１の外周を冷媒が通るようになっている。そして、室外エバポレータ５は、第２膨張弁７で減圧された低温低圧の冷媒と電動コンプレッサ１との間で熱交換させる。 The outdoor evaporator 5 is disposed outside the air conditioning duct 11 and capable of absorbing heat from the electric compressor 1. Specifically, as shown in detail in FIG. 2, the outdoor evaporator 5 is configured by a spiral pipe that is substantially in close contact with the outer periphery of the electric compressor 1, and is integrated with the outer periphery of the electric compressor 1. As a result, the refrigerant passes through the outer periphery of the electric compressor 1. The outdoor evaporator 5 exchanges heat between the low-temperature and low-pressure refrigerant decompressed by the second expansion valve 7 and the electric compressor 1.

図１に戻り、冷媒圧力調整手段９は、前記した２つの分岐通路にそれぞれ配置された第１圧力調整弁９ａと第２圧力調整弁９ｂとから構成されている。第１圧力調整弁９ａと第２圧力調整弁９ｂは、２つの分岐通路の合流箇所における冷媒圧力を同じにするよう上流側の圧力が高い方が調整される。又、第１圧力調整弁９ａと第２圧力調整弁９ｂは、制御部１５によって弁開度が調整される。 Returning to FIG. 1, the refrigerant pressure adjusting means 9 is composed of a first pressure adjusting valve 9 a and a second pressure adjusting valve 9 b disposed in the two branch passages. The first pressure regulating valve 9a and the second pressure regulating valve 9b are adjusted such that the pressure on the upstream side is higher so that the refrigerant pressure at the junction of the two branch passages is the same. Further, the opening degree of the first pressure regulating valve 9a and the second pressure regulating valve 9b is adjusted by the control unit 15.

制御部１５（図３に示す）は、上記したように第１膨張弁６及び第２膨張弁７の弁開度と三方弁８ａ，８ｂの切替えを制御することによって、図４に示す冷房用循環経路と、図５に示す暖房用循環経路に切り替える。この詳しい経路内容については、下記の動作で説明する。 As described above, the control unit 15 (shown in FIG. 3) controls the opening degree of the first expansion valve 6 and the second expansion valve 7 and the switching of the three-way valves 8a and 8b, so that the cooling unit shown in FIG. Switching to the circulation path and the heating circulation path shown in FIG. This detailed route content will be described in the following operation.

また、車両用空気調和システムＡには、室内エバポレータ４の出口側の冷媒温度を検知する第１冷媒温度センサＳ１と、室外エバポレータ５の出口側の冷媒温度を検知する第２冷媒温度センサＳ２と外気温を検知する外気温センサＳ３と車室内の温度を検知する車室内温度センサＳ４（図３に示す）、車室内の湿度を検知する湿度センサＳ５とが設けられている。制御部１５は、これらセンサＳ１，Ｓ２，Ｓ３，Ｓ４，Ｓ５の検知温度情報とユーザ指令（冷暖房スイッチのオン・オフ、温度設定など）に基づいて電動コンプレッサ１の駆動、第１膨張弁６及び第２膨張弁７の絞り、電磁弁８、三方弁９等を制御する。具体的な制御内容については、車両用空気調和システムＡの動作で説明する。 Further, the vehicle air conditioning system A includes a first refrigerant temperature sensor S1 that detects a refrigerant temperature on the outlet side of the indoor evaporator 4 and a second refrigerant temperature sensor S2 that detects a refrigerant temperature on the outlet side of the outdoor evaporator 5. An outside air temperature sensor S3 for detecting the outside air temperature, a vehicle interior temperature sensor S4 (shown in FIG. 3) for detecting the temperature inside the vehicle interior, and a humidity sensor S5 for detecting the humidity inside the vehicle interior are provided. Based on the detected temperature information of these sensors S1, S2, S3, S4, and S5 and a user command (on / off of an air conditioning switch, temperature setting, etc.), the control unit 15 drives the electric compressor 1, the first expansion valve 6 and The throttle of the second expansion valve 7, the electromagnetic valve 8, the three-way valve 9 and the like are controlled. The specific control contents will be described in the operation of the vehicle air conditioning system A.

また、車両用空気調和システムＡには、室内エバポレータ４を通過した冷媒温度を検知する第１冷媒温度センサＳ１と、室外エバポレータ５を通過した冷媒温度を検知する第２冷媒温度センサＳ２とエンジン冷却水の温度を検知する冷却水温度センサＳ３と車室内の温度を検知する車室内温度センサＳ４（図２に示す）とが設けられている。制御部１５は、これらセンサＳ１，Ｓ２，Ｓ３，Ｓ４の検知温度情報とユーザ指令（冷暖房スイッチのオン・オフ、温度設定など）に基づいてコンプレッサ１の駆動、第１膨張弁６及び第２膨張弁７の絞り、電磁弁８、三方弁９等を制御する。具体的な制御内容については、車両用空気調和システムＡの動作で説明する。 The vehicle air conditioning system A includes a first refrigerant temperature sensor S1 that detects the refrigerant temperature that has passed through the indoor evaporator 4, a second refrigerant temperature sensor S2 that detects the refrigerant temperature that has passed through the outdoor evaporator 5, and engine cooling. A cooling water temperature sensor S3 for detecting the temperature of water and a vehicle interior temperature sensor S4 (shown in FIG. 2) for detecting the temperature in the vehicle interior are provided. The control unit 15 drives the compressor 1, the first expansion valve 6 and the second expansion based on the detected temperature information of these sensors S1, S2, S3 and S4 and a user command (ON / OFF of the air conditioning switch, temperature setting, etc.). The throttle of the valve 7, the electromagnetic valve 8, the three-way valve 9 and the like are controlled. The specific control contents will be described in the operation of the vehicle air conditioning system A.

次に、車両用空気調和システムＡの動作を説明する。冷房運転が選択されると、制御部１５によって３つの三方弁８ａ，８ｂが室外コンデンサ２の通路を選択し、第２膨張弁７が全閉位置とされ、図４に示す冷房用循環経路に切り替えられる。 Next, the operation of the vehicle air conditioning system A will be described. When the cooling operation is selected, the control unit 15 causes the three three-way valves 8a and 8b to select the passage of the outdoor condenser 2, the second expansion valve 7 is set to the fully closed position, and the cooling circulation path shown in FIG. Can be switched.

電動コンプレッサ１からの高温高圧の冷媒は、室外コンデンサ２、室内コンデンサ３を通った後に、室内エバポレータ４のみを通ってコンプレッサ１に戻る。第１膨張弁６は、第１冷媒温度センサＳ１の検知冷媒温度に基づき、室内エバポレータ４の出口の冷媒過熱度を一定に保つよう弁開度が制御される。 The high-temperature and high-pressure refrigerant from the electric compressor 1 passes through the outdoor condenser 2 and the indoor condenser 3 and then returns to the compressor 1 through the indoor evaporator 4 only. The valve opening degree of the first expansion valve 6 is controlled so that the refrigerant superheat degree at the outlet of the indoor evaporator 4 is kept constant based on the refrigerant temperature detected by the first refrigerant temperature sensor S1.

車室内に導かれる送風は、室内エバポレータ４と必要に応じて室内コンデンサ３を通過し（フル冷房では、室内コンデンサ３を通らない）、所望温度の冷風とされて車室内に導かれる。そして、冷房運転における冷媒の熱の授受を見ると、冷媒は室外コンデンサ２と室内コンデンサ３の双方で放熱するため、室内エバポレータ４では吸熱量が室内コンデンサ３より大きく、高い冷房性能を発揮することができる。 The air blown into the vehicle interior passes through the indoor evaporator 4 and the indoor condenser 3 as necessary (in the case of full cooling, it does not pass through the indoor condenser 3), and is cooled to a desired temperature and guided into the vehicle interior. When looking at the heat exchange of the refrigerant in the cooling operation, the refrigerant dissipates heat in both the outdoor condenser 2 and the indoor condenser 3, so that the indoor evaporator 4 has a larger heat absorption than the indoor condenser 3, and exhibits high cooling performance. Can do.

除湿暖房運転が選択されると、制御部１５によって２つの三方弁８ａ，８ｂがバイパス通路１０を選択し、図５に示す除湿暖房用循環経路に切り替えられる。 When the dehumidifying and heating operation is selected, the two three-way valves 8a and 8b select the bypass passage 10 by the control unit 15, and are switched to the dehumidifying and heating circulation path shown in FIG.

コンプレッサ１からの高温高圧の冷媒は、室内コンデンサ３を通った後に分岐され、第１膨張弁６と室内エバポレータ４を通る分岐路と第２膨張弁７及び室外エバポレータ５を通る分岐路を流れ、その後に合流してコンプレッサ１に戻る。第１膨張弁６は、第１冷媒温度センサＳ１の検知冷媒温度に基づき、室内エバポレータ４の出口の冷媒過熱度を一定に保つよう弁開度が制御される。第２膨張弁７は、第２冷媒温度センサＳ２の検知冷媒温度に基づき、室外エバポレータ５の出口の冷媒過熱度を一定に保つよう弁開度が制御される。尚、電動コンプレッサ１の起動直後等にあって、電動コンプレッサ１より潜熱による吸熱ができない場合には、第２膨張弁７を全開位置として顕熱によって吸熱する。 The high-temperature and high-pressure refrigerant from the compressor 1 is branched after passing through the indoor condenser 3, and flows through a branch path that passes through the first expansion valve 6 and the indoor evaporator 4, and a branch path that passes through the second expansion valve 7 and the outdoor evaporator 5, After that, it merges and returns to the compressor 1. The valve opening degree of the first expansion valve 6 is controlled so that the refrigerant superheat degree at the outlet of the indoor evaporator 4 is kept constant based on the refrigerant temperature detected by the first refrigerant temperature sensor S1. The valve opening degree of the second expansion valve 7 is controlled so as to keep the refrigerant superheat degree at the outlet of the outdoor evaporator 5 constant based on the refrigerant temperature detected by the second refrigerant temperature sensor S2. Note that when the electric compressor 1 is immediately after the start-up and the like and the heat absorption by the latent heat cannot be performed by the electric compressor 1, the second expansion valve 7 is set to the fully open position to absorb the heat by sensible heat.

室内に導かれる送風は、室内エバポレータ４と必要に応じて室内コンデンサ３を通過し（フル暖房では、室内コンデンサ３を全て通る）、所望温度の温風とされて車室内に導かれる。車室内に導かれる送風は、室内エバポレータ４を通過する際に凝縮水を発生するため、車室内を除湿暖房することができる。そして、除湿暖房運転では、冷媒は室内エバポレータ４のみならず室外エバポレータ５でも吸熱するため、図７に示すように、電動コンプレッサ１の動力に相当する熱量と室外エバポレータ５の吸熱量に相当する熱量が暖房用熱量となる。しかも、室外エバポレータ５は外気に比べて十分に高温となる電動コンプレッサ１から吸熱するため、外気より吸熱させる場合に比べて吸熱性能が高い。以上より、冷房運転と暖房運転ができるシステムにあって、除湿暖房で、しかも、高い暖房性能を発揮することができる。 The air blown into the room passes through the indoor evaporator 4 and the indoor condenser 3 as necessary (in the case of full heating, all of the indoor condenser 3 passes), and is heated to a desired temperature and led into the vehicle interior. The air blown into the vehicle interior generates condensed water when passing through the interior evaporator 4, so that the vehicle interior can be dehumidified and heated. In the dehumidifying heating operation, the refrigerant absorbs heat not only in the indoor evaporator 4 but also in the outdoor evaporator 5, so that the heat amount corresponding to the power of the electric compressor 1 and the heat amount corresponding to the heat absorption amount of the outdoor evaporator 5 are shown in FIG. 7. Is the amount of heat for heating. In addition, since the outdoor evaporator 5 absorbs heat from the electric compressor 1 having a sufficiently high temperature compared to the outside air, the endothermic performance is higher than the case where the outdoor evaporator 5 absorbs heat from the outside air. As mentioned above, in the system which can perform air_conditionaing | cooling operation and heating operation, it can demonstrate high heating performance by dehumidification heating.

又、除湿暖房であるため、「リサーク」でも窓ガラスの曇りを防止できるとともに、「フレッシュ」に対して吸気温度が高いため、その分だけ吹き出し温度も高くできる。 In addition, since it is dehumidifying heating, fogging of the window glass can be prevented even in “Resirk”, and since the intake air temperature is higher than “fresh”, the blowing temperature can be increased accordingly.

内外気温度及び室内の湿度から室内の除湿が必要ない場合には非除湿暖房運転が選択される。非除湿暖房運転が選択されると、制御部１５によって２つの三方弁８ａ，８ｂがバイパス通路１０を選択し、第１膨張弁６が全閉位置に位置され、図６に示す非除湿暖房用循環経路に切り替えられる。 The non-dehumidifying heating operation is selected when indoor dehumidification is not required based on the inside / outside air temperature and the indoor humidity. When the non-dehumidifying heating operation is selected, the control unit 15 causes the two three-way valves 8a and 8b to select the bypass passage 10 and the first expansion valve 6 is located at the fully closed position, and the non-dehumidifying heating operation shown in FIG. Switch to the circulation path.

コンプレッサ１からの高温高圧の冷媒は、室内コンデンサ３を通った後に、第２膨張弁７及び室外エバポレータ５を通る分岐路のみを流れてコンプレッサ１に戻る。第２膨張弁７は、第２冷媒温度センサＳ２の検知冷媒温度に基づき、室外エバポレータ５の出口の冷媒過熱度を一定に保つよう弁開度が制御される。 The high-temperature and high-pressure refrigerant from the compressor 1 passes through the indoor condenser 3 and then flows only through the branch passage passing through the second expansion valve 7 and the outdoor evaporator 5 and returns to the compressor 1. The valve opening degree of the second expansion valve 7 is controlled so as to keep the refrigerant superheat degree at the outlet of the outdoor evaporator 5 constant based on the refrigerant temperature detected by the second refrigerant temperature sensor S2.

室内に導かれる送風は、室内コンデンサ３を通過し、温風とされて車室内に導かれる。車室内に導かれる送風は、室内エバポレータ４で吸熱されないため、除湿されることはないが冷却もされないことから除湿暖房運転に比べて高温の温風が得られる。 The air blown into the room passes through the indoor condenser 3 and is heated into the passenger compartment. Since the air blown into the passenger compartment is not absorbed by the indoor evaporator 4, it is not dehumidified but is not cooled, so that hot air having a temperature higher than that in the dehumidifying heating operation is obtained.

除湿暖房運転及び非除湿暖房運転では、室外エバポレータ５によって電動コンプレッサ１の熱が吸熱されるため、電動コンプレッサ１（特に、モータ制御部）が冷却され、長寿命化に寄与する。 In the dehumidifying heating operation and the non-dehumidifying heating operation, since the heat of the electric compressor 1 is absorbed by the outdoor evaporator 5, the electric compressor 1 (particularly, the motor control unit) is cooled, which contributes to a longer life.

この第１実施形態では、冷房運転では、コンプレッサ２からの高温高圧の冷媒が室外コンデンサ２を流れた後に室内コンデンサ３を流れるよう構成されているが、室外コンデンサ２を流れた後に、室内コンデンサ３を流れることなく第１膨張弁６を経て室内エバポレータ４に導かれるよう構成しても良い。 In the first embodiment, in the cooling operation, the high-temperature and high-pressure refrigerant from the compressor 2 is configured to flow through the indoor capacitor 3 after flowing through the outdoor capacitor 2, but after flowing through the outdoor capacitor 2, the indoor capacitor 3 It may be configured to be guided to the indoor evaporator 4 through the first expansion valve 6 without flowing through the first expansion valve 6.

この第１実施形態では、コンプレッサ１からの高温高圧の冷媒を室外コンデンサ２に流す熱交換経路と、バイパス通路１０に流すバイパス経路に切り替えできる三方弁９を有するので、前記したように非常に高い暖房性能を発揮することができる。 In the first embodiment, since the three-way valve 9 that can be switched between the heat exchange path for flowing the high-temperature and high-pressure refrigerant from the compressor 1 to the outdoor condenser 2 and the bypass path for flowing to the bypass path 10 is very high as described above. Heating performance can be demonstrated.

この第１実施形態では、減圧手段は、室内エバポレータ４への分岐通路に設けられた第１膨張弁６と、室外エバポレータ５への分岐通路に設けられた第２膨張弁７とから構成されている。つまり、室内エバポレータ４と室外エバポレータ５が専用の減圧手段を有するので、第１膨張弁６は、車室内温度等の吸気送風温度に応じて室内エバポレータ４の出口側の冷媒蒸発温度を調整し、第２膨張弁７は、電動コンプレッサ１の温度に応じて室外エバポレータ５の出口側の冷媒蒸発温度を調整できるため、室内エバポレータ４の出口側と室外エバポレータ５の出口側をそれぞれ一定の冷媒過熱度に調整する制御が可能である。例えば、第２膨張弁７によって室内エバポレータ４の冷媒蒸発温度より室外エバポレータ５の冷媒蒸発温度を低く設定できるため、室外エバポレータ５は電動コンプレッサ１の温度が非常に低い時でも電動コンプレッサ１からの吸熱を行うことができ、優れた暖房性能を発揮することができる。特に、この実施形態では、冷媒として超臨界冷媒を使用している。従って、外気温度が超低温（例えばマイナス２０℃程度）であり、エンジン２１の始動時に電動コンプレッサ１の低く、室外エバポレータ５の冷媒蒸発温度を外気温度より低温に設定しても電動コンプレッサ１の入口側（低圧側）の冷媒圧力が大気圧以下にならないため、外気が超低温でも不具合なく室外エバポレータ５を有効作動できる。 In this first embodiment, the decompression means is composed of a first expansion valve 6 provided in the branch passage to the indoor evaporator 4 and a second expansion valve 7 provided in the branch passage to the outdoor evaporator 5. Yes. That is, since the indoor evaporator 4 and the outdoor evaporator 5 have dedicated decompression means, the first expansion valve 6 adjusts the refrigerant evaporation temperature on the outlet side of the indoor evaporator 4 according to the intake air blowing temperature such as the vehicle interior temperature, Since the second expansion valve 7 can adjust the refrigerant evaporation temperature on the outlet side of the outdoor evaporator 5 according to the temperature of the electric compressor 1, a constant degree of refrigerant superheating is provided on the outlet side of the indoor evaporator 4 and the outlet side of the outdoor evaporator 5. It is possible to control to adjust to. For example, since the refrigerant expansion temperature of the outdoor evaporator 5 can be set lower than the refrigerant evaporation temperature of the indoor evaporator 4 by the second expansion valve 7, the outdoor evaporator 5 absorbs heat from the electric compressor 1 even when the temperature of the electric compressor 1 is very low. And can exhibit excellent heating performance. In particular, in this embodiment, a supercritical refrigerant is used as the refrigerant. Accordingly, the outside air temperature is extremely low (for example, about minus 20 ° C.), the electric compressor 1 is low when the engine 21 is started, and the refrigerant evaporation temperature of the outdoor evaporator 5 is set lower than the outside air temperature. Since the refrigerant pressure on the (low pressure side) does not become lower than the atmospheric pressure, the outdoor evaporator 5 can be effectively operated without any trouble even when the outside air is at a very low temperature.

この実施形態では、室内エバポレータ４側の分岐路と室外エバポレータ５側の分岐路の下流合流点における冷媒圧力を同一圧力に調整する冷媒圧力調整手段９ａ，９ｂが設けられている。つまり、冷媒の除湿暖房用循環経路にあって、室内エバポレータ４側の分岐路を通った冷媒と室外熱交換器５側の分岐路を通った冷媒がそれぞれ他の分岐路に逆流することを防止できる。これによって、室内エバポレータ４内を通過する冷媒圧力と室外エバポレータ５を通過する冷媒圧力をそれぞれ所望の圧力に維持できる。 In this embodiment, refrigerant pressure adjusting means 9a and 9b for adjusting the refrigerant pressure at the downstream junction of the branch path on the indoor evaporator 4 side and the branch path on the outdoor evaporator 5 side to the same pressure are provided. That is, in the refrigerant dehumidification heating circulation path, the refrigerant that has passed through the branch path on the indoor evaporator 4 side and the refrigerant that has passed through the branch path on the outdoor heat exchanger 5 side are prevented from flowing back to the other branch paths. it can. Thus, the refrigerant pressure passing through the indoor evaporator 4 and the refrigerant pressure passing through the outdoor evaporator 5 can be maintained at desired pressures, respectively.

又、冷媒圧力調整手段は、室内エバポレータ４と下流合流点との間に介在された第１圧力調整弁９ａと、室外エバポレータ５と下流合流点との間に介在された第２圧力調整弁９ｂとから構成されている。従って、室内温度と電動コンプレッサ１の温度の高低に関わらず双方の冷媒圧力を同じに調整できる。 The refrigerant pressure adjusting means includes a first pressure adjusting valve 9a interposed between the indoor evaporator 4 and the downstream junction, and a second pressure adjusting valve 9b interposed between the outdoor evaporator 5 and the downstream junction. It consists of and. Therefore, the refrigerant pressure of both can be adjusted to be the same regardless of the temperature of the room temperature and the temperature of the electric compressor 1.

この実施形態では、室外エバポレータ５が電動コンプレッサ１に一体化されているので、システムの構成部品の増加、これに伴うコストアップを極力抑えることができると共に、車載性にも影響を与えない。 In this embodiment, since the outdoor evaporator 5 is integrated with the electric compressor 1, an increase in the number of system components and the associated cost increase can be suppressed as much as possible, and the on-vehicle performance is not affected.

この実施形態では、室外エバポレータ５は、電動コンプレッサ１の外周を冷媒が通るよう構成されている。従って、室外エバポレータ５は電動コンプレッサ１の外周に配置すれば良いため、組み付けが容易である。 In this embodiment, the outdoor evaporator 5 is configured such that the refrigerant passes through the outer periphery of the electric compressor 1. Therefore, since the outdoor evaporator 5 should just be arrange | positioned on the outer periphery of the electric compressor 1, an assembly | attachment is easy.

（室外エバポレータの変形例）
図８は第１変形例の室外エバポレータを内蔵した電動コンプレッサの斜視図である。図８に示すように、電動コンプレッサ１は、ハウジング１ａによって被われおり、このハウジング１ａ内に本来の圧縮用とは異なる冷媒通路を設けることによって室外エバポレータ５Ａが一体に構成されている。室外エバポレータ５Ａは、ハウジング１ａの外側にサブ吸入ポート１ｂとサブ吐出ポート１ｃを有する。 (Modification of outdoor evaporator)
FIG. 8 is a perspective view of an electric compressor incorporating the outdoor evaporator of the first modification. As shown in FIG. 8, the electric compressor 1 is covered with a housing 1a, and an outdoor evaporator 5A is integrally formed by providing a refrigerant passage different from that for original compression in the housing 1a. The outdoor evaporator 5A has a sub suction port 1b and a sub discharge port 1c outside the housing 1a.

この第１変形例の室外エバポレータ５Ａが電動コンプレッサ１に一体化されているので、システムの構成部品の増加、これに伴うコストアップを極力抑えることができると共に、車載性にも影響を与えない。 Since the outdoor evaporator 5A of the first modification is integrated with the electric compressor 1, an increase in the number of system components and the associated cost increase can be suppressed as much as possible, and the on-vehicle performance is not affected.

この第１変形例の室外エバポレータ５Ａは、電動コンプレッサ１の内部を冷媒が通るよう構成されているので、冷媒が電動コンプレッサ１の内部の熱を効率良く吸熱できるため、室外エバポレータ５Ａの吸熱性能が向上する。 The outdoor evaporator 5A of the first modified example is configured so that the refrigerant passes through the electric compressor 1, so that the refrigerant can efficiently absorb the heat inside the electric compressor 1, and therefore the outdoor evaporator 5A has an endothermic performance. improves.

図９及び図１０は室外エバポレータの第２変形例を示し、図９は室外エバポレータを内蔵した電動コンプレッサ１の断面図、図１０は図９のＤ−Ｄ線断面図である。 9 and 10 show a second modification of the outdoor evaporator, FIG. 9 is a cross-sectional view of the electric compressor 1 incorporating the outdoor evaporator, and FIG. 10 is a cross-sectional view taken along the line DD of FIG.

図９及び図１０に示すように、電動コンプレッサ１は、ハウジング３０を有し、ハウジング３０に、冷媒を圧縮する圧縮機構部３１と、この圧縮機構部３１を駆動する電動モータ３２と、電動モータ３２を駆動制御するモータ制御部３３とを内蔵する。電動コンプレッサ１には、冷媒が吸入ポート３４から吸入通路３５を通って圧縮機構部３１に吸引され、圧縮機構部３１に圧縮された冷媒が吐出通路３６を通り吐出ポート３７から外部に排出される。ハウジング３０は、モータ制御部３３に密着する位置に２枚の密着された補助ハウジング４０，４１を有する。この補助ハウジング４０，４１は、吸入通路３５とは別の冷媒通路４２を設けることによって室外エバポレータ５Ｂが一体に構成されている。冷媒通路４２の一端は、補助ハウジング４０，４１のサブ吸入ポート４３に開口し、冷媒通路４２の他端は、電動コンプレッサ１の本来の冷媒吸入通路３４に開口されている。 As shown in FIGS. 9 and 10, the electric compressor 1 includes a housing 30, a compression mechanism portion 31 that compresses the refrigerant in the housing 30, an electric motor 32 that drives the compression mechanism portion 31, and an electric motor. A motor control unit 33 that drives and controls the motor 32 is incorporated. In the electric compressor 1, the refrigerant is sucked from the suction port 34 through the suction passage 35 to the compression mechanism 31, and the refrigerant compressed by the compression mechanism 31 is discharged from the discharge port 37 to the outside through the discharge passage 36. . The housing 30 has two auxiliary housings 40 and 41 in close contact with each other at a position in close contact with the motor control unit 33. The auxiliary housings 40 and 41 are configured integrally with the outdoor evaporator 5B by providing a refrigerant passage 42 different from the suction passage 35. One end of the refrigerant passage 42 opens to the sub suction port 43 of the auxiliary housings 40 and 41, and the other end of the refrigerant passage 42 opens to the original refrigerant suction passage 34 of the electric compressor 1.

この第２変形例の室外エバポレータ５Ｂにあっても、第１変形例のものと同様の効果が得られる。その上、この第２変形例の室外エバポレータ５Ｂは、モータ制御部３３の近傍を冷媒が通るため、電動コンプレッサ１内で最大の発熱体であるモータ制御部３３より有効に吸熱でき、吸熱性に優れている。 Even in the outdoor evaporator 5B of the second modification, the same effect as that of the first modification can be obtained. In addition, since the refrigerant passes through the vicinity of the motor control unit 33, the outdoor evaporator 5B of the second modification can absorb heat more effectively than the motor control unit 33, which is the largest heating element in the electric compressor 1, and is endothermic. Are better.

室外エバポレータとしては、熱交換効率が上げるための種々の手段が考えられる。例えば、管内ビードや冷媒の多パス流れ等を適用する手段である。 As the outdoor evaporator, various means for increasing the heat exchange efficiency can be considered. For example, it is a means to apply a multi-pass flow of pipe bead or refrigerant.

（その他）
減圧手段は、室内エバポレータ４側の分岐路と室外エバポレータ５側の分岐路の分岐箇所より上流に設けられた単一の減圧手段としても良い。２つのエバポレータ（室内エバポレータ４と室外エバポレータ５）に対して１つの第１膨張弁６で低圧の冷媒を導くため、部品点数の削減化、コストの低減化、システム構成のシンプル化になる。 (Other)
The pressure reducing means may be a single pressure reducing means provided upstream from the branching point of the branch path on the indoor evaporator 4 side and the branch path on the outdoor evaporator 5 side. Since the low-pressure refrigerant is guided to the two evaporators (the indoor evaporator 4 and the outdoor evaporator 5) by one first expansion valve 6, the number of parts, the cost, and the system configuration are simplified.

第１膨張弁６を温度感知式（圧力感知式）とすると共に、室内エバポレータ４の出口に感温筒を設け、第１膨張弁６が感温筒からの検知温度（検知圧力）に基づき、室内エバポレータ４の出口側の冷媒過熱度を一定に保つよう弁開度を自動調整するよう構成しても良い。第２膨張弁７側も同様である。 The first expansion valve 6 is a temperature sensing type (pressure sensing type), a temperature sensing cylinder is provided at the outlet of the indoor evaporator 4, and the first expansion valve 6 is based on the detected temperature (sensing pressure) from the temperature sensing cylinder, You may comprise so that a valve opening degree may be adjusted automatically so that the refrigerant | coolant superheat degree of the exit side of the indoor evaporator 4 may be kept constant. The same applies to the second expansion valve 7 side.

本発明の一実施形態を示し、車両用空気調和システムの概略構成図である。1 shows an embodiment of the present invention and is a schematic configuration diagram of a vehicle air conditioning system. FIG. 本発明の一実施形態を示し、室外エバポレータを電動コンプレッサの外周に装着した状態を示す斜視図である。It is a perspective view which shows one Embodiment of this invention and shows the state which attached the outdoor evaporator to the outer periphery of an electric compressor. 本発明の一実施形態を示し、車両用空気調和システムの要部回路ブロック図である。1 shows an embodiment of the present invention, and is a principal circuit block diagram of an air conditioning system for a vehicle. FIG. 本発明の一実施形態を示し、冷房運転時の冷媒の流れを示す図である。It is a figure which shows one Embodiment of this invention and shows the flow of the refrigerant | coolant at the time of air_conditionaing | cooling operation. 本発明の一実施形態を示し、除湿暖房運転時の冷媒の流れを示す図である。It is a figure which shows one Embodiment of this invention and shows the flow of the refrigerant | coolant at the time of dehumidification heating operation. 本発明の一実施形態を示し、非除湿暖房運転時の冷媒の流れを示す図である。It is a figure which shows one Embodiment of this invention and shows the flow of the refrigerant | coolant at the time of non-dehumidification heating operation. 本発明の一実施形態を示し、Ｐ−ｈ線上に本実施形態に係る冷凍サイクルの状態を示した図である。FIG. 5 is a diagram showing an embodiment of the present invention and showing the state of the refrigeration cycle according to the present embodiment on the Ph line. 第１変形例の室外エバポレータを内蔵した電動コンプレッサの斜視図である。It is a perspective view of the electric compressor which incorporated the outdoor evaporator of the 1st modification. 第２変形例の室外エバポレータを内蔵した電動コンプレッサ１の断面図である。It is sectional drawing of the electric compressor 1 incorporating the outdoor evaporator of the 2nd modification. 図９のＤ−Ｄ線断面図である。FIG. 10 is a sectional view taken along line D-D in FIG. 9. 従来例の空気調和システムの概略構成図である。It is a schematic block diagram of the air conditioning system of a prior art example. Ｐ−ｈ線上に従来例に係る冷凍サイクルの状態を示した図である。It is the figure which showed the state of the refrigerating cycle which concerns on a prior art example on Ph line. 他の従来例の空気調和システムの概略構成図である。It is a schematic block diagram of the air conditioning system of another prior art example.

Explanation of symbols

Ａ車両用空気調和システム（空気調和システム）
１電動コンプレッサ（コンプレッサ）
２室外コンデンサ
３室内コンデンサ
４室内エバポレータ
５，５Ａ，５Ｂ室外エバポレータ
６第１膨張弁（減圧手段、第１切替手段）
７第２膨張弁（減圧手段、第１切替手段）
８ａ，８ｂ三方弁（第２切替手段）
１０バイパス通路 A Vehicle air conditioning system (air conditioning system)
1 Electric compressor (compressor)
2 Outdoor condenser 3 Indoor condenser 4 Indoor evaporator 5, 5A, 5B Outdoor evaporator 6 First expansion valve (pressure reduction means, first switching means)
7 Second expansion valve (pressure reduction means, first switching means)
8a, 8b Three-way valve (second switching means)
10 Bypass passage

Claims

A compressor (1) that compresses the refrigerant and converts the refrigerant into a high-temperature and high-pressure refrigerant;
An outdoor condenser (2) for exchanging heat between the high-temperature and high-pressure refrigerant and the outside air;
An indoor condenser (3) for exchanging heat between the high-temperature and high-pressure refrigerant and the air blown into the room;
Decompression means (6), (7) that decompresses the high-pressure refrigerant into a low-pressure refrigerant;
An indoor evaporator (4) for exchanging heat between the refrigerant whose pressure has been reduced by the decompression means (6) and the air blown into the room;
An outdoor evaporator (5) that is connected in parallel with the indoor evaporator (4) and that exchanges heat between the refrigerant and the compressor (1), the pressure of which is reduced by the pressure reducing means (7).
A high-temperature and high-pressure refrigerant from the compressor (1) is led to the outdoor condenser (2) and then led to the indoor evaporator (4) through the decompression means (6), and the compressor ( Dehumidification in which the high-temperature and high-pressure refrigerant from 1) is guided to the indoor condenser (3) and then to the indoor evaporator (4) and the outdoor evaporator (5) through the decompression means (6) and (7). An air conditioning system (A) comprising a first switching means (8) capable of switching to a heating circulation path.

The air conditioning system (A) according to claim 1,
A second switching that can be switched between a heat exchange path that guides the high-temperature and high-pressure refrigerant from the compressor (1) to the outdoor condenser (2) and a bypass path that leads to a bypass path (10) that bypasses the outdoor condenser (2). An air conditioning system (A) characterized by comprising means (9).

The air conditioning system (A) according to claim 1 or 2,
The pressure reducing means includes a first pressure reducing means (6) provided in the branch path on the indoor evaporator (4) side, and a second pressure reducing means (7) provided on the branch path on the outdoor evaporator (5) side. The air conditioning system (A) characterized by having.

The air conditioning system (A) according to claim 3,
The first switching means (8) guides the high-temperature and high-pressure refrigerant from the compressor (1) to the outdoor evaporator (5) through the decompression means (7) after being guided to the indoor condenser (3). The air conditioning system (A) can be switched to a circulation path for non-dehumidifying heating that is not led to the indoor evaporator (4).

It is an air conditioning system (A) in any one of Claims 1-4,
The outdoor evaporator (5), (5A), (5B) is integrated with the compressor (1), and is an air conditioning system (A).

It is an air conditioning system (A) in any one of Claims 1-5,
The outdoor evaporator (5A) is configured to allow refrigerant to pass through the outer periphery of the compressor (1).

It is an air conditioning system (A) in any one of Claims 1-5,
The outdoor evaporator (5B) is configured to allow refrigerant to pass through the compressor (1), and is an air conditioning system (A).