JP2003139436A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JP2003139436A JP2003139436A JP2001334310A JP2001334310A JP2003139436A JP 2003139436 A JP2003139436 A JP 2003139436A JP 2001334310 A JP2001334310 A JP 2001334310A JP 2001334310 A JP2001334310 A JP 2001334310A JP 2003139436 A JP2003139436 A JP 2003139436A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- indoor heat
- air conditioner
- air
- indoor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Landscapes
- Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和機に関す
るものであり、特に再熱除湿運転をする空気調和機に関
するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner, and more particularly to an air conditioner that performs a reheat dehumidifying operation.
【０００２】[0002]
【従来の技術】図１０は従来の空気調和機の冷凍サイク
ルを示す冷媒回路図であり、図において、１は低温低圧
のガス冷媒を吸入して圧縮し高温高圧のガス冷媒を吐出
する圧縮機、２は四方弁、３ａは第１室内熱交換器、３
ｂは第２室内熱交換器、３０は第１室内熱交換器３ａと
第２室内熱交換器３ｂの間に配設された二方弁、３１は
二方弁３０のバイパス回路３２に配設された除湿用絞り
装置、５は主絞り装置、６は室外熱交換器、７は室外送
風機である。2. Description of the Related Art FIG. 10 is a refrigerant circuit diagram showing a refrigerating cycle of a conventional air conditioner. In the figure, reference numeral 1 is a compressor for sucking in and compressing a low-temperature low-pressure gas refrigerant and discharging a high-temperature high-pressure gas refrigerant. 2 is a four-way valve, 3a is a first indoor heat exchanger, 3
b is a second indoor heat exchanger, 30 is a two-way valve arranged between the first indoor heat exchanger 3a and the second indoor heat exchanger 3b, and 31 is a bypass circuit 32 of the two-way valve 30. The dehumidifying expansion device 5 is a main expansion device, 6 is an outdoor heat exchanger, and 7 is an outdoor blower.
【０００３】前記のように構成された従来の空調調和機
において、例えば再熱除湿運転の場合について動作を説
明する。圧縮機1より高温高圧のガス冷媒が吐出し、四
方弁２を通った後、室外熱交換器６へ流入する。ここ
で、室外送風機７はインバータ基板（図示せず）などの
電気基板冷却のため低回転数で運転され送風するため、
室外熱交換器６に流入したガス冷媒は、乾き度が比較的
高い二相冷媒に凝縮され室外熱交換器６を流出する。室
外熱交換器６を流出した高乾き度の高温二相冷媒は主絞
り装置５で若干減圧された後、第１室内熱交換器３ａに
流入する。ここで、高温二相冷媒は、第１室内熱交換器
３ａを通る室内空気と熱交換され、低乾き度の二相冷媒
または液冷媒に凝縮され第１室内熱交換器３ａを流出す
る。なお第１室内熱交換器３ａを通った室内空気は高温
となる。The operation of the conventional air conditioning conditioner configured as described above will be described, for example, in the case of reheat dehumidifying operation. The high-temperature and high-pressure gas refrigerant is discharged from the compressor 1, passes through the four-way valve 2, and then flows into the outdoor heat exchanger 6. Here, since the outdoor blower 7 is operated at a low rotational speed to blow air to cool an electric board such as an inverter board (not shown),
The gas refrigerant flowing into the outdoor heat exchanger 6 is condensed into a two-phase refrigerant having a relatively high degree of dryness and flows out of the outdoor heat exchanger 6. The high-dryness high-temperature two-phase refrigerant flowing out of the outdoor heat exchanger 6 is slightly decompressed by the main expansion device 5, and then flows into the first indoor heat exchanger 3a. Here, the high-temperature two-phase refrigerant is heat-exchanged with the indoor air passing through the first indoor heat exchanger 3a, condensed into a low-dryness two-phase refrigerant or liquid refrigerant, and flows out of the first indoor heat exchanger 3a. The room air that has passed through the first indoor heat exchanger 3a becomes hot.
【０００４】第１室内熱交換器３ａを流出した低乾き度
二相冷媒または液冷媒は、二方弁３０を閉止しているた
め、除湿用絞り装置３１側へ流れ、ここで低圧低温の二
相冷媒となって第２室内熱交換器３ｂに流入する。ここ
で第２室内熱交換器３ｂを通った室内空気と熱交換さ
れ、高乾き度の二相冷媒またはガス冷媒まで蒸発する。
なお、第２室内熱交換器３ｂを通った室内空気は冷却さ
れて低温となり、さらに露点温度以下の熱交換器表面に
て室内空気中の水蒸気が凝縮し、第２室内熱交換器を通
ったあとの室内空気は低温かつ低湿度の状態となる。第
２室内熱交換器３ｂを流出した冷媒は四方弁２を通って
圧縮機１に吸入される。また、第１室内熱交換器３ａを
通った高温空気と第２室内熱交換器３ｂを通った低温低
湿度の空気は、それぞれの室内熱交換器を出た後混合さ
れ、吸込み空気よりも温度がわずかに低く、湿度は低下
した状態となり再熱除湿運転が実現される。The low-dryness two-phase refrigerant or liquid refrigerant flowing out of the first indoor heat exchanger 3a flows to the dehumidifying expansion device 31 side because the two-way valve 30 is closed, and here, the low-pressure low-temperature two-way refrigerant is used. It becomes a phase refrigerant and flows into the second indoor heat exchanger 3b. Here, heat is exchanged with the room air that has passed through the second indoor heat exchanger 3b, and the two-phase refrigerant or gas refrigerant having a high degree of dryness is evaporated.
The room air that has passed through the second indoor heat exchanger 3b is cooled to a low temperature, and the water vapor in the room air is condensed on the surface of the heat exchanger below the dew point temperature and passed through the second indoor heat exchanger. The remaining indoor air is in a low temperature and low humidity state. The refrigerant flowing out of the second indoor heat exchanger 3b passes through the four-way valve 2 and is sucked into the compressor 1. Further, the high-temperature air that has passed through the first indoor heat exchanger 3a and the low-temperature low-humidity air that has passed through the second indoor heat exchanger 3b are mixed after exiting the respective indoor heat exchangers and have a higher temperature than the intake air. Is slightly low and the humidity is low, and reheat dehumidification operation is realized.
【０００５】また、他の運転として冷房運転について説
明する。圧縮機1より高温高圧のガス冷媒が吐出し、四
方弁２を通った後室外熱交換器６へ流入する。ここで、
室外送風機７は高回転で運転され、室外熱交換器６に流
入したガス冷媒は、乾き度が低乾き度の二相冷媒または
液冷媒に凝縮され室外熱交換器６を流出する。室外熱交
換器６を流出した冷媒は主絞り装置５で低圧に減圧され
た低圧低温の二相冷媒となる。第１室内熱交換器３ａと
第２室内熱交換器３ｂをつなぐ二方弁３０は開状態とな
っており、第１室内熱交換器３ａおよび第２室内熱交換
器３ｂはどちらも蒸発器として動作し、第１室内熱交換
器３ａおよび第２室内熱交換器３ｂに流入した低温低圧
の二相冷媒と第１室内熱交換器３ａおよび第２室内熱交
換器３ｂを通る室内空気は熱交換し、冷媒は第１室内熱
交換器３ａにて中間の乾き度の二相冷媒まで蒸発し、第
２室内熱交換器３ｂにて高乾き度の二相冷媒またはガス
冷媒となり、第２室内熱交換器３ｂを流出し、四方弁２
を通って圧縮機１に吸入される。一方第１室内熱交換器
３ａおよび第２室内熱交換器３ｂを通る室内空気は吸込
み空気よりも低温となり、冷房運転が実現する。A cooling operation will be described as another operation. High-temperature and high-pressure gas refrigerant is discharged from the compressor 1, passes through the four-way valve 2 and then flows into the outdoor heat exchanger 6. here,
The outdoor blower 7 is operated at a high rotation speed, and the gas refrigerant flowing into the outdoor heat exchanger 6 is condensed into a two-phase refrigerant or a liquid refrigerant having a low dryness and flows out of the outdoor heat exchanger 6. The refrigerant flowing out of the outdoor heat exchanger 6 becomes a low-pressure low-temperature two-phase refrigerant whose pressure is reduced to a low pressure by the main expansion device 5. The two-way valve 30 connecting the first indoor heat exchanger 3a and the second indoor heat exchanger 3b is in an open state, and both the first indoor heat exchanger 3a and the second indoor heat exchanger 3b are evaporators. The low-temperature low-pressure two-phase refrigerant that has operated and has flowed into the first indoor heat exchanger 3a and the second indoor heat exchanger 3b and the indoor air that has passed through the first indoor heat exchanger 3a and the second indoor heat exchanger 3b exchange heat. Then, the refrigerant evaporates up to the intermediate dryness two-phase refrigerant in the first indoor heat exchanger 3a, and becomes the high dryness two-phase refrigerant or gas refrigerant in the second indoor heat exchanger 3b. Flow out from the exchanger 3b, and the four-way valve 2
And is sucked into the compressor 1 through. On the other hand, the indoor air passing through the first indoor heat exchanger 3a and the second indoor heat exchanger 3b becomes lower in temperature than the intake air, and the cooling operation is realized.
【０００６】[0006]
【発明が解決しようとする課題】前記のような従来の空
気調和機の再熱除湿運転においては、電気基板の冷却な
どの目的のために室外送風機７を運転せざるえなく、室
外熱交換器６にて冷媒から外気へのかなりの放熱が発生
する。室外熱交換器６にて放熱があると、冷媒は凝縮さ
れ比エンタルピーが小さくなるため、そのあとの再熱熱
交換器となる第１室内熱交換器３ａでの放熱量が小さく
なり室内空気の加熱が不足してしまう。結果的に第２室
内熱交換器３ｂを通り冷却された空気を十分加熱するこ
とができず、必然的に吹出し空気温度は吸込み空気温度
よりも温度が低下してしまい、特に室内空気温度がそれ
ほど高くない中間期や室内温度の低い冬期などにおいて
は、快適性の面で問題があった。In the reheat dehumidification operation of the conventional air conditioner as described above, the outdoor blower 7 must be operated for the purpose of cooling the electric board, and the outdoor heat exchanger must be operated. At 6, considerable heat dissipation from the refrigerant to the outside air occurs. When heat is dissipated in the outdoor heat exchanger 6, the refrigerant is condensed and the specific enthalpy becomes smaller, so the amount of heat dissipated in the first indoor heat exchanger 3a, which is the reheat heat exchanger after that, becomes smaller and Insufficient heating. As a result, the cooled air that has passed through the second indoor heat exchanger 3b cannot be sufficiently heated, and the temperature of the blown air inevitably becomes lower than the temperature of the sucked air. There was a problem in terms of comfort in the middle of the year when it was not high and in the winter when the room temperature was low.
【０００７】また、通常の冷房運転を行う際、第１室内
熱交換器３ａにて蒸発した中間の乾き度の二相冷媒が二
方弁３０を通って第２室内熱交換器３ｂへ流れるため、
二方弁３０において冷媒の圧力損失が発生し冷凍サイク
ルの運転効率が低下するとともに、第１室内熱交換器３
ａと第２室内熱交換器３ｂで蒸発温度が異なり、出口空
気温度に温度差が生じるなどの問題もあった。Further, during normal cooling operation, the two-phase refrigerant of intermediate dryness evaporated in the first indoor heat exchanger 3a flows through the two-way valve 30 to the second indoor heat exchanger 3b. ,
Refrigerant pressure loss occurs in the two-way valve 30 to reduce the operation efficiency of the refrigeration cycle, and the first indoor heat exchanger 3
There is also a problem that the evaporating temperature differs between a and the second indoor heat exchanger 3b, and a temperature difference occurs in the outlet air temperature.
【０００８】本発明は、かかる課題を解決するためにな
されたもので、再熱除湿運転において、吹出し空気温度
が吸込み空気温度よりも高くできる空気調和機を得るこ
とを目的とする。また、再熱除湿運転において、吹出し
空気の除湿量と温度とを自由に調整可能な空気調和機を
得ることを目的とする。また、再熱除湿運転において、
熱ロスが小さく、効率の良い空気調和機を得ることを目
的とする。また、再熱除湿運転において、吹出し空気の
温度、湿度が一様である空気調和機を得ることを目的と
する。さらに、再熱除湿運転が可能であるとともに、吹
出し空気の状態を自由に調整可能な空気調和機を得るこ
とを目的とする。さらに、再熱除湿運転とともに通常の
冷房運転が可能であり、通常の冷房運転においても効率
の低下がない空気調和機を得ることを目的とする。さら
に、信頼性の高い空気調和機を得ることを目的とする。
さらに、地球環境に悪影響を与えない空気調和機を得る
ことを目的とする。The present invention has been made to solve the above problems, and an object of the present invention is to obtain an air conditioner capable of making the temperature of blown air higher than the temperature of intake air in the reheat dehumidification operation. Another object of the present invention is to obtain an air conditioner capable of freely adjusting the dehumidifying amount and temperature of blown air in the reheat dehumidifying operation. In the reheat dehumidification operation,
The objective is to obtain an efficient air conditioner with low heat loss. Another object is to obtain an air conditioner in which the temperature and humidity of blown air are uniform in the reheat dehumidification operation. Further, it is an object of the present invention to obtain an air conditioner capable of performing reheat dehumidification operation and freely adjusting the state of blown air. Further, it is an object of the present invention to obtain an air conditioner that can perform a normal cooling operation as well as a reheat dehumidifying operation, and that does not have a decrease in efficiency even in the normal cooling operation. Furthermore, it aims at obtaining a highly reliable air conditioner.
Furthermore, it aims at obtaining an air conditioner that does not adversely affect the global environment.
【０００９】[0009]
【課題を解決するための手段】本発明の請求項１に係る
空気調和機は、圧縮機、室外熱交換器、絞り装置及び室
内熱交換器を備えた空気調和機であって、室内熱交換器
は、第１室内熱交換器及び第２室内熱交換器から一体構
成され、第１室内熱交換器は、第１圧縮機、第１室外熱
交換器及び第１絞り装置とともに第１冷凍サイクルを構
成し、第２室内熱交換器は、第２圧縮機、第２室外熱交
換器及び第２絞り装置とともに第２冷凍サイクルを構成
し、第１冷凍サイクルで暖房運転を行い、同時に第２冷
凍サイクルで冷房運転を行うものである。An air conditioner according to claim 1 of the present invention is an air conditioner equipped with a compressor, an outdoor heat exchanger, a throttling device and an indoor heat exchanger. The reactor is integrally configured of a first indoor heat exchanger and a second indoor heat exchanger, and the first indoor heat exchanger is a first refrigeration cycle together with a first compressor, a first outdoor heat exchanger and a first expansion device. The second indoor heat exchanger constitutes a second refrigeration cycle together with the second compressor, the second outdoor heat exchanger, and the second expansion device, and performs the heating operation in the first refrigeration cycle, and simultaneously performs the second refrigeration cycle. The cooling operation is performed in the refrigeration cycle.
【００１０】また、本発明の請求項２に係る空気調和機
は、請求項１記載の空気調和機において、第１室内熱交
換器を再熱用熱交換器とし、第２室内熱交換器を除湿用
熱交換器とするものである。An air conditioner according to claim 2 of the present invention is the air conditioner according to claim 1, wherein the first indoor heat exchanger is a reheat heat exchanger and the second indoor heat exchanger is The heat exchanger is for dehumidification.
【００１１】また、本発明の請求項３に係る空気調和機
は、請求項１または請求項２記載の空気調和機におい
て、第１圧縮機及び第２圧縮機は、容量制御装置を備え
たものである。An air conditioner according to a third aspect of the present invention is the air conditioner according to the first or second aspect, wherein the first compressor and the second compressor have a capacity control device. Is.
【００１２】また、本発明の請求項４に係る空気調和機
は、請求項３の空気調和機において、除湿量は第２圧縮
機の容量制御装置で調節し、空気温度は第１圧縮機の容
量制御装置で調整するものである。According to a fourth aspect of the present invention, in the air conditioner of the third aspect, the dehumidifying amount is adjusted by the capacity control device of the second compressor, and the air temperature of the first compressor is adjusted. It is adjusted by the capacity control device.
【００１３】また、本発明の請求項５に係る空気調和機
は、請求項１〜４のいずれかの空気調和機において、室
内熱交換器は、上段側を第１室内熱交換器とし、下段側
を第２室内熱交換器としたものである。An air conditioner according to a fifth aspect of the present invention is the air conditioner according to any one of the first to fourth aspects, wherein the indoor heat exchanger has a first indoor heat exchanger on the upper stage side and a lower stage. The side is the second indoor heat exchanger.
【００１４】また、本発明の請求項６に係る空気調和機
は、請求項５の空気調和機において、第１室内熱交換器
の冷媒の流れ方向は、風向に対して対向流とし、第２室
内熱交換器の冷媒の流れ方向は、風向に対して並行流と
したものである。The air conditioner according to a sixth aspect of the present invention is the air conditioner according to the fifth aspect, wherein the flow direction of the refrigerant in the first indoor heat exchanger is a counterflow with respect to the wind direction. The flow direction of the refrigerant in the indoor heat exchanger is parallel to the wind direction.
【００１５】また、本発明の請求項７に係る空気調和機
は、請求項１〜４のいずれかにの空気調和機において、
室内熱交換器を風上側に第２室内熱交換器、風下側に第
１熱交換器の配置としたものである。An air conditioner according to claim 7 of the present invention is the air conditioner according to any one of claims 1 to 4, wherein:
The indoor heat exchanger has a second indoor heat exchanger on the windward side and a first heat exchanger on the leeward side.
【００１６】また、本発明の請求項８に係る空気調和機
は、請求項１〜７の空気調和機において、箱体の中に室
内熱交換器、送風機を収納して室内ユニットを構成し、
室内熱交換器で熱交換した空気を室内ユニットに接続さ
れたダクトから室内へ送風するダクト式室内ユニットを
備えたものである。An air conditioner according to claim 8 of the present invention is the air conditioner according to any one of claims 1 to 7, wherein an indoor heat exchanger and a blower are housed in a box to form an indoor unit,
This is provided with a duct type indoor unit that blows the air, which has been heat-exchanged by the indoor heat exchanger, into the room from the duct connected to the indoor unit.
【００１７】また、本発明の請求項９に係る空気調和機
は、請求項１〜８のいずれかの空気調和機において、第
１冷凍サイクル及び第２冷凍サイクル共に冷房運転する
か、またはどちらか一方で冷房運転し、他方は運転停止
とするものである。According to a ninth aspect of the present invention, in the air conditioner according to any of the first to eighth aspects, either the first refrigerating cycle or the second refrigerating cycle is cooled or operated. The cooling operation is performed on the one hand and the operation is stopped on the other.
【００１８】本発明の請求項１０に係る空気調和機は、
請求項１〜９のいずれかの空気調和機において、圧縮機
の冷凍機油として、冷媒に弱溶解性の冷凍機油を用いた
ものである。An air conditioner according to claim 10 of the present invention comprises:
The air conditioner according to any one of claims 1 to 9, wherein a refrigerating machine oil having a weak solubility is used as a refrigerating machine oil of the compressor.
【００１９】また、本発明の請求項１１に係る空気調和
機は、請求項１〜１０のいずれかの空気調和機におい
て、冷凍サイクルに使用する冷媒として、ＨＦＣ冷媒ま
たはＨＣ冷媒を用いたものである。An air conditioner according to an eleventh aspect of the present invention is the air conditioner according to any one of the first to tenth aspects, wherein an HFC refrigerant or an HC refrigerant is used as the refrigerant used in the refrigeration cycle. is there.
【００２０】[0020]
【発明の実施の形態】実施の形態１．図１は、本発明の
実施の形態1に係る空気調和機の冷凍サイクルを示す冷
媒回路図である。なお、図1の冷凍サイクルは再熱除湿
運転時の状態を示しており、図１０で説明した従来と同
一又は相当部分には同じ符号を付し説明を省略する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiment 1. FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle of an air conditioner according to Embodiment 1 of the present invention. The refrigerating cycle in FIG. 1 shows a state during the reheat dehumidifying operation, and the same or corresponding parts as those of the conventional one described in FIG.
【００２１】図において、１ａは第１圧縮機、１ｂは第
２圧縮機、２ａは第１四方弁、２ｂは第２四方弁、５ａ
は第１絞り装置、５ｂは第２絞り装置、６ａは第１室外
熱交換器、６ｂは第２室外熱交換器、１０ａは第１冷凍
サイクル、１０ｂは第２冷凍サイクルである。なお、再
熱除湿運転時は第１四方弁２ａは暖房モード、第２四方
弁２ｂは冷房モードとなっている。In the figure, 1a is a first compressor, 1b is a second compressor, 2a is a first four-way valve, 2b is a second four-way valve, 5a.
Is a first expansion device, 5b is a second expansion device, 6a is a first outdoor heat exchanger, 6b is a second outdoor heat exchanger, 10a is a first refrigeration cycle, and 10b is a second refrigeration cycle. During the reheat dehumidifying operation, the first four-way valve 2a is in the heating mode and the second four-way valve 2b is in the cooling mode.
【００２２】次に、このように構成された冷凍サイクル
において、再熱除湿運転時の動作を図1を参照しながら
説明する。まず、第１冷凍サイクル１０ａは暖房モード
で運転されており、第１圧縮機１ａより高温高圧のガス
冷媒が吐出し、第１四方弁２ａを通ったのち、第１室内
熱交換器３ａに流入する。第１室内熱交換器３ａに流入
した高温高圧ガス冷媒は、第１室内熱交換器３ａを通る
室内空気と熱交換され、低乾き度の二相冷媒または液冷
媒に凝縮され第１室内熱交換器３ａを流出する。なお第
１室内熱交換器３ａを通った室内空気は高温となる。第
１室内熱交換器３ａを流出した低乾き度二相冷媒または
液冷媒は、第１絞り装置５ａで低圧低温の二相冷媒とな
って第１室外熱交換器６ａに流入する。ここで第１室外
熱交換器６ａを通った外気と熱交換され、高乾き度の二
相冷媒またはガス冷媒まで蒸発され、第１四方弁２ａを
通って第１圧縮機１ａに吸入される。Next, in the refrigerating cycle thus constructed, the operation during the reheat dehumidifying operation will be described with reference to FIG. First, the first refrigeration cycle 10a is operated in the heating mode, high-temperature and high-pressure gas refrigerant is discharged from the first compressor 1a, passes through the first four-way valve 2a, and then flows into the first indoor heat exchanger 3a. To do. The high-temperature high-pressure gas refrigerant that has flowed into the first indoor heat exchanger 3a is heat-exchanged with the indoor air passing through the first indoor heat exchanger 3a, is condensed into a low-dryness two-phase refrigerant or liquid refrigerant, and is the first indoor heat exchanger. Flow out of the vessel 3a. The room air that has passed through the first indoor heat exchanger 3a becomes hot. The low-dryness two-phase refrigerant or the liquid refrigerant flowing out of the first indoor heat exchanger 3a becomes a low-pressure low-temperature two-phase refrigerant in the first expansion device 5a and flows into the first outdoor heat exchanger 6a. Here, heat is exchanged with the outside air that has passed through the first outdoor heat exchanger 6a, the high-dryness two-phase refrigerant or the gas refrigerant is evaporated, and the second compressor 2a is sucked into the first compressor 1a through the first four-way valve 2a.
【００２３】次に、第２冷凍サイクル１０ｂは冷房モー
ドで運転されており、第２圧縮機２ｂより高温高圧のガ
ス冷媒が吐出し、第２四方弁２ｂを通ったのち、第２室
外熱交換器６ｂに流入する。第２室外熱交換器６ｂに流
入した高温高圧ガス冷媒は、第２室外熱交換器６ｂを通
る外気と熱交換され、低乾き度の二相冷媒または液冷媒
に凝縮され、第２室外熱交換器６ｂを流出する。第２室
外熱交換器６ｂを流出した低乾き度二相冷媒または液冷
媒は、第２絞り装置５ｂで低圧低温の二相冷媒となって
第２室内熱交換器３ｂに流入する。ここで第２室内熱交
換器３ｂを通った室内空気と熱交換され、高乾き度の二
相冷媒またはガス冷媒まで蒸発され、第２四方弁２ｂを
通って第２圧縮機２ｂに吸入される。なお、第２室内熱
交換器３ｂを通った室内空気は冷却されて低温となり、
さらに露点温度以下の熱交換器表面にて室内空気中の水
蒸気が凝縮し、第２室内熱交換器を通ったあとの室内空
気は低温かつ低湿度の状態となる。第１室内熱交換器３
ａで加熱された室内空気と第２室内熱交換器３ｂで冷却
除湿された室内空気は出口で混合され室内ユニットより
吹出される。Next, the second refrigeration cycle 10b is operated in the cooling mode, the high-temperature and high-pressure gas refrigerant is discharged from the second compressor 2b, passes through the second four-way valve 2b, and then the second outdoor heat exchange. Flows into the vessel 6b. The high-temperature high-pressure gas refrigerant that has flowed into the second outdoor heat exchanger 6b is heat-exchanged with the outside air that passes through the second outdoor heat exchanger 6b, is condensed into a low-dryness two-phase refrigerant or a liquid refrigerant, and is the second outdoor heat exchanger. Outflow from the vessel 6b. The low-dryness two-phase refrigerant or the liquid refrigerant flowing out of the second outdoor heat exchanger 6b becomes a low-pressure low-temperature two-phase refrigerant in the second expansion device 5b and flows into the second indoor heat exchanger 3b. Here, heat is exchanged with the room air that has passed through the second indoor heat exchanger 3b, the high-dryness two-phase refrigerant or gas refrigerant is evaporated, and the second compressor 4b is sucked into the second compressor 2b through the second four-way valve 2b. . The room air that has passed through the second indoor heat exchanger 3b is cooled to a low temperature,
Further, water vapor in the room air is condensed on the surface of the heat exchanger having a dew point temperature or lower, and the room air after passing through the second indoor heat exchanger is in a low temperature and low humidity state. First indoor heat exchanger 3
The indoor air heated in a and the indoor air cooled and dehumidified in the second indoor heat exchanger 3b are mixed at the outlet and blown out from the indoor unit.
【００２４】ここで、図２に示すように第１圧縮機１ａ
および第２圧縮機１ｂは、それぞれインバータ駆動装置
６０ａ、６０ｂにて駆動される容量可変型である場合の
運転制御について図３のフローチャートを用いて説明す
る。除湿用熱交換器となる第２室内熱交換器３ｂの蒸発
温度は、第２圧縮機の運転周波数を調整することによ
り、広範囲に設定することが可能となり、それに伴なっ
て除湿量も広い範囲で調整することが可能となる。した
がって再熱除湿運転開始時、要求される除湿量に対して
目標蒸発温度Teoを設定し、現在の蒸発温度Teが目標蒸
発温度Teoに近づくように第２圧縮機運転周波数を制御
する。即ち、図３に示すように、目標蒸発温度Teoと検
出蒸発温度Teの差（ΔTe）を算出し、Δte＜０の場合
は、第２圧縮機の周波数を大きくし、Δte＞０の場合
は、第２圧縮機の周波数を小さくする。Here, as shown in FIG. 2, the first compressor 1a
The operation control when the second compressor 1b and the second compressor 1b are of the variable capacity type driven by the inverter drive devices 60a and 60b will be described with reference to the flowchart of FIG. The evaporation temperature of the second indoor heat exchanger 3b, which is a heat exchanger for dehumidification, can be set in a wide range by adjusting the operating frequency of the second compressor, and accordingly, the dehumidification amount also has a wide range. Can be adjusted with. Therefore, at the start of the reheat dehumidification operation, the target evaporation temperature Teo is set for the required dehumidification amount, and the second compressor operating frequency is controlled so that the current evaporation temperature Te approaches the target evaporation temperature Teo. That is, as shown in FIG. 3, the difference (ΔTe) between the target evaporation temperature Teo and the detected evaporation temperature Te is calculated, and when Δte <0, the frequency of the second compressor is increased, and when Δte> 0. , Reduce the frequency of the second compressor.
【００２５】一方、再熱用熱交換器となる第１室内熱交
換器３ａの凝縮温度は、第１圧縮機の運転周波数を調整
することにより、広範囲に設定することが可能となり、
それに伴なって再熱量を広い範囲で調整して吹出し空気
温度を変え、結果的に室内空気温度を調節することが可
能となる。したがって再熱除湿運転開始時、要求される
室内空気温度に対して目標凝縮温度Tcoを設定し、現在
の凝縮温度Tcが目標凝縮温度Tcoに近づくように第１圧
縮機運転周波数を制御する。即ち、図３に示すように、
目標凝縮温度Tcoと検出凝縮温度Tcの差（ΔTc）を算出
し、ΔTc＞０の場合は、第１圧縮機の周波数を小さく
し、ΔTc＜０の場合は、第１圧縮機の周波数を大きくす
る。以上のように、第１圧縮機と第２圧縮機の運転周波
数を組合せることにより、除湿量と室内空気温度を広範
囲で調整することが可能となり、さらに従来不可能であ
った吸込み空気温度よりも吹出し空気温度を高くするこ
とも可能となる。On the other hand, the condensing temperature of the first indoor heat exchanger 3a, which is the heat exchanger for reheating, can be set in a wide range by adjusting the operating frequency of the first compressor,
Along with this, it is possible to adjust the amount of reheat in a wide range to change the blown air temperature, and consequently to adjust the indoor air temperature. Therefore, at the start of the reheat dehumidifying operation, the target condensing temperature Tco is set to the required indoor air temperature, and the first compressor operating frequency is controlled so that the current condensing temperature Tc approaches the target condensing temperature Tco. That is, as shown in FIG.
The difference (ΔTc) between the target condensing temperature Tco and the detected condensing temperature Tc is calculated. When ΔTc> 0, the frequency of the first compressor is decreased, and when ΔTc <0, the frequency of the first compressor is increased. To do. As described above, by combining the operating frequencies of the first compressor and the second compressor, it becomes possible to adjust the dehumidification amount and the indoor air temperature over a wide range, and more It is also possible to raise the temperature of the blown air.
【００２６】前記のように実施の形態１によれば、再熱
除湿運転を実施する場合、第１冷凍サイクルと第２冷凍
サイクルが冷凍サイクル上完全に独立しており、第２圧
縮機運転周波数により除湿用熱交換器の蒸発温度を自由
に制御し、第１圧縮機運転周波数により再熱用熱交換器
の凝縮温度を自由に制御できるため、除湿量と吹出し空
気温度を広範囲に、かつ任意に設定することが可能とな
り、使用者の要求にあった空気状態を作り出し、快適感
を与えることができる。また、中間期冬期など室温が低
い時も除湿運転が可能となるため、窓への結露防止など
新しい機能を提供することができる。As described above, according to the first embodiment, when the reheat dehumidification operation is performed, the first refrigeration cycle and the second refrigeration cycle are completely independent on the refrigeration cycle, and the second compressor operation frequency is Since the evaporation temperature of the dehumidification heat exchanger can be controlled freely and the condensing temperature of the reheat heat exchanger can be controlled freely by the first compressor operating frequency, the dehumidification amount and the blown air temperature can be set in a wide range and arbitrarily. It is possible to set the air condition to create an air condition that meets the user's request and give a comfortable feeling. Further, since the dehumidifying operation can be performed even when the room temperature is low such as in the middle winter, it is possible to provide a new function such as prevention of dew condensation on the window.
【００２７】なお、図３で説明した制御フローチャート
は、図４で示す制御フローチャートのように第２圧縮機
運転周波数は除湿用熱交換器の蒸発温度を制御する代わ
りに、除湿運転により結果的に変化する吸込み空気湿度
Haが目標空気湿度Haoとなるように制御しても同様の効
果が得られる。即ち、図４で、目標空気湿度Haoと検出
吸込み空気湿度Haの差（ΔHa）を算出し、Δha＜０の場
合は、第２圧縮機の周波数を大きくし、ΔTc＞０の場合
は、第２圧縮機の周波数を小さくする。また、第１圧縮
機運転周波数は、再熱用熱交換器の凝縮温度を制御する
代わりに再熱運転により結果的に変化する吸込み空気温
度Taが目標空気温度Taoとなるように制御しても同様の
効果が得られる。即ち、図４で、目標空気温度Taoと検
出吸込み空気温度Taの差（ΔTa）を算出し、ΔTa＜０の
場合は、第１圧縮機の周波数を小さくし、ΔTa＞０の場
合は、第１圧縮機の周波数を大きくする。In the control flow chart described in FIG. 3, instead of controlling the evaporation temperature of the heat exchanger for dehumidification by the second compressor operating frequency as in the control flow chart shown in FIG. Changing intake air humidity
The same effect can be obtained by controlling so that Ha becomes the target air humidity Hao. That is, in FIG. 4, the difference (ΔHa) between the target air humidity Hao and the detected intake air humidity Ha is calculated. When Δha <0, the frequency of the second compressor is increased, and when ΔTc> 0, the 2 Reduce the frequency of the compressor. In addition, the first compressor operating frequency may be controlled such that the suction air temperature Ta that changes as a result of the reheat operation becomes the target air temperature Tao instead of controlling the condensing temperature of the reheat heat exchanger. The same effect can be obtained. That is, in FIG. 4, the difference (ΔTa) between the target air temperature Tao and the detected intake air temperature Ta is calculated. When ΔTa <0, the frequency of the first compressor is reduced, and when ΔTa> 0, the 1 Increase the frequency of the compressor.
【００２８】なお、第１、第２圧縮機１ａ、１ｂの容量
を制御する容量制御装置は、インバータ駆動装置６０
ａ、６０ｂの他、公知の圧縮機の容量を制御する容量制
御装置を使ってもよい。The capacity control device for controlling the capacities of the first and second compressors 1a and 1b is the inverter drive device 60.
In addition to a and 60b, a known capacity control device for controlling the capacity of the compressor may be used.
【００２９】また、図１の冷凍サイクルの空気調和機に
おいて、第１、第２圧縮機は容量制御装置を備えていな
くても、図２の冷凍サイクルと同様に、目標温度又は目
標湿度の設定、現状の温度又は湿度の検知、両者の比
較、比較結果により第１、第２圧縮機のＯＮ−ＯＦＦ制
御を組合せることにより、ほぼ同様の効果を得ることが
できる。Further, in the air conditioner of the refrigeration cycle of FIG. 1, even if the first and second compressors are not provided with the capacity control device, the target temperature or the target humidity is set similarly to the refrigeration cycle of FIG. By detecting the current temperature or humidity, comparing the two, and combining ON-OFF control of the first and second compressors according to the comparison result, almost the same effect can be obtained.
【００３０】また、前記の目標凝縮温度の設定、目標蒸
発温度の設定、目標空気温度の設定及び目標空気湿度の
設定、前記の凝縮温度の検知、蒸発温度の検知、吸込み
空気温度の検知及び吸込み空気湿度の検知、前記の設定
目標値と検出値との比較と比較結果による容量制御装置
の制御等は、それぞれ、公知の設定手段、検知手段及び
制御手段で行う。The setting of the target condensing temperature, the setting of the target evaporation temperature, the setting of the target air temperature and the setting of the target air humidity, the detection of the condensing temperature, the detection of the evaporation temperature, the detection of the intake air temperature and the intake The detection of the air humidity, the comparison between the set target value and the detected value, the control of the capacity control device based on the comparison result, and the like are performed by known setting means, detection means, and control means, respectively.
【００３１】また、通常の冷房運転においては、負荷の
大小に応じて、第１冷凍サイクル及び第２冷凍サイクル
を共に冷房運転するか、一方で冷房運転し、他方の運転
は停止する。本実施の形態では、従来の除湿用絞り装置
など通常冷房運転時に効率を悪化させる部品を用いてい
ないため、通常冷房運転時においても本来の冷凍サイク
ルにおける効率にて運転することができる。In the normal cooling operation, either the first refrigerating cycle and the second refrigerating cycle are both cooled or the one is cooled and the other is stopped, depending on the load. In the present embodiment, since a component such as a conventional dehumidifying expansion device that deteriorates the efficiency during normal cooling operation is not used, it is possible to operate at the original efficiency of the refrigeration cycle even during normal cooling operation.
【００３２】実施の形態２．図５は、本発明の実施の形
態２に係る空気調和機に用いられる室内熱交換器の再熱
除湿運転時の構成図であり、実施の形態１の室内熱交換
器３の具体的な構成例を示す。図５において、白抜き矢
印は風の流れ方向、黒矢印は冷媒の流れ方向を示す。室
内熱交換器３は、段方向で２分割されており、上段側の
第１室内熱交換器３ａは再熱用熱交換器、下段側の第２
熱交換器３ｂは除湿用熱交換器として用いられている。
また、再熱用熱交換器である第１室内熱交換器３ａの冷
媒の流れ方向は風向に対して対向流であり、除湿用熱交
換器である第２室内熱交換器３ｂの冷媒の流れ方向は風
向に対して並行流となっている。Embodiment 2. FIG. 5: is a block diagram at the time of reheat dehumidification operation of the indoor heat exchanger used for the air conditioner which concerns on Embodiment 2 of this invention, and the specific structure of the indoor heat exchanger 3 of Embodiment 1. Here is an example: In FIG. 5, a white arrow indicates a wind flow direction, and a black arrow indicates a refrigerant flow direction. The indoor heat exchanger 3 is divided into two in the stage direction, and the first indoor heat exchanger 3a on the upper stage side is the heat exchanger for reheat and the second indoor heat exchanger on the lower stage side.
The heat exchanger 3b is used as a heat exchanger for dehumidification.
In addition, the flow direction of the refrigerant in the first indoor heat exchanger 3a, which is the heat exchanger for reheating, is a counterflow with respect to the wind direction, and the flow of the refrigerant in the second indoor heat exchanger 3b, which is the heat exchanger for dehumidification. The direction is parallel to the wind direction.
【００３３】図６は、再熱用熱交換器内を流れる冷媒の
温度変化と空気の温度変化を示しており、過熱ガスで入
った冷媒は熱交換が進むにつれて温度が低下し、熱交換
器中間ではほぼ温度が一定の二相冷媒となる。さらに出
口側では過冷却液冷媒となり、再び温度が低下する。一
方空気側は冷媒によって加熱され、入口から出口へ向か
って温度が上昇する。FIG. 6 shows a temperature change of the refrigerant flowing in the reheat heat exchanger and a temperature change of the air. The temperature of the refrigerant containing the superheated gas decreases as the heat exchange proceeds, and the heat exchanger changes. In the middle, it becomes a two-phase refrigerant whose temperature is almost constant. Further, it becomes supercooled liquid refrigerant on the outlet side, and the temperature drops again. On the other hand, the air side is heated by the refrigerant, and the temperature rises from the inlet to the outlet.
【００３４】図７は、除湿用熱交換器内を流れる冷媒の
温度変化と空気の温度変化を示す。除湿用熱交換器には
二相冷媒として流入するが、熱交換器内の圧力損失によ
り冷媒温度は入口から出口へ向かって低下する。一方空
気側は冷媒によって冷却され、入口から出口へ向かって
温度が低下する。FIG. 7 shows the temperature change of the refrigerant and the temperature change of the air flowing in the dehumidifying heat exchanger. Although it flows into the dehumidifying heat exchanger as a two-phase refrigerant, the refrigerant temperature decreases from the inlet to the outlet due to the pressure loss in the heat exchanger. On the other hand, the air side is cooled by the refrigerant, and the temperature decreases from the inlet to the outlet.
【００３５】以上のように、室内熱交換器を段方向で分
割し、上段側の第１室内熱交換器３ａを再熱用熱交換
器、下段側の第２熱交換器３ｂを除湿用熱交換器として
いるため、再熱用熱交換器と除湿用熱交換器の接触部の
面積が小さく、再熱用熱交換器と除湿用熱交換器の間の
熱ロスを小さくすることが可能となり、効率の良い再熱
除湿運転をすることができる。さらに、分割部に断熱材
を挿入することにより、熱ロスを抑えることができる。
また、除湿用熱交換器を再熱用熱交換器の下側に位置す
ることにより、除湿用熱交換器の表面に結露した露が再
熱用熱交換器に触れることを防ぎ、結露水の再蒸発を防
止することができる。また、再熱用熱交換器である第１
室内熱交換器３ａの冷媒の流れ方向は風向に対して対向
流、除湿用熱交換器である第２室内熱交換器３ｂの冷媒
の流れ方向は風向に対して並行流としているため、再熱
用熱交換器、除湿用熱交換器ともに入口から出口まで全
領域で冷媒と空気の温度差を確保することが可能となり
効率の良い熱交換を行うことができる。As described above, the indoor heat exchanger is divided in the stage direction, the first indoor heat exchanger 3a on the upper stage side is the heat exchanger for reheat, and the second heat exchanger 3b on the lower stage side is the heat for dehumidification. Since it is an exchanger, the contact area between the reheat heat exchanger and the dehumidifying heat exchanger is small, and it is possible to reduce the heat loss between the reheat heat exchanger and the dehumidifying heat exchanger. The efficient reheat dehumidification operation can be performed. Furthermore, heat loss can be suppressed by inserting a heat insulating material into the divided portions.
Also, by placing the dehumidifying heat exchanger below the reheating heat exchanger, it is possible to prevent dew condensation on the surface of the dehumidifying heat exchanger from touching the reheating heat exchanger. Re-evaporation can be prevented. Also, the first heat exchanger for reheating
Since the flow direction of the refrigerant in the indoor heat exchanger 3a is countercurrent to the wind direction and the flow direction of the refrigerant in the second indoor heat exchanger 3b, which is the heat exchanger for dehumidification, is parallel to the wind direction, reheating is performed. Both the heat exchanger for dehumidification and the heat exchanger for dehumidification can secure a temperature difference between the refrigerant and the air in the entire region from the inlet to the outlet, and can perform efficient heat exchange.
【００３６】実施の形態３．図８は、本発明の実施の形
態３に係る空気調和機に用いられる室内熱交換器の再熱
除湿運転時の構成図であり、白抜き矢印は風の流れ方
向、黒矢印は冷媒の流れ方向を示す。本実施の形態の室
内熱交換器も実施の形態１の室内熱交換器３の具体的な
別の構成例を示す。図８において、室内熱交換器は列方
向で２分割されており、風下側の第１室内熱交換器３ａ
は再熱用熱交換器、風上側の第２室内熱交換器３ｂは除
湿用熱交換器として用いられている。Embodiment 3. FIG. 8: is a block diagram at the time of reheat dehumidification operation of the indoor heat exchanger used for the air conditioner which concerns on Embodiment 3 of this invention, a white arrow shows the flow direction of a wind, and a black arrow shows the flow of a refrigerant | coolant. Indicates the direction. The indoor heat exchanger of the present embodiment also shows another specific configuration example of the indoor heat exchanger 3 of the first embodiment. In FIG. 8, the indoor heat exchanger is divided into two in the row direction, and the first indoor heat exchanger 3a on the leeward side is provided.
Is used as a heat exchanger for reheat, and the second indoor heat exchanger 3b on the windward side is used as a heat exchanger for dehumidification.
【００３７】以上のように、室内熱交換器は列方向で２
分割され、風下側の第１室内熱交換器３ａは再熱用熱交
換器、風上側の第２室内熱交換器３ｂは除湿用熱交換器
となるように用いられるため、除湿用熱交換器３ｂにお
いて空気が通過する前面面積を広く取ることが可能とな
り、効率良く除湿することができる。また、除湿用熱交
換器を通過し、冷却除湿された空気をすべて再熱用熱交
換器へ通すことができるため、室内熱交換器出口空気の
温度を一様とすることができる。As described above, the indoor heat exchanger has two rows in the row direction.
Since the first indoor heat exchanger 3a on the leeward side is used as a reheat heat exchanger and the second indoor heat exchanger 3b on the leeward side is used as a dehumidifying heat exchanger, the dehumidifying heat exchanger is divided. In 3b, the front surface area through which air passes can be widened, and dehumidification can be performed efficiently. Further, since all the air that has passed through the dehumidifying heat exchanger and has been cooled and dehumidified can be passed to the reheat heat exchanger, the temperature of the indoor heat exchanger outlet air can be made uniform.
【００３８】実施の形態４．図９は、本発明の実施の形
態４に係る空気調和機の構成図である。本空気調和機
は、実施の形態１の空気調和機の具体的な構成例を示し
ている。図において、４０ａは第１室外機、４０ｂは第
２室外機、４１ａ、４１ｂは第１室外機４０ａおよび第
２室外機４０ｂと室内ユニット５０内の第１室内熱交換
器３ａおよび第２室内熱交換器３ｂを接続する冷媒配
管、５１は室内ユニット５０内に配設され吸込み口５２
より室内空気を吸込み、室内ユニット吹出し口に接続さ
れたダクト５３より空気を吹出すための送風機である。Fourth Embodiment FIG. 9 is a configuration diagram of an air conditioner according to Embodiment 4 of the present invention. The present air conditioner shows a specific configuration example of the air conditioner of the first embodiment. In the figure, 40a is the first outdoor unit, 40b is the second outdoor unit, 41a and 41b are the first outdoor unit 40a and the second outdoor unit 40b, and the first indoor heat exchanger 3a and the second indoor heat in the indoor unit 50. Refrigerant piping for connecting the exchanger 3b, 51 is provided in the indoor unit 50, and a suction port 52 is provided.
It is a blower for sucking more indoor air and blowing the air from the duct 53 connected to the indoor unit outlet.
【００３９】以上のように、実施の形態４によれば、室
内ユニット５０は内部に第１室内熱交換器３ａおよび第
２室内熱交換器３ｂおよび送風機５１を有し、例えば再
熱除湿運転時は吸込み口５２より吸込んだ室内空気を第
１室内熱交換器３ａにて加熱、第２室内熱交換器３ｂに
て冷却除湿し、第１室内熱交換器３ａおよび第２室内熱
交換器３ｂをそれぞれ通過した空気を送風機５１で吸込
みながら混合し、室内ユニット５０の吹出し口に接続さ
れたダクト５３より室内側へ空気を送るダクト式室内ユ
ニットであるため、第１室内熱交換器３ａにて加熱され
た空気と第２室内熱交換器３ｂにて冷却除湿された空気
を均一に混合した状態で室内側へ送風することが可能と
なり、使用者に対して吹出し空気温度むらによる不快性
を与えることを防止できると共に、吹出し空気温度むら
による露付きなども防止することができる。As described above, according to the fourth embodiment, the indoor unit 50 has the first indoor heat exchanger 3a, the second indoor heat exchanger 3b, and the blower 51 inside, and, for example, during reheat dehumidification operation. Heats the indoor air sucked from the suction port 52 by the first indoor heat exchanger 3a, cools and dehumidifies it by the second indoor heat exchanger 3b, and removes the first indoor heat exchanger 3a and the second indoor heat exchanger 3b. Since it is a duct type indoor unit that mixes the air that has passed through it while sucking it with the blower 51 and sends the air to the indoor side from the duct 53 connected to the outlet of the indoor unit 50, it is heated by the first indoor heat exchanger 3a. It is possible to blow the generated air and the air that has been dehumidified by cooling in the second indoor heat exchanger 3b to the indoor side in a state of being uniformly mixed, and to give the user uncomfortableness due to the uneven temperature of the blown air. Prevent Is possible, it is possible to prevent such dew by blowing air temperature unevenness.
【００４０】実施の形態５.本発明の実施の形態５にお
いては、実施の形態１〜４の空気調和機に使用する冷凍
機油として冷媒に対して弱溶解性の油であるアルキルベ
ンゼン油を用いたものである。また、冷媒として、ＨＦ
Ｃ冷媒またはＨＣ冷媒を用いたものである。Fifth Embodiment In the fifth embodiment of the present invention, an alkylbenzene oil, which is an oil slightly soluble in a refrigerant, is used as a refrigerating machine oil used in the air conditioners of the first to fourth embodiments. It is a thing. In addition, as a refrigerant, HF
It uses a C refrigerant or an HC refrigerant.
【００４１】例えば、冷媒に対して弱溶解性の油である
アルキルベンゼン油は、非常に安定性が高い油として知
られており、水分などの異物が混入しても分解すること
なくスラッジの発生により冷媒回路が閉塞したりする危
険性が小さい。For example, an alkylbenzene oil, which is an oil that is weakly soluble in a refrigerant, is known as an oil having a very high stability, and even if foreign matter such as water is mixed in, it is not decomposed and sludge is generated. The risk of blockage of the refrigerant circuit is small.
【００４２】以上のように、本実施例の空気調和機は、
冷凍機油として非常に安定性が高い弱溶解性油であるア
ルキルベンゼン油を用いているため、設置工事などの
際、異物が混入してもシステムに故障を起こす危険性が
少なく高い信頼性を確保することができる。As described above, the air conditioner of this embodiment is
Alkylbenzene oil, which is a highly stable and weakly soluble oil, is used as the refrigeration oil, so there is little risk of system failure even if foreign matter enters during installation work, etc., ensuring high reliability. be able to.
【００４３】また、空気調和機に使用する冷媒として、
例えばＲ３２、Ｒ１３４ａ、Ｒ４１０Ａ，Ｒ４０７Ｃ、
Ｒ４０７Ｅ、Ｒ４０４ＡなどのＨＦＣ冷媒、または例え
ばＲ２９０、Ｒ６００ａなどのＨＣ冷媒を用いているた
め、オゾン層破壊など地球環境に悪影響を与えない空気
調和機を提供することができる。そこで、冷媒としてＨ
ＦＣ冷媒又はＨＣ冷媒を使用し、冷凍機油としてこれら
に弱溶解性であるアルキルベンゼン油を使用することに
より、安定性が高く、地球環境に悪影響を与えない空気
調和機を提供することができる。As a refrigerant used in the air conditioner,
For example, R32, R134a, R410A, R407C,
Since an HFC refrigerant such as R407E or R404A or an HC refrigerant such as R290 or R600a is used, an air conditioner that does not adversely affect the global environment such as ozone layer depletion can be provided. Therefore, H as a refrigerant
By using the FC refrigerant or the HC refrigerant and the weakly soluble alkylbenzene oil as the refrigerating machine oil, it is possible to provide an air conditioner having high stability and not adversely affecting the global environment.
【００４４】[0044]
【発明の効果】以上のように、本発明の請求項１に係る
空気調和機は、圧縮機、室外熱交換器、絞り装置及び室
内熱交換器を備えた空気調和機であって、室内熱交換器
は、第１室内熱交換器及び第２室内熱交換器から一体構
成され、第１室内熱交換器は、第１圧縮機、第１室外熱
交換器及び第１絞り装置とともに第１冷凍サイクルを構
成し、第２室内熱交換器は、第２圧縮機、第２室外熱交
換器及び第２絞り装置とともに第２冷凍サイクルを構成
し、第１冷凍サイクルで暖房運転を行い、同時に第２冷
凍サイクルで冷房運転を行うものである。そこで、加熱
運転と冷却運転を組合せた運転を行うことによって、再
熱除湿運転はもとより、室内熱交換器出口の温度、湿度
等の空気状態を自由に調整することができる。As described above, the air conditioner according to claim 1 of the present invention is an air conditioner including a compressor, an outdoor heat exchanger, a throttling device, and an indoor heat exchanger. The exchanger is integrally configured of a first indoor heat exchanger and a second indoor heat exchanger, and the first indoor heat exchanger is a first refrigeration unit together with a first compressor, a first outdoor heat exchanger and a first expansion device. The second indoor heat exchanger constitutes a second refrigeration cycle together with the second compressor, the second outdoor heat exchanger and the second expansion device, and performs the heating operation in the first refrigeration cycle, and at the same time, the second The cooling operation is performed in two refrigeration cycles. Therefore, by performing an operation that combines the heating operation and the cooling operation, it is possible to freely adjust not only the reheat dehumidifying operation but also the air condition such as the temperature and humidity at the outlet of the indoor heat exchanger.
【００４５】また、本発明の請求項２に係る空気調和機
は、請求項１記載の空気調和機において、第１室内熱交
換器を再熱用熱交換器とし、第２室内熱交換器を除湿用
熱交換器とするものである。そこで、除湿量と吹出し温
度を調整することが可能な再熱除湿運転を実現すること
ができる。An air conditioner according to claim 2 of the present invention is the air conditioner according to claim 1, wherein the first indoor heat exchanger is a reheat heat exchanger and the second indoor heat exchanger is The heat exchanger is for dehumidification. Therefore, the reheat dehumidifying operation capable of adjusting the dehumidifying amount and the blowing temperature can be realized.
【００４６】また、本発明の請求項３に係る空気調和機
は、請求項１または請求項２記載の空気調和機におい
て、第１圧縮機及び第２圧縮機は、容量制御装置を備え
たものである。そこで、除湿量と吹出し温度を広範囲に
調整することが可能となり、さらに吹出し空気温度を吸
込み空気温度よりも高くすることも可能となる。An air conditioner according to claim 3 of the present invention is the air conditioner according to claim 1 or 2, wherein the first compressor and the second compressor are provided with a capacity control device. Is. Therefore, it is possible to adjust the dehumidification amount and the blowing temperature in a wide range, and it is also possible to make the blowing air temperature higher than the suction air temperature.
【００４７】また、本発明の請求項４に係る空気調和機
は、請求項３の空気調和機において、除湿量は第２圧縮
機の容量制御装置で調節し、空気温度は第１圧縮機の容
量制御装置で調整するものである。そこで、除湿用熱交
換器の蒸発温度や再熱用熱交換器の凝縮温度を自由に制
御できるため、除湿量と吹出し空気温度を広範囲の中で
任意に設定することが可能となり、使用者の要求にあっ
た空気状態を作り出し快適感を与えることができるま
た、中間期冬期など室温が低い時も除湿運転が可能とな
るため、窓への結露防止など新しい機能を提供すること
ができる。According to a fourth aspect of the present invention, in the air conditioner according to the third aspect, the dehumidifying amount is adjusted by the capacity control device of the second compressor, and the air temperature of the first compressor is adjusted. It is adjusted by the capacity control device. Therefore, since the evaporation temperature of the dehumidifying heat exchanger and the condensing temperature of the reheating heat exchanger can be freely controlled, it becomes possible to arbitrarily set the dehumidifying amount and the blown air temperature in a wide range, and the user's It is possible to create a desired air condition and give a comfortable feeling. Also, since dehumidification operation is possible even when the room temperature is low such as in the middle of winter, it is possible to provide new functions such as prevention of dew condensation on windows.
【００４８】また、本発明の請求項５に係る空気調和機
は、請求項１〜４のいずれかの空気調和機において、室
内熱交換器は、上段側を第１室内熱交換器とし、下段側
を第２室内熱交換器としたものである。そこで、再熱用
熱交換器と除湿用熱交換器の接触部の面積が小さく、再
熱用熱交換器と除湿用熱交換器の間の熱ロスを小さくす
ることが可能となり、効率の良い再熱除湿運転をするこ
とができる。また、除湿用熱交換器を再熱用熱交換器の
下側に位置することにより、除湿用熱交換器の表面に結
露した露が再熱用熱交換器に触れることを防ぎ、結露水
の再蒸発を防止することができる。The air conditioner according to claim 5 of the present invention is the air conditioner according to any one of claims 1 to 4, wherein the indoor heat exchanger has a first indoor heat exchanger on the upper stage side and a lower stage. The side is the second indoor heat exchanger. Therefore, the area of the contact portion between the reheat heat exchanger and the dehumidifying heat exchanger is small, and it is possible to reduce the heat loss between the reheat heat exchanger and the dehumidifying heat exchanger, resulting in high efficiency. Reheat dehumidification operation can be performed. Also, by placing the dehumidifying heat exchanger below the reheating heat exchanger, it is possible to prevent dew condensation on the surface of the dehumidifying heat exchanger from touching the reheating heat exchanger. Re-evaporation can be prevented.
【００４９】また、本発明の請求項６に係る空気調和機
は、請求項５の空気調和機において、第１室内熱交換器
の冷媒の流れ方向は、風向に対して対向流とし、第２室
内熱交換器の冷媒の流れ方向は、風向に対して並行流と
したものである。そこで、再熱用熱交換器、除湿用熱交
換器ともに入口から出口まで全領域で冷媒と空気の温度
差を確保することが可能となり効率の良い熱交換を行う
ことができる。The air conditioner according to a sixth aspect of the present invention is the air conditioner according to the fifth aspect, wherein the flow direction of the refrigerant in the first indoor heat exchanger is a counterflow with respect to the wind direction. The flow direction of the refrigerant in the indoor heat exchanger is parallel to the wind direction. Therefore, both the reheat heat exchanger and the dehumidifying heat exchanger can secure a temperature difference between the refrigerant and the air in the entire region from the inlet to the outlet, and efficient heat exchange can be performed.
【００５０】また、本発明の請求項７に係る空気調和機
は、請求項１〜４のいずれかにの空気調和機において、
室内熱交換器を風上側に第２室内熱交換器、風下側に第
１熱交換器の配置としたものである。そこで、除湿用熱
交換器３ｂにおいて空気が通過する前面面積を広く取る
ことが可能となり、効率良く除湿することができる。ま
た、除湿用熱交換器を通過し、冷却除湿された空気をす
べて再熱用熱交換器へ通すことができるため、室内熱交
換器出口空気の温度を一様とすることができる。An air conditioner according to claim 7 of the present invention is the air conditioner according to any one of claims 1 to 4.
The indoor heat exchanger has a second indoor heat exchanger on the windward side and a first heat exchanger on the leeward side. Therefore, in the dehumidifying heat exchanger 3b, it is possible to increase the area of the front surface through which the air passes, and it is possible to dehumidify efficiently. Further, since all the air that has passed through the dehumidifying heat exchanger and has been cooled and dehumidified can be passed to the reheat heat exchanger, the temperature of the indoor heat exchanger outlet air can be made uniform.
【００５１】また、本発明の請求項８に係る空気調和機
は、請求項１〜７の空気調和機において、箱体の中に室
内熱交換器、送風機を収納して室内ユニットを構成し、
室内熱交換器で熱交換した空気を室内ユニットに接続さ
れたダクトから室内へ送風するダクト式室内ユニットを
備えたものである。そこで、室内熱交換器の第１室内熱
交換器にて加熱された空気と第２室内熱交換器にて冷却
除湿された空気を均一に混合した状態で室内側へ送風す
ることが可能となり、使用者に対して吹出し空気温度む
らによる不快性を与えることを防止できると共に、吹出
し空気温度むらによる露付きなども防止することができ
る。An air conditioner according to claim 8 of the present invention is the air conditioner according to any one of claims 1 to 7, wherein an indoor heat exchanger and a blower are housed in a box to form an indoor unit,
This is provided with a duct type indoor unit that blows the air, which has been heat-exchanged by the indoor heat exchanger, into the room from the duct connected to the indoor unit. Therefore, it becomes possible to blow the air heated in the first indoor heat exchanger of the indoor heat exchanger and the air dehumidified in the second indoor heat exchanger to the indoor side in a uniformly mixed state, It is possible to prevent the user from being uncomfortable due to the uneven temperature of the blown air, and also to prevent dew formation due to the uneven temperature of the blown air.
【００５２】また、本発明の請求項９に係る空気調和機
は、請求項１〜８のいずれかの空気調和機において、第
１冷凍サイクル及び第２冷凍サイクル共に冷房運転する
か、またはどちらか一方で冷房運転し、他方は運転停止
とするものである。そこで、本冷凍サイクルには従来の
除湿用絞り装置など通常冷房運転時に効率を悪化させる
部品を用いていないため、通常冷房運転時においても本
来の冷凍サイクルにおける効率にて運転することができ
る。According to a ninth aspect of the present invention, in the air conditioner according to any of the first to eighth aspects, either the first refrigerating cycle or the second refrigerating cycle is cooled or operated. The cooling operation is performed on the one hand and the operation is stopped on the other. Therefore, since the refrigeration cycle does not use a component such as a conventional dehumidifying expansion device that deteriorates the efficiency during the normal cooling operation, the refrigeration cycle can be operated at the original efficiency during the normal cooling operation.
【００５３】また、本発明の請求項１０に係る空気調和
機は、請求項１〜９のいずれかの空気調和機において、
圧縮機の冷凍機油として、冷媒に弱溶解性の冷凍機油を
用いたものである。そこで、設置工事などの際、異物が
混入してもシステムに故障を起こす危険性が少なく高い
信頼性を確保することができる。An air conditioner according to claim 10 of the present invention is the air conditioner according to any one of claims 1 to 9.
As the refrigerating machine oil of the compressor, a refrigerating machine oil having a weak solubility in the refrigerant is used. Therefore, at the time of installation work or the like, even if foreign matter is mixed in, there is little risk of causing a failure in the system, and high reliability can be secured.
【００５４】また、本発明の請求項１１に係る空気調和
機は、請求項１〜１０のいずれかの空気調和機におい
て、冷凍サイクルに使用する冷媒として、ＨＦＣ冷媒ま
たはＨＣ冷媒を用いたものである。そこで、空気調和機
において、ＨＦＣ冷媒またはＨＣ冷媒を用いているた
め、オゾン層破壊や地球温暖化など地球環境に悪影響を
与えない空気調和機を提供することができる。The air conditioner according to claim 11 of the present invention is the air conditioner according to any one of claims 1 to 10, wherein HFC refrigerant or HC refrigerant is used as the refrigerant used in the refrigeration cycle. is there. Therefore, since the HFC refrigerant or the HC refrigerant is used in the air conditioner, it is possible to provide an air conditioner that does not adversely affect the global environment such as ozone layer depletion and global warming.
【図１】 本発明の実施の形態1に係る空気調和機の冷
凍サイクルを示す冷媒回路図である。FIG. 1 is a refrigerant circuit diagram showing a refrigeration cycle of an air conditioner according to Embodiment 1 of the present invention.
【図２】 本発明の実施の形態1に係る空気調和機の冷
凍サイクルを示す別の冷媒回路図である。FIG. 2 is another refrigerant circuit diagram showing the refrigeration cycle of the air-conditioning apparatus according to Embodiment 1 of the present invention.
【図３】 本発明の実施の形態１に係る空気調和機の再
熱除湿運転の制御フローチャートである。FIG. 3 is a control flowchart of a reheat dehumidifying operation of the air conditioner according to Embodiment 1 of the present invention.
【図４】 本発明の実施の形態１に係る空気調和機の再
熱除湿運転の別の制御フローチャートである。FIG. 4 is another control flowchart of the reheat dehumidifying operation of the air conditioner according to Embodiment 1 of the present invention.
【図５】 本発明の実施の形態２に係る空気調和機に用
いられる室内熱交換器の構成図である。FIG. 5 is a configuration diagram of an indoor heat exchanger used in the air conditioner according to Embodiment 2 of the present invention.
【図６】 本発明の実施の形態２に係る空気調和機に用
いられる室内熱交換器の再熱用熱交換器内の冷媒と空気
の温度変化を示す図である。FIG. 6 is a diagram showing temperature changes of a refrigerant and air in a reheat heat exchanger of an indoor heat exchanger used in an air conditioner according to Embodiment 2 of the present invention.
【図７】 本発明の実施の形態２に係る空気調和機に用
いられる室内熱交換器の除湿用熱交換器内の冷媒と空気
の温度変化を示す図である。FIG. 7 is a diagram showing temperature changes of a refrigerant and air in a dehumidifying heat exchanger of an indoor heat exchanger used in an air conditioner according to Embodiment 2 of the present invention.
【図８】 本発明の実施の形態３に係る空気調和機に用
いられる室内熱交換器の構成図である。FIG. 8 is a configuration diagram of an indoor heat exchanger used in an air conditioner according to Embodiment 3 of the present invention.
【図９】 本発明の実施の形態４に係る空気調和機の構
成図である。FIG. 9 is a configuration diagram of an air conditioner according to Embodiment 4 of the present invention.
【図１０】 従来の空気調和機の冷凍サイクルを示す冷
媒回路図である。FIG. 10 is a refrigerant circuit diagram showing a refrigeration cycle of a conventional air conditioner.
１ 圧縮機、１ａ 第１圧縮機、１ｂ 第２圧縮機、３
室内熱交換器、３ａ第１室内熱交換器、 ３ｂ 第２
室内熱交換器、５ 絞り装置、５ａ 第１絞り装置、５
ｂ 第２絞り装置、６ 室外熱交換器、６ａ 第１室外
熱交換器、６ｂ 第２室外熱交換器、１０ａ 第１冷凍
サイクル、１０ｂ 第２冷凍サイクル、５０ 室内ユニ
ット、５１ 送風機、５３ ダクト、６０ 容量制御装
置。1 compressor, 1a first compressor, 1b second compressor, 3
Indoor heat exchanger, 3a first indoor heat exchanger, 3b second
Indoor heat exchanger, 5 expansion device, 5a 1st expansion device, 5
b second expansion device, 6 outdoor heat exchanger, 6a first outdoor heat exchanger, 6b second outdoor heat exchanger, 10a first refrigeration cycle, 10b second refrigeration cycle, 50 indoor unit, 51 blower, 53 duct, 60 Capacity control device.
─────────────────────────────────────────────────────
─────────────────────────────────────────────────── ───
【手続補正書】[Procedure amendment]
【提出日】平成１３年１１月１日（２００１．１１．
１）[Submission date] November 1, 2001 (2001.11.
1)
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】発明の名称[Name of item to be amended] Title of invention
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【発明の名称】 空気調和機
─────────────────────────────────────────────────────
[Title of Invention] Air conditioner ─────────────────────────────────────────── ───────────
【手続補正書】[Procedure amendment]
【提出日】平成１５年２月３日（２００３．２．３）[Submission date] February 3, 2003 (2003.2.3)
【手続補正１】[Procedure Amendment 1]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】特許請求の範囲[Name of item to be amended] Claims
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【特許請求の範囲】[Claims]
【請求項９】 前記室内熱交換器は、上段側を第１室内
熱交換器とし、下段側を第２室内熱交換器としたことを
特徴とする請求項１〜８のいずれかに記載の空気調和
機。 Wherein said indoor heat exchanger, the upper side and the first indoor heat exchanger, according to any one of claims 1 to 8, characterized in that the lower side and the second indoor heat exchanger Air conditioner.
【請求項１０】 第１室内熱交換器の冷媒の流れ方向
は、風向に対して対向流とし、第２室内熱交換器の冷媒
の流れ方向は、風向に対して並行流としたことを特徴と
する請求項９記載の空気調和機。 10. The flow direction of the refrigerant in the first indoor heat exchanger is a counterflow to the wind direction, and the flow direction of the refrigerant in the second indoor heat exchanger is a parallel flow to the wind direction. The air conditioner according to claim 9 .
【請求項１１】 前記室内熱交換器を風上側に第２室内
熱交換器、風下側に第１熱交換器の配置としたことを特
徴とする請求項１〜８のいずれかに記載の空気調和機。 11. The air according to any one of claims 1 to 8, characterized in that said indoor heat exchanger second indoor heat exchanger on the windward side, and the arrangement of the first heat exchanger downwind Harmony machine.
【請求項１２】 箱体の中に前記室内熱交換器、送風機
を収納して室内ユニットを構成し、前記室内熱交換器で
熱交換した空気を前記室内ユニットに接続されたダクト
から室内へ送風するダクト式室内ユニットを備えたこと
を特徴とする請求項１〜請求項１１のいずれかに記載の
空気調和機。The indoor heat exchanger in the 12. box, blowing constitute the indoor unit housing the blower, the air heat-exchanged by the indoor heat exchanger from the connected ducts to the indoor unit to the room The air conditioner according to any one of claims 1 to 11 , further comprising a duct type indoor unit.
【請求項１３】 前記第１冷凍サイクル及び第２冷凍サ
イクル共に冷房運転するか、またはどちらか一方で冷房
運転し、他方は運転停止とすることを特徴とする請求項
１〜１２のいずれかに記載の空気調和機。 13. Either the cooling operation to the first refrigeration cycle and the second refrigeration cycle both or cooling operation either on the one hand, and the other to any one of claims 1 to 12, characterized in that the shutdown Air conditioner described.
【請求項１４】 前記圧縮機の冷凍機油として、冷媒に
弱溶解性の冷凍機油を用いたことを特徴とする請求項１
〜１３のいずれかに記載の空気調和機。 14. The refrigerating machine oil of the compressor is a refrigerating machine oil having a weak solubility in a refrigerant.
The air conditioner according to any one of to 13 .
【請求項１５】 前記冷凍サイクルに使用する冷媒とし
て、ＨＦＣ冷媒またはＨＣ冷媒を用いたことを特徴とす
る請求項１〜１４のいずれかに記載の空気調和機。 15. As refrigerant used in the refrigeration cycle, an air conditioner according to any one of claims 1 to 14, characterized in that with HFC refrigerant or HC refrigerant.
【手続補正２】[Procedure Amendment 2]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１２[Correction target item name] 0012
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１２】また、本発明の請求項４〜請求項８に係る
空気調和機は、それぞれ、除湿量を第２圧縮機の容量制
御装置で調節し、空気温度を第１圧縮機の容量制御装置
で調整するものであり、再熱除湿運転により、再熱用熱
交換器の検出凝縮温度が目標凝縮温度に近づくように第
１圧縮機の運転周波数を制御するものであり、再熱除湿
運転により、除湿用熱交換器の蒸発温度が目標蒸発温度
に近づくように第２圧縮機の運転周波数を制御するもの
であり、再熱除湿運転により、再熱用熱交換器の検出吸
込み空気温度が目標空気温度となるように第１圧縮機の
運転周波数を制御するものであり、また、再熱除湿運転
により、除湿用熱交換器の吸込み空気湿度が目標空気湿
度となるように第２圧縮機の運転周波数を制御するもの
である。 Further, according to claims 4 to 8 of the present invention.
Each air conditioner controls the dehumidification amount by the capacity control of the second compressor.
Control the air temperature to control the air temperature of the first compressor
The heat for reheating is adjusted by the reheat dehumidification operation.
Make sure that the detected condensing temperature of the exchanger is close to the target condensing temperature.
1 It controls the operating frequency of the compressor, and reheat dehumidification
Depending on the operation, the evaporation temperature of the dehumidifying heat exchanger will be the target evaporation temperature.
For controlling the operating frequency of the second compressor to approach
Therefore, the reheat dehumidification operation detects and detects the reheat heat exchanger.
Set the first compressor so that the intake air temperature becomes the target air temperature.
It controls the operating frequency, and reheat dehumidification operation
Causes the intake air humidity of the dehumidifying heat exchanger to change to the target air humidity.
To control the operating frequency of the second compressor so that
Is.
【手続補正３】[Procedure 3]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１３[Correction target item name] 0013
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１３】また、本発明の請求項９に係る空気調和機
は、室内熱交換器を、上段側を第１室内熱交換器とし、
下段側を第２室内熱交換器としたものである。[0013] The air conditioner according to claim 9 of the present invention, the chamber heat exchanger, and the upper side of the first indoor heat exchanger,
The lower side is the second indoor heat exchanger.
【手続補正４】[Procedure amendment 4]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１４[Correction target item name] 0014
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１４】また、本発明の請求項１０に係る空気調和
機は、第１室内熱交換器の冷媒の流れ方向を、風向に対
して対向流とし、第２室内熱交換器の冷媒の流れ方向
を、風向に対して並行流としたものである。In the air conditioner according to a tenth aspect of the present invention, the flow direction of the refrigerant in the first indoor heat exchanger is set to be a counterflow with respect to the wind direction , and the flow direction of the refrigerant in the second indoor heat exchanger is set.
Is parallel to the wind direction.
【手続補正５】[Procedure Amendment 5]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１５[Name of item to be corrected] 0015
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１５】また、本発明の請求項１１に係る空気調和
機は、室内熱交換器を風上側に第２室内熱交換器、風下
側に第１熱交換器の配置としたものである。[0015] The air conditioner according to claim 11 of the present invention, the second indoor heat exchanger chamber heat exchanger on the windward side, is obtained by the arrangement of the first heat exchanger on the leeward side.
【手続補正６】[Procedure correction 6]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１６[Correction target item name] 0016
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１６】また、本発明の請求項１２に係る空気調和
機は、箱体の中に室内熱交換器、送風機を収納して室内
ユニットを構成し、室内熱交換器で熱交換した空気を室
内ユニットに接続されたダクトから室内へ送風するダク
ト式室内ユニットを備えたものである。[0016] The air conditioner according to claim 12 of the present invention, the indoor heat exchanger in the box body, constitutes the indoor unit housing the blower, the indoor air heat-exchanged in the indoor heat exchanger It is provided with a duct type indoor unit that blows air indoors from a duct connected to the unit.
【手続補正７】[Procedure Amendment 7]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１７[Correction target item name] 0017
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１７】また、本発明の請求項１３に係る空気調和
機は、第１冷凍サイクル及び第２冷凍サイクル共に冷房
運転するか、またはどちらか一方で冷房運転し、他方は
運転停止とするものである。In the air conditioner according to a thirteenth aspect of the present invention, either the first refrigerating cycle and the second refrigerating cycle are cooled, or either one is cooled and the other is stopped. is there.
【手続補正８】[Procedure Amendment 8]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１８[Correction target item name] 0018
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１８】本発明の請求項１４に係る空気調和機は、
圧縮機の冷凍機油として、冷媒に弱溶解性の冷凍機油を
用いたものである。An air conditioner according to claim 14 of the present invention comprises :
As refrigerating machine oil compressors, those with weak solubility of the refrigerating machine oil in the refrigerant.
【手続補正９】[Procedure Amendment 9]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００１９[Correction target item name] 0019
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００１９】本発明の請求項１５に係る空気調和機は、
冷凍サイクルに使用する冷媒として、ＨＦＣ冷媒または
ＨＣ冷媒を用いたものである。The air conditioner according to claim 15 of the present invention,
As refrigerant used in the refrigeration cycle, in which using a HFC refrigerant or HC refrigerant.
【手続補正１０】[Procedure Amendment 10]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００４７[Correction target item name] 0047
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００４７】また、本発明の請求項４〜請求項８に係る
空気調和機は、それぞれ、除湿量を第２圧縮機の容量制
御装置で調節し、空気温度を第１圧縮機の容量制御装置
で調整するものであり、再熱除湿運転により、再熱用熱
交換器の検出凝縮温度が目標凝縮温度に近づくように第
１圧縮機の運転周波数を制御するものであり、再熱除湿
運転により、除湿用熱交換器の蒸発温度が目標蒸発温度
に近づくように第２圧縮機の運転周波数を制御するもの
であり、再熱除湿運転により、再熱用熱交換器の検出吸
込み空気温度が目標空気温度となるように第１圧縮機の
運転周波数を制御するものであり、また、再熱除湿運転
により、除湿用熱交換器の吸込み空気湿度が目標空気湿
度となるように第２圧縮機の運転周波数を制御するもの
である。そこで、除湿用熱交換器の蒸発温度や再熱用熱
交換器の凝縮温度を自由に制御できるため、除湿量と吹
出し空気温度を広範囲の中で任意に設定することが可能
となり、使用者の要求にあった空気状態を作り出し快適
感を与えることができるまた、中間期冬期など室温が低
い時も除湿運転が可能となるため、窓への結露防止など
新しい機能を提供することができる。Further, according to claims 4 to 8 of the present invention.
Each air conditioner controls the dehumidification amount by the capacity control of the second compressor.
Control the air temperature to control the air temperature of the first compressor
The heat for reheating is adjusted by the reheat dehumidification operation.
Make sure that the detected condensing temperature of the exchanger is close to the target condensing temperature.
1 It controls the operating frequency of the compressor, and reheat dehumidification
Depending on the operation, the evaporation temperature of the dehumidifying heat exchanger will be the target evaporation temperature.
For controlling the operating frequency of the second compressor to approach
Therefore, the reheat dehumidification operation detects and detects the reheat heat exchanger.
Set the first compressor so that the intake air temperature becomes the target air temperature.
It controls the operating frequency, and reheat dehumidification operation
Causes the intake air humidity of the dehumidifying heat exchanger to change to the target air humidity.
To control the operating frequency of the second compressor so that
Is. Therefore, since the evaporation temperature of the dehumidifying heat exchanger and the condensing temperature of the reheating heat exchanger can be freely controlled, it becomes possible to arbitrarily set the dehumidifying amount and the blown air temperature in a wide range, and the user's It is possible to create a desired air condition and give a comfortable feeling. Also, since dehumidification operation is possible even when the room temperature is low such as in the middle of winter, it is possible to provide new functions such as prevention of dew condensation on windows.
【手続補正１１】[Procedure Amendment 11]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００４８[Correction target item name] 0048
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００４８】また、本発明の請求項９に係る空気調和機
は、室内熱交換器を、上段側を第１室内熱交換器とし、
下段側を第２室内熱交換器としたものである。そこで、
再熱用熱交換器と除湿用熱交換器の接触部の面積が小さ
く、再熱用熱交換器と除湿用熱交換器の間の熱ロスを小
さくすることが可能となり、効率の良い再熱除湿運転を
することができる。また、除湿用熱交換器を再熱用熱交
換器の下側に位置することにより、除湿用熱交換器の表
面に結露した露が再熱用熱交換器に触れることを防ぎ、
結露水の再蒸発を防止することができる。[0048] The air conditioner according to claim 9 of the present invention, the chamber heat exchanger, and the upper side of the first indoor heat exchanger,
The lower side is the second indoor heat exchanger. Therefore,
The area of contact between the reheat heat exchanger and the dehumidification heat exchanger is small, which makes it possible to reduce the heat loss between the reheat heat exchanger and the dehumidification heat exchanger, resulting in efficient reheat. Dehumidification operation can be performed. Also, by positioning the dehumidifying heat exchanger below the reheating heat exchanger, it is possible to prevent dew condensation on the surface of the dehumidifying heat exchanger from touching the reheating heat exchanger,
It is possible to prevent re-evaporation of condensed water.
【手続補正１２】[Procedure Amendment 12]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００４９[Correction target item name] 0049
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００４９】また、本発明の請求項１０に係る空気調和
機は、第１室内熱交換器の冷媒の流れ方向を、風向に対
して対向流とし、第２室内熱交換器の冷媒の流れ方向
を、風向に対して並行流としたものである。そこで、再
熱用熱交換器、除湿用熱交換器ともに入口から出口まで
全領域で冷媒と空気の温度差を確保することが可能とな
り効率の良い熱交換を行うことができる。In the air conditioner according to a tenth aspect of the present invention, the flow direction of the refrigerant in the first indoor heat exchanger is set to be a counterflow with respect to the wind direction , and the flow direction of the refrigerant in the second indoor heat exchanger is set.
Is parallel to the wind direction. Therefore, both the reheat heat exchanger and the dehumidifying heat exchanger can secure a temperature difference between the refrigerant and the air in the entire region from the inlet to the outlet, and efficient heat exchange can be performed.
【手続補正１３】[Procedure Amendment 13]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００５０[Correction target item name] 0050
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００５０】また、本発明の請求項１１に係る空気調和
機は、室内熱交換器を風上側に第２室内熱交換器、風下
側に第１熱交換器の配置としたものである。そこで、除
湿用熱交換器において空気が通過する前面面積を広く取
ることが可能となり、効率良く除湿することができる。
また、除湿用熱交換器を通過し、冷却除湿された空気を
すべて再熱用熱交換器へ通すことができるため、室内熱
交換器出口空気の温度を一様とすることができる。[0050] The air conditioner according to claim 11 of the present invention, the second indoor heat exchanger chamber heat exchanger on the windward side, is obtained by the arrangement of the first heat exchanger on the leeward side. Therefore, Oite air to the heat exchanger for dehumidification becomes possible to widen the frontal area to pass, it can be efficiently dehumidified.
Further, since all the air that has passed through the dehumidifying heat exchanger and has been cooled and dehumidified can be passed to the reheat heat exchanger, the temperature of the indoor heat exchanger outlet air can be made uniform.
【手続補正１４】[Procedure Amendment 14]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００５１[Correction target item name] 0051
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００５１】また、本発明の請求項１２に係る空気調和
機は、箱体の中に室内熱交換器、送風機を収納して室内
ユニットを構成し、室内熱交換器で熱交換した空気を室
内ユニットに接続されたダクトから室内へ送風するダク
ト式室内ユニットを備えたものである。そこで、室内熱
交換器の第１室内熱交換器にて加熱された空気と第２室
内熱交換器にて冷却除湿された空気を均一に混合した状
態で室内側へ送風することが可能となり、使用者に対し
て吹出し空気温度むらによる不快性を与えることを防止
できると共に、吹出し空気温度むらによる露付きなども
防止することができる。[0051] The air conditioner according to claim 12 of the present invention, the indoor heat exchanger in the box body, constitutes the indoor unit housing the blower, the indoor air heat-exchanged in the indoor heat exchanger It is provided with a duct type indoor unit that blows air indoors from a duct connected to the unit. Therefore, it becomes possible to blow the air heated in the first indoor heat exchanger of the indoor heat exchanger and the air dehumidified in the second indoor heat exchanger to the indoor side in a uniformly mixed state, It is possible to prevent the user from being uncomfortable due to the uneven temperature of the blown air, and also to prevent dew formation due to the uneven temperature of the blown air.
【手続補正１５】[Procedure Amendment 15]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００５２[Correction target item name] 0052
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００５２】また、本発明の請求項１３に係る空気調和
機は、第１冷凍サイクル及び第２冷凍サイクル共に冷房
運転するか、またはどちらか一方で冷房運転し、他方は
運転停止とするものである。そこで、本冷凍サイクルに
は従来の除湿用絞り装置など通常冷房運転時に効率を悪
化させる部品を用いていないため、通常冷房運転時にお
いても本来の冷凍サイクルにおける効率にて運転するこ
とができる。Further , in the air conditioner according to claim 13 of the present invention, either the first refrigerating cycle and the second refrigerating cycle perform cooling operation, or either one performs cooling operation and the other stops. is there. Therefore, since the refrigeration cycle does not use a component such as a conventional dehumidifying expansion device that deteriorates the efficiency during the normal cooling operation, the refrigeration cycle can be operated at the original efficiency during the normal cooling operation.
【手続補正１６】[Procedure Amendment 16]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００５３[Correction target item name] 0053
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００５３】本発明の請求項１４に係る空気調和機は、
圧縮機の冷凍機油として、冷媒に弱溶解性の冷凍機油を
用いたものである。そこで、設置工事などの際、異物が
混入してもシステムに故障を起こす危険性が少なく高い
信頼性を確保することができる。An air conditioner according to claim 14 of the present invention comprises :
As refrigerating machine oil compressors, those with weak solubility of the refrigerating machine oil in the refrigerant. Therefore, at the time of installation work or the like, even if foreign matter is mixed in, there is little risk of causing a failure in the system, and high reliability can be secured.
【手続補正１７】[Procedure Amendment 17]
【補正対象書類名】明細書[Document name to be amended] Statement
【補正対象項目名】００５４[Correction target item name] 0054
【補正方法】変更[Correction method] Change
【補正内容】[Correction content]
【００５４】また、本発明の請求項１５に係る空気調和
機は、冷凍サイクルに使用する冷媒として、ＨＦＣ冷媒
またはＨＣ冷媒を用いたものである。そこで、空気調和
機において、ＨＦＣ冷媒またはＨＣ冷媒を用いているた
め、オゾン層破壊や地球温暖化など地球環境に悪影響を
与えない空気調和機を提供することができる。[0054] The air conditioner according to claim 15 of the present invention, as the refrigerant used in the refrigeration cycle, in which using a HFC refrigerant or HC refrigerant. Therefore, since the HFC refrigerant or the HC refrigerant is used in the air conditioner, it is possible to provide an air conditioner that does not adversely affect the global environment such as ozone layer depletion and global warming.
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ２４Ｆ 13/30 Ｆ２４Ｆ 1/00 ３９１Ａ (72)発明者 横山 博 東京都千代田区丸の内二丁目２番３号 三 菱電機株式会社内 Ｆターム(参考） 3L051 BE05 BG06 BJ03 BJ10 3L060 AA06 DD02 EE02 ─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. 7 Identification code FI theme code (reference) F24F 13/30 F24F 1/00 391A (72) Inventor Hiroshi Yokoyama 2-3-2 Marunouchi, Chiyoda-ku, Tokyo Sanryo Electric Co., Ltd. F term (reference) 3L051 BE05 BG06 BJ03 BJ10 3L060 AA06 DD02 EE02
Claims (11)
内熱交換器を備えた空気調和機であって、 前記室内熱交換器は、第１室内熱交換器及び第２室内熱
交換器から一体構成され、 前記第１室内熱交換器は、第１圧縮機、第１室外熱交換
器及び第１絞り装置とともに第１冷凍サイクルを構成
し、 前記第２室内熱交換器は、第２圧縮機、第２室外熱交換
器及び第２絞り装置とともに第２冷凍サイクルを構成
し、 前記第１冷凍サイクルで暖房運転を行い、同時に前記第
２冷凍サイクルで冷房運転を行うことを特徴とする空気
調和機。1. An air conditioner comprising a compressor, an outdoor heat exchanger, a throttling device, and an indoor heat exchanger, wherein the indoor heat exchanger is a first indoor heat exchanger and a second indoor heat exchanger. The first indoor heat exchanger constitutes a first refrigeration cycle together with a first compressor, a first outdoor heat exchanger and a first expansion device, and the second indoor heat exchanger has a second A second refrigeration cycle is configured with a compressor, a second outdoor heat exchanger, and a second expansion device, heating operation is performed in the first refrigeration cycle, and cooling operation is performed in the second refrigeration cycle at the same time. Air conditioner.
とし、前記第２室内熱交換器を除湿用熱交換器とするこ
とを特徴とする請求項１記載の空気調和機。2. The air conditioner according to claim 1, wherein the first indoor heat exchanger is a reheat heat exchanger, and the second indoor heat exchanger is a dehumidifying heat exchanger.
容量制御装置を備えたことを特徴とする請求項１または
請求項２記載の記載の空気調和機。3. The first compressor and the second compressor,
The air conditioner according to claim 1 or 2, further comprising a capacity control device.
節し、空気温度は第１圧縮機の容量制御装置で調整する
ことを特徴とする請求項３記載の空気調和機。4. The air conditioner according to claim 3, wherein the dehumidification amount is adjusted by the capacity control device of the second compressor, and the air temperature is adjusted by the capacity control device of the first compressor.
熱交換器とし、下段側を第２室内熱交換器としたことを
特徴とする請求項１〜４のいずれかに記載の空気調和
機。5. The indoor heat exchanger according to claim 1, wherein the upper stage side is a first indoor heat exchanger and the lower stage side is a second indoor heat exchanger. Air conditioner.
風向に対して対向流とし、第２室内熱交換器の冷媒の流
れ方向は、風向に対して並行流としたことを特徴とする
請求項５記載の空気調和機。6. The flow direction of the refrigerant in the first indoor heat exchanger is
The air conditioner according to claim 5, wherein the air flow is a counterflow to the wind direction, and the flow direction of the refrigerant in the second indoor heat exchanger is a parallel flow to the air direction.
交換器、風下側に第１熱交換器の配置としたことを特徴
とする請求項１〜４のいずれかに記載の空気調和機。7. The air according to claim 1, wherein the indoor heat exchanger has a second indoor heat exchanger on the windward side and a first heat exchanger on the leeward side. Harmony machine.
収納して室内ユニットを構成し、前記室内熱交換器で熱
交換した空気を前記室内ユニットに接続されたダクトか
ら室内へ送風するダクト式室内ユニットを備えたことを
特徴とする請求項１〜請求項７のいずれかに記載の空気
調和機。8. An indoor unit is configured by accommodating the indoor heat exchanger and a blower in a box, and air that has been heat-exchanged by the indoor heat exchanger is blown indoors from a duct connected to the indoor unit. The air conditioner according to any one of claims 1 to 7, further comprising a duct type indoor unit.
クル共に冷房運転するか、またはどちらか一方で冷房運
転し、他方は運転停止とすることを特徴とする請求項１
〜８のいずれかに記載の空気調和機。9. The cooling operation of both the first refrigeration cycle and the second refrigeration cycle, or cooling operation of either one of them, and operation stop of the other.
The air conditioner according to any one of to 8.
弱溶解性の冷凍機油を用いたことを特徴とする請求項１
〜９のいずれかに記載の空気調和機。10. The refrigerating machine oil of the compressor is a refrigerating machine oil having a weak solubility in a refrigerant.
The air conditioner according to any one of to 9.
て、ＨＦＣ冷媒またはＨＣ冷媒を用いたことを特徴とす
る請求項１〜１０のいずれかに記載の空気調和機。11. The air conditioner according to claim 1, wherein an HFC refrigerant or an HC refrigerant is used as the refrigerant used in the refrigeration cycle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001334310A JP2003139436A (en) | 2001-10-31 | 2001-10-31 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001334310A JP2003139436A (en) | 2001-10-31 | 2001-10-31 | Air conditioner |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003139436A true JP2003139436A (en) | 2003-05-14 |
Family
ID=19149460
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001334310A Pending JP2003139436A (en) | 2001-10-31 | 2001-10-31 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003139436A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100813555B1 (en) * | 2006-09-25 | 2008-03-17 | 이운상 | Thermo-hygrostat |
| JP2010121798A (en) * | 2008-11-17 | 2010-06-03 | Mitsubishi Electric Corp | Air conditioning equipment |
| WO2014132433A1 (en) * | 2013-03-01 | 2014-09-04 | 三菱電機株式会社 | Air conditioning device |
| WO2015173896A1 (en) * | 2014-05-13 | 2015-11-19 | 三菱電機株式会社 | Air conditioning system |
| JP2017015316A (en) * | 2015-06-30 | 2017-01-19 | ダイキン工業株式会社 | Air conditioner |
| CN111397183A (en) * | 2020-04-03 | 2020-07-10 | 珠海格力电器股份有限公司 | Air conditioning unit with additional heat exchanger |
| CN112577101A (en) * | 2019-09-11 | 2021-03-30 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
| CN115854448A (en) * | 2022-12-28 | 2023-03-28 | 北京建筑大学 | Double-evaporation temperature and humidity independent control air conditioner |
| CN112577101B (en) * | 2019-09-11 | 2024-06-25 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
-
2001
- 2001-10-31 JP JP2001334310A patent/JP2003139436A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100813555B1 (en) * | 2006-09-25 | 2008-03-17 | 이운상 | Thermo-hygrostat |
| JP2010121798A (en) * | 2008-11-17 | 2010-06-03 | Mitsubishi Electric Corp | Air conditioning equipment |
| JP4667496B2 (en) * | 2008-11-17 | 2011-04-13 | 三菱電機株式会社 | Air conditioner |
| WO2014132433A1 (en) * | 2013-03-01 | 2014-09-04 | 三菱電機株式会社 | Air conditioning device |
| GB2540906A (en) * | 2014-05-13 | 2017-02-01 | Mitsubishi Electric Corp | Air conditioning system |
| WO2015173896A1 (en) * | 2014-05-13 | 2015-11-19 | 三菱電機株式会社 | Air conditioning system |
| US10317120B2 (en) | 2014-05-13 | 2019-06-11 | Mitsubishi Electric Corporation | Air conditioning system with indoor and ventilation circuits |
| GB2540906B (en) * | 2014-05-13 | 2020-03-04 | Mitsubishi Electric Corp | Air conditioning system |
| JP2017015316A (en) * | 2015-06-30 | 2017-01-19 | ダイキン工業株式会社 | Air conditioner |
| CN112577101A (en) * | 2019-09-11 | 2021-03-30 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
| CN112577101B (en) * | 2019-09-11 | 2024-06-25 | 广东美的制冷设备有限公司 | Air conditioner and control method thereof |
| CN111397183A (en) * | 2020-04-03 | 2020-07-10 | 珠海格力电器股份有限公司 | Air conditioning unit with additional heat exchanger |
| CN115854448A (en) * | 2022-12-28 | 2023-03-28 | 北京建筑大学 | Double-evaporation temperature and humidity independent control air conditioner |
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