JP2003097842A - Air-conditioner - Google Patents

Air-conditioner

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Publication number
JP2003097842A
JP2003097842A JP2002262509A JP2002262509A JP2003097842A JP 2003097842 A JP2003097842 A JP 2003097842A JP 2002262509 A JP2002262509 A JP 2002262509A JP 2002262509 A JP2002262509 A JP 2002262509A JP 2003097842 A JP2003097842 A JP 2003097842A
Authority
JP
Japan
Prior art keywords
heat exchanger
indoor
compressor
indoor heat
dehumidifying
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.)
Granted
Application number
JP2002262509A
Other languages
Japanese (ja)
Other versions
JP3653261B2 (en
Inventor
Hiroo Nakamura
啓夫 中村
Hidenori Yokoyama
英範 横山
Motoo Morimoto
素生 森本
Hironobu Kawamura
浩伸 川村
Kazuya Matsuo
一也 松尾
Hiroshi Kogure
博志 小暮
Akinobu Okamura
哲信 岡村
Soichi Kosoto
荘一 小曽戸
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP2002262509A priority Critical patent/JP3653261B2/en
Publication of JP2003097842A publication Critical patent/JP2003097842A/en
Application granted granted Critical
Publication of JP3653261B2 publication Critical patent/JP3653261B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Abstract

PROBLEM TO BE SOLVED: To easily and selectively perform the dehumidifying operation for the purpose to get the temperature and humidity comfortable for people, and another dehumidifying operation for the purpose other than the above purpose. SOLUTION: This air-conditioner comprises a power-controllable compressor 1, an outdoor heat exchanger 3, an outdoor fan 10 capable of controlling its air blasting amount, a first indoor heat exchanger 6a, a second indoor heat exchanger 6b, a dehumidifying restrictor functioning as a restrictor 7 in dehumidifying operation, and an indoor fan 12 capable of controlling its capacity. Two dehumidifying operation modes are provided: a dehumidifying operation mode to get the comfortable temperature and humidity by controlling the compressor 1 and the outdoor fan, and having a function for setting the air capacity of the indoor fan; and a dehumidifying operation mode to dry washing by controlling the compressor 1 and the outdoor fan 10, and setting the air capacity of the indoor fan 12 to a predetermined high air capacity to allow the air flow to reach over a wide range. These dehumidifying modes are selectively set.

Description

【発明の詳細な説明】Detailed Description of the Invention

【０００１】[0001]

【産業上の利用分野】本発明は、空気調和機及びその運
転方法に係り、特に冷房気味から暖房気味にわたる広い
温度範囲で除湿運転が可能な空気調和機及びその運転方
法に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner and an operating method thereof, and more particularly to an air conditioner capable of dehumidifying operation in a wide temperature range ranging from cooling to heating and an operating method thereof.

【０００２】[0002]

【従来の技術】従来の空気調和機としては、湿度を下げ
るための除湿運転を行う際、主として蒸発器により冷却
された空気を電気ヒータにより再び加熱する方式のもの
や、冷凍サイクルの凝縮熱により再び加熱する方式のも
のが知られている。この２つの方式のものを特に省エネ
ルギ-の点から比較した場合、前者の方式のものは、消
費電力が非常に多くなるため、後者の方式のものの方が
優れている。2. Description of the Related Art Conventional air conditioners mainly use a system in which air cooled by an evaporator is heated again by an electric heater when a dehumidifying operation is performed, or a condensation heat in a refrigeration cycle is used. A method of heating again is known. When comparing the two methods, especially from the viewpoint of energy saving, the former method consumes much more power, and thus the latter method is superior.

【０００３】又、除湿運転時に冷却された空気を冷凍サ
イクル自身により再び加熱する冷凍サイクルの例とし
て、特開昭６０−１８１５５９号公報、特開平２−１８
３７７６号公報、特開平３−３１６４０号公報、及び実
開昭５１−１８０５９号公報に記載のものがある。Further, as an example of a refrigerating cycle in which the air cooled in the dehumidifying operation is heated again by the refrigerating cycle itself, JP-A-60-181559 and JP-A-2-18.
37376, JP-A-3-31640, and JP-A-51-18059.

【０００４】このうち特開昭６０−１８１５５９号公報
には、圧縮機、四方弁、室外熱交換器、絞り装置、室内
熱交換器等を順次冷媒配管で接続し、さらに室内熱交換
器を二分割してこれらの間に除湿運転用の除湿絞り装置
とこの除湿絞り装置をバイパスする二方弁とを並列に設
けたサイクル構成が開示されている。そして除湿運転時
には、前記二方弁を閉じて冷媒を除湿絞り装置に流すこ
とにより、二分割した室内熱交換器のうち上流側を凝縮
器、下流側を蒸発器とし、室内空気流をこの蒸発器から
凝縮器に流し、蒸発器で冷却・除湿した後、凝縮器で再
び加熱して温度をあまり下げずに湿度を下げる除湿運転
を可能にしている。In JP-A-60-181559, a compressor, a four-way valve, an outdoor heat exchanger, a throttling device, an indoor heat exchanger, etc. are successively connected by a refrigerant pipe, and an indoor heat exchanger is further connected. Disclosed is a cycle configuration in which a dehumidifying throttle device for dehumidifying operation and a two-way valve bypassing the dehumidifying throttle device are provided in parallel between them. During the dehumidifying operation, the two-way valve is closed to allow the refrigerant to flow through the dehumidifying expansion device, so that the upstream side of the indoor heat exchanger divided into two is a condenser and the downstream side is an evaporator. It allows the dehumidification operation to flow from the condenser to the condenser, cool and dehumidify with the evaporator, and then reheat with the condenser to lower the humidity without lowering the temperature too much.

【０００５】特開平２−１８３７７６号公報では、さら
に、除湿絞り装置として小孔付二方弁を用い、室内熱交
換器を上下に二分割したサイクル構成として、除湿運転
時に上側室内熱交換器を凝縮器、下側室内熱交換器を蒸
発器とし、さらに室内空気流をこれらの室内熱交換器に
並列に流し、蒸発器で冷却・除湿、凝縮器で加熱するこ
とにより、冷え過ぎを防止しながら湿度を下げる除湿運
転を可能にしている。Further, in Japanese Unexamined Patent Publication No. 2-183776, a two-way valve with a small hole is used as a dehumidifying expansion device, and the indoor heat exchanger is divided into upper and lower halves, and the upper indoor heat exchanger is operated during dehumidifying operation. The condenser and lower indoor heat exchanger are used as evaporators, and the indoor air flow is made to flow in parallel to these indoor heat exchangers to prevent overcooling by cooling and dehumidifying with the evaporator and heating with the condenser. However, it enables dehumidifying operation to lower the humidity.

【０００６】特開平３−３１６４０号公報では、前述の
特開昭６０−１８１５５９号公報のサイクル構成に加
え、さらに逆止弁４個からなる流路切替手段を設けて四
方弁を暖房サイクルに切換えた場合でも室内側で空気流
が蒸発器から加熱器に流れるようにして、強力な暖房気
味除湿運転が可能なサイクル構成にしている。又室外フ
ァンの回転数制御により室外熱交換器での放熱量をコン
トロールし、室温が設定温度になるように室内熱交換器
での空気加熱量を調節するようにしている。又公知例の
中に、室外ファンを、外気温度が２２℃以下で微弱運
転、２２℃以上で弱運転にすることが記載されている。In Japanese Patent Laid-Open No. 3-31640, in addition to the cycle configuration of Japanese Patent Laid-Open No. 60-181559, flow path switching means consisting of four check valves is further provided to switch the four-way valve to a heating cycle. Even in such a case, the air flow is made to flow from the evaporator to the heater on the indoor side so that a powerful heating-like dehumidifying operation is possible. In addition, the amount of heat radiated in the outdoor heat exchanger is controlled by controlling the rotation speed of the outdoor fan, and the amount of air heated in the indoor heat exchanger is adjusted so that the room temperature reaches the set temperature. In addition, in the publicly known example, it is described that the outdoor fan is operated weakly when the outside air temperature is 22 ° C. or less and weakly operated when the outside air temperature is 22 ° C. or more.

【０００７】実開昭５１−１８０５９号公報におけるサ
イクル構成を図３０に、各部の運転一覧を図３１に示
す。図３０のサイクル構成は、圧縮機を２台設けている
が、基本的には前述の特開昭６０−１８１５５９号公報
に記載のサイクル構成と同等である。図３１に示す運転
方法では、室外ファンや圧縮機は、運転機能に応じた制
御を行うが室外温度等に応じた制御は行っていない。例
えば、室外ファンは、冷房気味除湿運転では低速で、暖
房気味除湿運転では停止させる。又、圧縮機は除湿運転
時１台運転である。FIG. 30 shows a cycle configuration in Japanese Utility Model Laid-Open No. 51-18059, and FIG. 31 shows an operation list of each part. Although the cycle structure of FIG. 30 is provided with two compressors, it is basically the same as the cycle structure described in the above-mentioned JP-A-60-181559. In the operation method shown in FIG. 31, the outdoor fan and the compressor perform control according to the operation function, but do not perform control according to the outdoor temperature and the like. For example, the outdoor fan is operated at a low speed in the cooling dehumidifying operation and is stopped in the heating dehumidifying operation. In addition, the compressor operates at the time of dehumidifying operation.

【０００８】[0008]

【発明が解決しようとする課題】最近は、除湿運転を多
目的に使用するようになっている。例えば、（１）梅雨
や秋雨の季節で気温はそれほど高くないがじめじめする
時に、設定室温を保ちながら除湿を行う、快適除湿運
転、（２）蒸し暑い夜や明け方に気流感が無く低騒音状
態で、温度をあまり下げずに湿度を下げて快適な睡眠が
できるようにする、おやすみ・おめざめ除湿運転、
（３）相対湿度を５０％位に保ってカビやダニの繁殖を
防止する、カビ・ダニ防止除湿運転、（４）梅雨や秋雨
の季節で家の中に干した洗濯物を乾かす時に使用する、
ランドリー除湿運転等がある。しかし、前記の四つの公
知公報には、上記（１）〜（４）の使用目的に対する運
転方法については配慮されていない。Recently, the dehumidifying operation has been used for various purposes. For example, (1) In the rainy season and autumn rain season, when the temperature is not so high but dehumidification is performed, the dehumidification is performed while maintaining the set room temperature, (2) there is no airflow feeling on a hot and humid night or at dawn, and in a low noise state. , Good night sleep, dehumidifying operation, which allows you to sleep comfortably by lowering the humidity without lowering the temperature too much
(3) Relative humidity is kept at around 50% to prevent the growth of mold and mites, mold and mite prevention dehumidifying operation, (4) Used to dry the laundry hung in the house during the rainy season and autumn rain season. ,
There are laundry dehumidification operation etc. However, the above-mentioned four publicly-known publications do not consider the driving method for the purpose of use (1) to (4).

【０００９】なお特開平３−３１６４０号公報では、室
外ファンの回転数を制御して除湿運転における室内熱交
換器での空気加熱量を調整するようにしているが、圧縮
機の運転に関しては何も触れておらず、特に上記（１）
〜（４）の様な多くの使用目的に適用するためには不十
分である。又外気温度の対して、室外ファンを外気温度
が２２℃以下では微弱運転、２２℃以上では弱運転の二
段階に制御しているが、室外温度に対する制御としては
不十分である。In Japanese Patent Laid-Open No. 3-31640, the rotation speed of the outdoor fan is controlled to adjust the air heating amount in the indoor heat exchanger in the dehumidifying operation. I haven't even touched on it, especially (1) above
It is insufficient to be applied to many purposes such as ~ (4). Further, the outdoor fan is controlled in two steps, ie, a weak operation when the outside air temperature is 22 ° C. or less and a weak operation when the outside air temperature is 22 ° C. or more, but it is insufficient as a control for the outdoor temperature.

【００１０】又、空気調和機では、除湿運転の他に冷房
運転や暖房運転を行う場合が多いが、前述の四つの公知
公報に記載のように二分割した室内熱交換器を直列につ
なぐと、冷房運転や暖房運転では室内熱交換器の冷媒流
路が長くなり、特に２つの室内熱交換器を蒸発器として
使用する冷房運転において、室内熱交換器での冷媒流の
圧力損失が大きくなり、さらには空気流と冷媒流の流れ
が対向流にならなかったり、暖房運転時に十分なサブク
ールが取れなかったりすると、冷凍サイクルの性能が低
下してしまう。この場合、特開平２−１８３７７６号公
報には二分割した室内熱交換器のうちの少なくとも一方
の冷媒流路を二経路にして圧力損失が少なくなるように
しているが、まだ不十分である。その他の公知公報で
は、この問題に付いて特に触れていない。In addition, in an air conditioner, in many cases, a cooling operation and a heating operation are performed in addition to the dehumidifying operation. However, if two divided indoor heat exchangers are connected in series as described in the above-mentioned four known publications. In the cooling operation and the heating operation, the refrigerant flow path of the indoor heat exchanger becomes long, and especially in the cooling operation using the two indoor heat exchangers as the evaporator, the pressure loss of the refrigerant flow in the indoor heat exchanger becomes large. Moreover, if the air flow and the refrigerant flow do not become counter flows, or if sufficient subcooling cannot be obtained during the heating operation, the performance of the refrigeration cycle deteriorates. In this case, Japanese Patent Laid-Open No. 2-183776 discloses that at least one of the indoor heat exchangers divided into two has two refrigerant passages to reduce the pressure loss, but it is still insufficient. Other known publications do not specifically mention this problem.

【００１１】さらに、ルームエアコン等の小形の空気調
和器では、室内ユニット（室内機とも言う）の寸法に制
限があり、こうした制限された条件下において、室内熱
交換器の配管構成と空気流との関係等を工夫して、除
湿、冷房、暖房の各運転において室内熱交換器での伝熱
性能をできるだけ良くして冷凍サイクルの性能を十分高
く保つ必要がある。Further, in a small air conditioner such as a room air conditioner, the size of an indoor unit (also called an indoor unit) is limited, and under such restricted conditions, the piping structure of the indoor heat exchanger and the air flow are It is necessary to improve the heat transfer performance of the indoor heat exchanger as much as possible in each operation of dehumidification, cooling and heating to keep the performance of the refrigeration cycle sufficiently high by devising the relationship between the above.

【００１２】又さらに実開昭５１−１８０５９号公報で
は、暖房ぎみ除湿運転時、室外側ファンを停止させるた
め、室外ユニット（室外機ともいう）側の電気部品の温
度が高くなり寿命が短くなってしまう。又室外温度によ
って室外ファンを制御しないため、室外熱交換器からの
放熱量（廃熱量）が室外温度により変わり室内吹出空気
温度や除湿量を十分には制御できなかったり、圧縮機が
一定速で一台であるため、設定湿度と室内湿度の差によ
る除湿量制御が十分にはできない。Further, in Japanese Utility Model Laid-Open No. 51-18059, since the outdoor fan is stopped at the time of heating and dehumidifying operation, the temperature of the electric parts on the outdoor unit (also referred to as the outdoor unit) side becomes high and the life becomes short. Will end up. Also, because the outdoor fan is not controlled by the outdoor temperature, the amount of heat radiated from the outdoor heat exchanger (waste heat amount) changes depending on the outdoor temperature, and it is not possible to adequately control the indoor blown air temperature and dehumidification amount, or the compressor operates at a constant speed. Since there is only one unit, the dehumidification amount control based on the difference between the set humidity and the indoor humidity cannot be performed sufficiently.

【００１３】本発明の第一の目的は、人が快適に感じる
温湿度にする使用目的で用いる除湿運転と、これ以外の
使用目的で用いる他の除湿運転とを選択指定して容易に
行なうことができる空気調和機を提供することにある。
本発明の第二の目的は、冷房、暖房及び除湿運転の性能
を向上しつつ、人が快適に感じる温湿度にする使用目的
で用いる除湿運転と、これ以外の使用目的で用いる他の
除湿運転とを選択指定して容易に行なうことができる空
気調和機を提供することにある。A first object of the present invention is to easily perform a dehumidifying operation which is used for the purpose of making the temperature and humidity comfortable for humans and a dehumidifying operation which is used for other purposes. It is to provide an air conditioner capable of
A second object of the present invention is to improve the performance of cooling, heating and dehumidifying operation, and to use the dehumidifying operation for the purpose of use to make the temperature and humidity that people feel comfortable, and other dehumidifying operation for the purpose of use other than this. An object of the present invention is to provide an air conditioner that can be easily selected and designated.

【００１４】[0014]

【課題を解決するための手段】前記第一の目的を達成す
るために、本発明の空気調和機は、能力制御可能な圧縮
機と、室外熱交換器と、送風量制御が可能な室外ファン
と、第１室内熱交換器と、第２室内熱交換器と、除湿運
転時に絞り装置として機能する除湿絞り装置と、風量制
御可能な室内ファンとを備え、前記圧縮機、前記室外熱
交換器、前記第１室内熱交換器、前記除湿絞り装置、前
記第２室内熱交換器を順次管路によって接続された空気
調和機において、除湿運転モードとして、人が快適に感
じる温湿度の運転を実現するように前記圧縮機及び前記
室外ファンが制御され且つ前記室内ファンの風量を設定
する機能を有する除湿運転モードと、洗濯物を乾燥させ
る運転を実現するように前記圧縮機及び前記室外ファン
が制御され且つ前記室内ファンの風量を気流が広い範囲
にゆき渡るように予め設定された高風量とする除湿運転
モードとを備え、これら除湿運転モードの何れかを選択
指定する構成としたものである。前記第一の目的を達成
するために、本発明の空気調和機は、能力制御可能な圧
縮機と、室外熱交換器と、送風量制御が可能な室外ファ
ンと、第１室内熱交換器と、第２室内熱交換器と、除湿
運転時に絞り装置として機能する除湿絞り装置と、風量
制御可能な室内ファンとを備え、前記圧縮機、前記室外
熱交換器、前記第１室内熱交換器、前記除湿絞り装置、
前記第２室内熱交換器を順次管路によって接続された空
気調和機において、除湿運転モードとして、人が快適に
感じる温湿度の運転を実現するように前記圧縮機及び前
記室外ファンが制御され且つ前記室内ファンの風量を設
定する機能を有する除湿運転モードと、洗濯物を乾燥さ
せる運転を実現するように前記圧縮機及び前記室外ファ
ンが制御され且つ前記室内ファンの風量を気流が広い範
囲にゆき渡るように予め設定された高風量とし、この室
内ファンが高風量であっても除湿能力が得られる能力で
前記圧縮機を運転する除湿運転モードとを備え、これら
除湿運転モードの何れかを選択指定する構成としたもの
である。前記第一の目的を達成するために、本発明の空
気調和機は、能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、除
湿運転モードとして、人が快適に感じる温湿度の運転を
実現するように前記圧縮機及び前記室外ファンが制御さ
れ且つ前記室内ファンの風量を設定する機能を有する除
湿運転モードと、睡眠時に快適な環境となる運転を実現
するように前記圧縮機及び前記室外ファンが制御され且
つ前記室内ファンの風量を予め設定された低風量とする
除湿運転モードとを備え、これら除湿運転モードの何れ
かを選択指定する構成としたものである。前記第一の目
的を達成するために、本発明の空気調和機は、能力制御
可能な圧縮機と、室外熱交換器と、送風量制御が可能な
室外ファンと、第１室内熱交換器と、第２室内熱交換器
と、除湿運転時に絞り装置として機能する除湿絞り装置
と、風量制御可能な室内ファンとを備え、前記圧縮機、
前記室外熱交換器、前記第１室内熱交換器、前記除湿絞
り装置、前記第２室内熱交換器を順次管路によって接続
された空気調和機において、除湿運転モードとして、人
が快適に感じる温湿度の運転を実現するように前記圧縮
機及び前記室外ファンが制御され且つ前記室内ファンの
風量を設定する機能を有する除湿運転モードと、湿度が
４０％〜６０％となる運転を実現するように前記圧縮機
及び前記室外ファンが制御され且つ前記室内ファンの風
量を設定する機能を有する除湿運転モードとを備え、こ
れら除湿運転モードの何れかを選択指定する構成とした
ものである。前記第一の目的を達成するために、本発明
の空気調和機は、能力制御可能な圧縮機と、室外熱交換
器と、送風量制御が可能な室外ファンと、第１室内熱交
換器と、第２室内熱交換器と、除湿運転時に絞り装置と
して機能する除湿絞り装置と、風量制御可能な室内ファ
ンとを備え、前記圧縮機、前記室外熱交換器、前記第１
室内熱交換器、前記除湿絞り装置、前記第２室内熱交換
器を順次管路によって接続された空気調和機において、
除湿運転モードとして、人が快適に感じる温湿度の運転
を実現するように前記圧縮機及び前記室外ファンが制御
され且つ前記室内ファンの風量を設定する機能を有する
除湿運転モードと、洗濯物を乾燥させる運転を実現する
ように前記圧縮機及び前記室外ファンが制御され且つ前
記室内ファンの風量を気流が広い範囲にゆき渡るように
予め設定された高風量とする除湿運転モードと、睡眠時
に快適な環境となる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を予め設定された低風量とする除湿運転モードとを備
え、これら除湿運転モードの何れかを選択指定する構成
としたものである。前記第一の目的を達成するために、
本発明の空気調和機は、能力制御可能な圧縮機と、室外
熱交換器と、送風量制御が可能な室外ファンと、第１室
内熱交換器と、第２室内熱交換器と、除湿運転時に絞り
装置として機能する除湿絞り装置と、風量制御可能な室
内ファンとを備え、前記圧縮機、前記室外熱交換器、前
記第１室内熱交換器、前記除湿絞り装置、前記第２室内
熱交換器を順次管路によって接続された空気調和機にお
いて、除湿運転モードとして、人が快適に感じる温湿度
の運転を実現するように前記圧縮機及び前記室外ファン
が制御され且つ前記室内ファンの風量を設定する機能を
有する除湿運転モードと、洗濯物を乾燥させる運転を実
現するように前記圧縮機及び前記室外ファンが制御され
且つ前記室内ファンの風量を気流が広い範囲にゆき渡る
ように予め設定された高風量とし、この室内ファンが高
風量であっても除湿能力が得られる能力で前記圧縮機を
運転する除湿運転モードと、睡眠時に快適な環境となる
運転を実現するように前記圧縮機及び前記室外ファンが
制御され且つ前記室内ファンの風量を予め設定された低
風量とする除湿運転モードとを備え、これら除湿運転モ
ードの何れかを選択指定する構成としたものである。前
記第一の目的を達成するために、本発明の空気調和機
は、能力制御可能な圧縮機と、室外熱交換器と、送風量
制御が可能な室外ファンと、第１室内熱交換器と、第２
室内熱交換器と、除湿運転時に絞り装置として機能する
除湿絞り装置と、風量制御可能な室内ファンとを備え、
前記圧縮機、前記室外熱交換器、前記第１室内熱交換
器、前記除湿絞り装置、前記第２室内熱交換器を順次管
路によって接続された空気調和機において、除湿運転モ
ードとして、人が快適に感じる温湿度の運転を実現する
ように前記圧縮機及び前記室外ファンが制御され且つ前
記室内ファンの風量を設定する機能を有する除湿運転モ
ードと、洗濯物を乾燥させる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を気流が広い範囲にゆき渡るように予め設定さ
れた高風量とする除湿運転モードと、湿度が４０％〜６
０％となる運転を実現するように前記圧縮機及び前記室
外ファンが制御され且つ前記室内ファンの風量を設定す
る機能を有する除湿運転モードとを備え、これら除湿運
転モードの何れかを選択指定する構成としたものであ
る。前記第一の目的を達成するために、本発明の空気調
和機は、能力制御可能な圧縮機と、室外熱交換器と、送
風量制御が可能な室外ファンと、第１室内熱交換器と、
第２室内熱交換器と、除湿運転時に絞り装置として機能
する除湿絞り装置と、風量制御可能な室内ファンとを備
え、前記圧縮機、前記室外熱交換器、前記第１室内熱交
換器、前記除湿絞り装置、前記第２室内熱交換器を順次
管路によって接続された空気調和機において、除湿運転
モードとして、人が快適に感じる温湿度の運転を実現す
るように前記圧縮機及び前記室外ファンが制御され且つ
前記室内ファンの風量を設定する機能を有する除湿運転
モードと、洗濯物を乾燥させる運転を実現するように前
記圧縮機及び前記室外ファンが制御され且つ前記室内フ
ァンの風量を気流が広い範囲にゆき渡るように予め設定
された高風量とし、この室内ファンが高風量であっても
除湿能力が得られる能力で前記圧縮機を運転する除湿運
転モードと、湿度が４０％〜６０％となる運転を実現す
るように前記圧縮機及び前記室外ファンが制御され且つ
前記室内ファンの風量を設定する機能を有する除湿運転
モードとを備え、これら除湿運転モードの何れかを選択
指定する構成としたものである。前記第一の目的を達成
するために、本発明の空気調和機は、能力制御可能な圧
縮機と、室外熱交換器と、送風量制御が可能な室外ファ
ンと、第１室内熱交換器と、第２室内熱交換器と、除湿
運転時に絞り装置として機能する除湿絞り装置と、風量
制御可能な室内ファンとを備え、前記圧縮機、前記室外
熱交換器、前記第１室内熱交換器、前記除湿絞り装置、
前記第２室内熱交換器を順次管路によって接続された空
気調和機において、除湿運転モードとして、人が快適に
感じる温湿度の運転を実現するように前記圧縮機及び前
記室外ファンが制御され且つ前記室内ファンの風量を設
定する機能を有する除湿運転モードと、洗濯物を乾燥さ
せる運転を実現するように前記圧縮機及び前記室外ファ
ンが制御され且つ前記室内ファンの風量を気流が広い範
囲にゆき渡るように予め設定された高風量とする除湿運
転モードと、睡眠時に快適な環境となる運転を実現する
ように前記圧縮機及び前記室外ファンが制御され且つ前
記室内ファンの風量を予め設定された低風量とする除湿
運転モードと、湿度が４０％〜６０％となる運転を実現
するように前記圧縮機及び前記室外ファンが制御され且
つ前記室内ファンの風量を設定する機能を有する除湿運
転モードとを備え、これら除湿運転モードの何れかを選
択指定する構成としたものである。前記第一の目的を達
成するために、本発明の空気調和機は、能力制御可能な
圧縮機と、室外熱交換器と、送風量制御が可能な室外フ
ァンと、第１室内熱交換器と、第２室内熱交換器と、除
湿運転時に絞り装置として機能する除湿絞り装置と、風
量制御可能な室内ファンとを備え、前記圧縮機、前記室
外熱交換器、前記第１室内熱交換器、前記除湿絞り装
置、前記第２室内熱交換器を順次管路によって接続され
た空気調和機において、除湿運転モードとして、人が快
適に感じる温湿度の運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を設定する機能を有する除湿運転モードと、洗濯物を乾
燥させる運転を実現するように前記圧縮機及び前記室外
ファンが制御され且つ前記室内ファンの風量を気流が広
い範囲にゆき渡るように予め設定された高風量とし、こ
の室内ファンが高風量であっても除湿能力が得られる能
力で前記圧縮機を運転する除湿運転モードと、睡眠時に
快適な環境となる運転を実現するように前記圧縮機及び
前記室外ファンが制御され且つ前記室内ファンの風量を
予め設定された低風量とする除湿運転モードと、湿度が
４０％〜６０％となる運転を実現するように前記圧縮機
及び前記室外ファンが制御され且つ前記室内ファンの風
量を設定する機能を有する除湿運転モードとを備え、こ
れら除湿運転モードの何れかを選択指定する構成とした
ものである。前記第二の目的を達成するために、本発明
の空気調和機は、能力制御可能な圧縮機と、室外熱交換
器と、送風量制御が可能な室外ファンと、第１室内熱交
換器及び第２室内熱交換器を有する室内熱交換器と、除
湿運転時に絞り装置として機能する除湿絞り装置と、風
量制御可能な室内ファンとを備え、除湿運転時に前記圧
縮機、前記室外熱交換器、前記第１室内熱交換器、前記
除湿絞り装置、前記第２室内熱交換器の順に接続され、
冷房運転時に前記圧縮機、前記室外熱交換器、前記第１
室内熱交換器、前記第２室内熱交換器の順に接続され、
暖房運転時に前記圧縮機、前記第２室内熱交換器、前記
第１室内熱交換器、前記室外熱交換器の順に接続される
空気調和機において、前記第１室内熱交換器及び前記第
２室内熱交換器のそれぞれの冷媒流路を二系統以上に分
けて構成すると共に、一方の前記室内熱交換器の冷媒流
路の合流点と他方の前記室内熱交換器の冷媒流路の分岐
点との間に前記除湿絞り装置を接続し、暖房運転時に下
流側となる方の前記室内熱交換器の出口側を一系統の冷
媒流路で構成し、除湿運転モードとして、人が快適に感
じる温湿度の運転を実現するように前記圧縮機及び前記
室外ファンが制御され且つ前記室内ファンの風量を設定
する機能を有する除湿運転モードと、睡眠時に快適な環
境となる運転を実現するように前記圧縮機及び前記室外
ファンが制御され且つ前記室内ファンの風量を予め設定
された低風量とする除湿運転モードとを備え、これら除
湿運転モードの何れかを選択指定する構成としたもので
ある。前記第二の目的を達成するために、能力制御可能
な圧縮機と、室外熱交換器と、送風量制御が可能な室外
ファンと、第１室内熱交換器及び第２室内熱交換器を有
する室内熱交換器と、除湿運転時に絞り装置として機能
する除湿絞り装置と、風量制御可能な室内ファンとを備
え、除湿運転時に前記圧縮機、前記室外熱交換器、前記
第１室内熱交換器、前記除湿絞り装置、前記第２室内熱
交換器の順に接続され、冷房運転時に前記圧縮機、前記
室外熱交換器、前記第１室内熱交換器、前記第２室内熱
交換器の順に接続され、暖房運転時に前記圧縮機、前記
第２室内熱交換器、前記第１室内熱交換器、前記室外熱
交換器の順に接続される空気調和機において、前記第１
室内熱交換器及び前記第２室内熱交換器のそれぞれの冷
媒流路を二系統以上に分けて構成すると共に、一方の前
記室内熱交換器の冷媒流路の合流点と他方の前記室内熱
交換器の冷媒流路の分岐点との間に前記除湿絞り装置を
接続し、暖房運転時に下流側となる方の前記室内熱交換
器の出口側を一系統の冷媒流路で構成し、除湿運転モー
ドとして、人が快適に感じる温湿度の運転を実現するよ
うに前記圧縮機及び前記室外ファンが制御され且つ前記
室内ファンの風量を設定する機能を有する除湿運転モー
ドと、洗濯物を乾燥させる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を気流が広い範囲にゆき渡るように予め設定され
た高風量とする除湿運転モードとを備え、睡眠時に快適
な環境となる運転を実現するように前記圧縮機及び前記
室外ファンが制御され且つ前記室内ファンの風量を予め
設定された低風量とする除湿運転モードとを備え、これ
ら除湿運転モードの何れかを選択指定する構成としたも
のである。In order to achieve the first object, the air conditioner of the present invention is a compressor capable of controlling the capacity, an outdoor heat exchanger, and an outdoor fan capable of controlling the air flow rate. A first indoor heat exchanger, a second indoor heat exchanger, a dehumidifying expansion device functioning as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume, the compressor, the outdoor heat exchanger In the air conditioner in which the first indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchanger are sequentially connected by a pipe line, a dehumidifying operation mode is realized to realize operation of temperature and humidity that a person feels comfortable. The compressor and the outdoor fan are controlled so as to realize a dehumidifying operation mode having a function of setting the air volume of the indoor fan and an operation of drying the laundry. And before It includes a wind of the indoor fan and the drying mode and the high air volume that is set in advance so Yukiwataru a wide range of air flow is obtained by a structure for designating selected one of these drying mode. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan that can control the air volume, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, The dehumidifying squeezing device,
In an air conditioner in which the second indoor heat exchanger is sequentially connected by a pipeline, the compressor and the outdoor fan are controlled so that a dehumidifying operation mode is realized and operation of temperature and humidity that a person feels comfortable is realized. The compressor and the outdoor fan are controlled so that the dehumidifying operation mode having a function of setting the air volume of the indoor fan and the operation of drying the laundry are realized, and the air volume of the indoor fan is spread over a wide range. It has a preset high air flow rate so that even if this indoor fan has a high air flow rate, it has a dehumidification operation mode in which the compressor is operated with the ability to obtain dehumidification capacity, and one of these dehumidification operation modes is selected. The configuration is specified. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan that can control the air volume, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, In an air conditioner in which the dehumidifying expansion device and the second indoor heat exchanger are sequentially connected by a pipeline, the compressor and the outdoor unit are set in a dehumidifying operation mode so as to realize a temperature and humidity operation that a person feels comfortable. A dehumidifying operation mode in which a fan is controlled and a function of setting the air volume of the indoor fan, and the compressor and the outdoor fan are controlled so as to realize an operation that provides a comfortable environment during sleep, and the air volume of the indoor fan is controlled. Pre And a dehumidifying operation mode and set low air volume, in which a structure for designating selected one of these drying mode. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan whose air volume can be controlled,
In an air conditioner in which the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchanger are sequentially connected by a pipeline, a dehumidifying operation mode is set to a temperature that a person feels comfortable. To realize a dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize a humidity operation and which has a function of setting the air volume of the indoor fan, and an operation in which the humidity is 40% to 60%. The compressor and the outdoor fan are controlled, and a dehumidifying operation mode having a function of setting the air volume of the indoor fan is provided, and any one of these dehumidifying operation modes is selected and designated. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume, the compressor, the outdoor heat exchanger, and the first
An air conditioner in which an indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchanger are sequentially connected by a pipeline,
As the dehumidifying operation mode, a dehumidifying operation mode having a function of controlling the compressor and the outdoor fan and setting an air volume of the indoor fan so as to realize a comfortable temperature and humidity operation for a person, and drying laundry The compressor and the outdoor fan are controlled so as to realize the operation to be performed, and the dehumidifying operation mode in which the air volume of the indoor fan is set to a high air volume set in advance so that the airflow spreads over a wide range, and comfortable during sleep The compressor and the outdoor fan are controlled so as to realize an environmental operation, and a dehumidification operation mode in which the air volume of the indoor fan is set to a preset low air volume is provided, and one of these dehumidification operation modes is selected. The configuration is specified. In order to achieve the first purpose,
The air conditioner of the present invention includes a compressor whose capacity can be controlled, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a dehumidifying operation. The compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchange are equipped with a dehumidifying expansion device that sometimes functions as an expansion device and an indoor fan whose air volume can be controlled. In the air conditioner in which the compressors are sequentially connected by a pipeline, the compressor and the outdoor fan are controlled so as to realize a temperature and humidity operation that a person feels comfortable as a dehumidifying operation mode, and the air volume of the indoor fan is controlled. The compressor and the outdoor fan are controlled so as to realize a dehumidifying operation mode having a setting function and an operation for drying the laundry, and the air volume of the indoor fan is preset so as to spread the airflow over a wide range. With a high air flow rate, the dehumidification operation mode in which the compressor is operated with the ability to obtain dehumidification capacity even when the indoor fan has a high air flow rate, and the compressor and the compressor are provided so as to realize an operation in a comfortable environment during sleep. A dehumidifying operation mode in which the outdoor fan is controlled and the air volume of the indoor fan is set to a preset low air volume is provided, and any one of these dehumidifying operation modes is selected and designated. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. , Second
An indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume,
In the air conditioner in which the compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchanger are sequentially connected by a pipeline, the dehumidifying operation mode is To realize a dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize comfortable temperature and humidity operation and a function of setting the air volume of the indoor fan, and an operation for drying laundry are realized. A dehumidifying operation mode in which the compressor and the outdoor fan are controlled and the air volume of the indoor fan is set to a high air volume set in advance so that the air flow spreads over a wide range, and the humidity is 40% to 6%.
A dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize an operation of 0% and a function of setting the air volume of the indoor fan is provided, and any one of these dehumidifying operation modes is selected and designated. It is configured. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. ,
A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, and the In an air conditioner in which a dehumidifying expansion device and the second indoor heat exchanger are sequentially connected by a pipeline, the compressor and the outdoor fan are set in a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. Is controlled and the dehumidifying operation mode having a function of setting the air volume of the indoor fan and the compressor and the outdoor fan are controlled so as to realize the operation of drying the laundry, and the air volume of the indoor fan is controlled by the air flow. With a high air volume preset to spread over a wide range, a dehumidification operation mode in which the compressor is operated with the ability to obtain dehumidification ability even if this indoor fan has a high air volume, and humidity. A dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize an operation of 40% to 60% and a function of setting the air volume of the indoor fan is provided, and one of these dehumidifying operation modes is provided. It is configured to be selected and designated. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan that can control the air volume, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, The dehumidifying squeezing device,
In an air conditioner in which the second indoor heat exchanger is sequentially connected by a pipeline, the compressor and the outdoor fan are controlled so that a dehumidifying operation mode is realized and operation of temperature and humidity that a person feels comfortable is realized. The compressor and the outdoor fan are controlled so that the dehumidifying operation mode having a function of setting the air volume of the indoor fan and the operation of drying the laundry are realized, and the air volume of the indoor fan is spread over a wide range. The compressor and the outdoor fan are controlled so as to realize a dehumidifying operation mode in which a high air flow rate is preset to cross and a comfortable environment during sleep, and the air flow rate of the indoor fan is preset. The compressor and the outdoor fan are controlled so as to realize a dehumidifying operation mode in which the air volume is low and an operation in which the humidity is 40% to 60%, and the indoor fan And a drying mode having a function of setting the air volume, is obtained by a structure for designating selected one of these drying mode. In order to achieve the first object, an air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, and a first indoor heat exchanger. A second indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan that can control the air volume, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, In an air conditioner in which the dehumidifying expansion device and the second indoor heat exchanger are sequentially connected by a pipeline, the compressor and the outdoor unit are set in a dehumidifying operation mode so as to realize a temperature and humidity operation that a person feels comfortable. The compressor and the outdoor fan are controlled to realize a dehumidifying operation mode in which a fan is controlled and a function of setting the air volume of the indoor fan and an operation of drying the laundry are realized, and the air volume of the indoor fan is made to flow. Wide With a high air flow rate preset to spread over the range, a dehumidification operation mode in which the compressor is operated with the ability to obtain dehumidification capacity even when this indoor fan has a high air flow rate, and an operation that provides a comfortable environment during sleep In order to realize the above, the compressor and the outdoor fan are controlled, and a dehumidifying operation mode in which the air volume of the indoor fan is set to a preset low air volume and an operation in which the humidity is 40% to 60% are realized. The compressor and the outdoor fan are controlled, and a dehumidifying operation mode having a function of setting the air volume of the indoor fan is provided, and any one of these dehumidifying operation modes is selected and designated. In order to achieve the second object, the air conditioner of the present invention includes a compressor capable of controlling a capacity, an outdoor heat exchanger, an outdoor fan capable of controlling an air flow rate, a first indoor heat exchanger, and An indoor heat exchanger having a second indoor heat exchanger, a dehumidifying expansion device functioning as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume, and the compressor, the outdoor heat exchanger during dehumidification operation, The first indoor heat exchanger, the dehumidifying expansion device, and the second indoor heat exchanger are connected in this order,
During the cooling operation, the compressor, the outdoor heat exchanger, the first
The indoor heat exchanger and the second indoor heat exchanger are connected in this order,
In the air conditioner in which the compressor, the second indoor heat exchanger, the first indoor heat exchanger, and the outdoor heat exchanger are connected in this order during heating operation, the first indoor heat exchanger and the second indoor Each refrigerant flow path of the heat exchanger is divided into two or more systems and configured, and the confluence of the refrigerant flow path of the one indoor heat exchanger and the branch point of the refrigerant flow path of the other indoor heat exchanger. The dehumidifying expansion device is connected between the two, and the outlet side of the indoor heat exchanger, which is the downstream side during the heating operation, is configured with a refrigerant flow path of one system, and as a dehumidifying operation mode, a temperature that a person feels comfortable The dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize the operation at the humidity and the function of setting the air volume of the indoor fan, and the compression so as to realize the operation in a comfortable environment during sleep Machine and the outdoor fan are controlled One said a dehumidifying operation mode and a low air volume which is previously set the air volume of the indoor fan, in which a structure for designating selected one of these drying mode. In order to achieve the second object, it has a compressor whose capacity can be controlled, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger and a second indoor heat exchanger. An indoor heat exchanger, a dehumidifying expansion device that functions as a expansion device during dehumidification operation, and an indoor fan capable of controlling the air volume, and the compressor, the outdoor heat exchanger, and the first indoor heat exchanger during dehumidification operation, The dehumidifying expansion device and the second indoor heat exchanger are connected in this order, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger are connected in this order during cooling operation, In the air conditioner in which the compressor, the second indoor heat exchanger, the first indoor heat exchanger, and the outdoor heat exchanger are connected in this order during heating operation, the first
The respective refrigerant flow paths of the indoor heat exchanger and the second indoor heat exchanger are configured by being divided into two or more systems, and the confluence of the refrigerant flow paths of the one indoor heat exchanger and the other indoor heat exchange The dehumidifying expansion device is connected between the branch point of the refrigerant flow path of the heat exchanger, and the outlet side of the indoor heat exchanger, which is the downstream side during the heating operation, is configured with a single-system refrigerant flow path, and the dehumidifying operation is performed. As a mode, a dehumidifying operation mode having a function of controlling the compressor and the outdoor fan and setting an air volume of the indoor fan so as to realize a temperature and humidity operation that a person feels comfortable, and an operation of drying laundry The compressor and the outdoor fan are controlled so as to realize a dehumidifying operation mode in which the air volume of the indoor fan is set to a high air volume preset so that the air flow spreads over a wide range, and comfortable during sleep. Driving to become an environment The compressor and the outdoor fan are controlled so as to be realized, and a dehumidifying operation mode in which the air volume of the indoor fan is set to a preset low air volume is provided, and one of these dehumidifying operation modes is selectively designated. It is a thing.

【作用】上述した第一の目的を達成するための本発明の
空気調和機によれば、人が快適に感じる温湿度の運転を
実現するように圧縮機及び室外ファンが制御され且つ室
内ファンの風量を設定する機能を有する除湿運転モード
と、洗濯物を乾燥させる運転を実現するように圧縮機及
び室外ファンが制御され且つ室内ファンの風量を気流が
広い範囲にゆき渡るように予め設定された高風量とする
除湿運転モードとの何れかを選択指定するように構成し
ているので、除湿運転の利用範囲を拡大することができ
る。上述した本発明の第二の目的を達成するための本発
明の空気調和機によれば、第１室内熱交換器及び第２室
内熱交換器のそれぞれの冷媒流路を二系統以上に分けて
構成すると共に、室内熱交換器の一方の冷媒流路の合流
点と室内熱交換器の他方の冷媒流路の分岐点との間に除
湿絞り装置を接続することを加えているので、冷房、暖
房及び除湿運転における各室内熱交換器での冷媒流圧力
損失を低減することができる。さらには、暖房運転時に
下流側となる方の前記室内熱交換器の出口側を一系統の
冷媒流路で構成しているので、暖房運転時には、二系統
以上の冷媒流路の部分で凝縮した液冷媒流が一系統の冷
媒流路に入って高速となり、管内熱伝達率が高くなるこ
とにより、サブクールが十分に取れて熱交換効率を向上
することができる。また、冷房運転時には、一系統の冷
媒流路の部分に乾き度の低い冷媒が流れるため圧力損失
の増大が抑えられる。一方、この部分での冷媒の流速が
速くなることから管内熱伝達率が高くなって伝熱性能を
向上できる。According to the air conditioner of the present invention for achieving the above-mentioned first object, the compressor and the outdoor fan are controlled and the indoor fan of the indoor fan is controlled so as to realize the operation of the temperature and humidity that a person feels comfortable. The dehumidifying operation mode that has the function of setting the air volume and the compressor and the outdoor fan are controlled to realize the operation of drying the laundry, and the air volume of the indoor fan is preset to spread the airflow over a wide range. Since it is configured to selectively specify one of the dehumidifying operation modes in which the air volume is high, it is possible to expand the use range of the dehumidifying operation. According to the air conditioner of the present invention for achieving the above-mentioned second object of the present invention, the respective refrigerant flow paths of the first indoor heat exchanger and the second indoor heat exchanger are divided into two or more systems. With the configuration, since it is added to connect the dehumidifying expansion device between the confluence of one refrigerant flow path of the indoor heat exchanger and the branch point of the other refrigerant flow path of the indoor heat exchanger, cooling, It is possible to reduce the refrigerant flow pressure loss in each indoor heat exchanger in the heating and dehumidifying operations. Furthermore, since the outlet side of the indoor heat exchanger, which is the downstream side during heating operation, is configured with a single-system refrigerant flow path, during heating operation, condensation occurs in the two or more systems of refrigerant flow paths. Since the liquid refrigerant flow enters the single-system refrigerant flow path to have a high speed and a high heat transfer coefficient in the pipe, a sufficient subcool can be obtained and heat exchange efficiency can be improved. Further, during the cooling operation, the refrigerant having a low degree of dryness flows in the portion of the refrigerant flow path of one system, so that an increase in pressure loss can be suppressed. On the other hand, since the flow velocity of the refrigerant in this portion is increased, the heat transfer coefficient in the tube is increased and the heat transfer performance can be improved.

【００１５】[0015]

【実施例】以下、本発明の各実施例を建家に取り付ける
空気調和機を例にとり、図面により詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, each embodiment of the present invention will be described in detail with reference to the drawings by taking an air conditioner attached to a building as an example.

【００１６】本発明による一実施例を図１から図４によ
り説明する。図１は本実施例である冷凍サイクルと制御
の系統を示す図、図２は運転モードの流れ図、図３は低
風量の除湿運転での運転方法の流れ図、図４は高風量の
除湿運転方法の流れ図である。 本実施例の空気調和機
は次のように構成されている。図１において、１は圧縮
機、２は冷房や暖房等の運転状態を切り換える際に切り
換えられる四方弁、３は室外熱交換器、４は冷房運転及
び暖房運転時に冷媒が流れる主絞り装置、５は主絞り装
置４と並列に設けられ除湿運転時に冷媒を流すための二
方弁、６ａ、６ｂは二分割された室内熱交換器、７は室
内熱交換器６ａと６ｂとの間にこれらと直列に設けられ
除湿運転時に冷媒の流れる除湿絞り装置、８は室内熱交
換器６ａと６ｂとの間に除湿絞り装置７と並列に設けら
れ冷房及び暖房運転時に冷媒を流すための二方弁、９は
圧縮機への液戻りを防止するためのアキュムレータ、１
０は室外ファン、１１は室外ファンモータ、１２は室内
ファン、１３は室内ファンモータ、１４、１５はそれぞ
れ室外、室内の風向を示す矢印、１６は制御部、１７は
室内温度を検知する温度センサ等の温度検出手段、１８
は室内湿度を検知する湿度センサ等の湿度検出手段、２
１、２２、２３、２４、２５はそれぞれ配線を示してい
る。また、圧縮機１は、能力制御が可能で、室外ファン
１０及び室内ファン１２は能力制御すなわち送風量制御
が可能にしてある。特に最近は、圧縮機１やファンモー
タ１１、１３には、回転数が連続して変えられる回転数
制御方式が用いられており、能力をきめ細かく制御する
ことができる。An embodiment according to the present invention will be described with reference to FIGS. FIG. 1 is a diagram showing a refrigeration cycle and a control system according to the present embodiment, FIG. 2 is a flow chart of an operation mode, FIG. 3 is a flow chart of an operation method in a dehumidifying operation with a low air volume, and FIG. 4 is a dehumidifying operation method with a high air volume. 2 is a flowchart of. The air conditioner of this embodiment is configured as follows. In FIG. 1, 1 is a compressor, 2 is a four-way valve that is switched when switching operating states such as cooling and heating, 3 is an outdoor heat exchanger, 4 is a main expansion device through which a refrigerant flows during cooling and heating operations, 5 Is a two-way valve that is provided in parallel with the main expansion device 4 for flowing the refrigerant during the dehumidifying operation, 6a and 6b are indoor heat exchangers divided into two, and 7 is between the indoor heat exchangers 6a and 6b. A dehumidifying throttle device which is provided in series and through which the refrigerant flows during the dehumidifying operation, and 8 is a two-way valve which is provided in parallel with the dehumidifying throttle device 7 between the indoor heat exchangers 6a and 6b and which allows the refrigerant to flow during the cooling and heating operations, 9 is an accumulator for preventing liquid from returning to the compressor, 1
Reference numeral 0 is an outdoor fan, 11 is an outdoor fan motor, 12 is an indoor fan, 13 is an indoor fan motor, 14 and 15 are outdoor and arrows indicating the wind direction in the room, 16 is a control unit, and 17 is a temperature sensor for detecting the indoor temperature. Temperature detecting means such as 18
Is a humidity detecting means such as a humidity sensor for detecting indoor humidity, 2
Reference numerals 1, 22, 23, 24, and 25 denote wirings, respectively. Further, the compressor 1 is capable of capacity control, and the outdoor fan 10 and the indoor fan 12 are capable of capacity control, that is, air flow rate control. In particular, recently, the compressor 1 and the fan motors 11 and 13 use a rotation speed control method in which the rotation speed can be continuously changed, and the performance can be finely controlled.

【００１７】以上のようなサイクル構成において、冷房
運転時には、二方弁５を閉じ二方弁８を開くことによ
り、冷媒を実線の矢印で示すように循環させ、室外熱交
換器３を凝縮器、室内熱交換器６ａ及び６ｂを蒸発器と
して室内の冷房を行う。暖房運転時には、四方弁２を切
り替え二方弁５を閉じ二方弁８を開くことにより、冷媒
を破線の矢印で示すように循環させ、室内熱交換器６ａ
及び６ｂを凝縮器、室外熱交換器３を蒸発器として室内
の暖房を行う。In the above-described cycle structure, during cooling operation, the two-way valve 5 is closed and the two-way valve 8 is opened to circulate the refrigerant as shown by the solid line arrow, and the outdoor heat exchanger 3 is connected to the condenser. The indoor heat exchangers 6a and 6b are used as evaporators to cool the room. During the heating operation, the four-way valve 2 is switched, the two-way valve 5 is closed, and the two-way valve 8 is opened to circulate the refrigerant as indicated by a dashed arrow, thereby allowing the indoor heat exchanger 6a to circulate.
And 6b are used as condensers and the outdoor heat exchanger 3 is used as an evaporator to heat the room.

【００１８】又、除湿運転時には、四方弁２を冷房運転
時と同様に切り換え、二方弁５を開き二方弁８を閉じる
ことにより、冷媒を一点鎖線で示すように圧縮機１、四
方弁２、室外熱交換器３、二方弁５、室内熱交換器６
ａ、除湿絞り装置７、室内熱交換器６ｂ、四方弁２、ア
キュムレータ９、圧縮機１の順に循環させ、室外熱交換
器３を上流側の凝縮器、室内熱交換器６ａを下流側の凝
縮器、室内熱交換器６ｂを蒸発器とするように設定す
る。そして、室内空気を室内ファン１２により矢印１５
で示すように流すと、空気は蒸発器として作用する室内
熱交換器６ｂで冷却・除湿された後、下流側の凝縮器、
すなわち加熱器となる室内熱交換器６ａで再び加熱され
て室内に吹き出される。この場合、さらに圧縮機１の能
力や室内ファン１２及び室外ファン１０の送風能力を制
御することにより、蒸発器６ｂ及び加熱器６ａの能力を
調節することができ、最終的には除湿量や吹き出し空気
温度を使用目的に合わせて制御することができる。In the dehumidifying operation, the four-way valve 2 is switched in the same manner as in the cooling operation, the two-way valve 5 is opened and the two-way valve 8 is closed, so that the refrigerant is compressed by the compressor 1 and the four-way valve as shown by the one-dot chain line. 2, outdoor heat exchanger 3, two-way valve 5, indoor heat exchanger 6
a, the dehumidifying expansion device 7, the indoor heat exchanger 6b, the four-way valve 2, the accumulator 9, and the compressor 1 are circulated in this order, the outdoor heat exchanger 3 is an upstream condenser, and the indoor heat exchanger 6a is a downstream condenser. The device and the indoor heat exchanger 6b are set to be an evaporator. Then, the indoor air is directed by the indoor fan 12 to the arrow 15
, The air is cooled and dehumidified by the indoor heat exchanger 6b acting as an evaporator, and then the condenser on the downstream side,
That is, it is heated again by the indoor heat exchanger 6a serving as a heater and blown out into the room. In this case, the capacities of the evaporator 6b and the heater 6a can be adjusted by further controlling the capacities of the compressor 1 and the blowing capacities of the indoor fan 12 and the outdoor fan 10, and finally the dehumidifying amount and the blowing amount. The air temperature can be controlled according to the purpose of use.

【００１９】ところで、上記したように最近は除湿運転
を多目的に使用するようになっている。例えば、（１）
梅雨や秋雨の季節等で気温はそれほど高くないが、じめ
じめする時に設定温度を保ちながら除湿をおこなういわ
ゆる快適除湿運転、（２）蒸し暑い夜や明け方に気流感
がなく、低騒音状態で温度を余り下げずに湿度を下げて
快適な睡眠ができるようにする、おやすみ・おめざめ除
湿運転、（３）相対湿度を５０％位に保ってカビやダニ
の繁殖を防止する、いわゆるカビ・ダニ防止の除湿運
転、さらには（４）梅雨や秋雨の季節等で家の中に干し
た洗濯物を乾かす時に使用する、いわゆるランドリー除
湿運転、等がある。By the way, as described above, the dehumidifying operation has recently been used for multiple purposes. For example, (1)
The temperature is not so high due to the rainy season and autumn rain, etc., but the so-called comfortable dehumidifying operation that dehumidifies while maintaining the set temperature when damp, (2) There is no airflow feeling on a hot and humid night or at dawn, and the temperature is low in a low noise state. To reduce the humidity without lowering it so that you can sleep comfortably, good night / wake good dehumidifying operation, (3) Keep relative humidity at around 50% to prevent the growth of mold and mites, so-called mold / mite prevention There are also dehumidification operation, and (4) so-called laundry dehumidification operation, which is used when drying the laundry dried in the house in the rainy season or autumn rain season.

【００２０】又、上記した種々の使用目的の除湿運転に
おける圧縮機や室内ファン、室外ファンの運転状態につ
いて考えてみると、おやすみ・おめざめ除湿運転では、
特に気流感がなく低騒音で除湿量の多い低風量除湿運転
が必要であり、ランドリー除湿運転では、特に気流が広
い範囲まで届きしかも乾燥能力の高い高風量除湿運転が
必要である。快適除湿運転やカビ・ダニ防止除湿運転で
は、前記した低風量での除湿運転や高風量での除湿運転
を適当に使い分ける必要がある。また、低風量の除湿運
転や高風量の除湿運転に対して、さらに室温に応じて冷
房気味、等温気味あるいは暖房気味の運転を行う必要が
ある。Further, considering the operating states of the compressor, the indoor fan, and the outdoor fan in the dehumidifying operation for the various purposes described above, in the good night / awakening dehumidifying operation,
In particular, a low air volume dehumidifying operation that does not have a feeling of air flow and has a low noise and a large dehumidifying amount is required. In the laundry dehumidifying operation, a high air amount dehumidifying operation that allows a particularly large airflow and has a high drying capacity is required. In the comfortable dehumidifying operation and the mold / mite preventing dehumidifying operation, it is necessary to properly use the above-described dehumidifying operation with a low air flow and dehumidifying operation with a high air flow. Further, in addition to the dehumidifying operation with a low air volume and the dehumidifying operation with a high air volume, it is necessary to further perform a cooling-like, isothermal-like, or heating-like operation depending on the room temperature.

【００２１】以上述べた種々の使用目的の除湿運転方法
について、以下に運転モードの流れ図である図２に基づ
いて説明する。図２に示すように、強制運転あるいは室
内外の温湿度を検知した自動運転などにより除湿運転開
始（２００）の指示がでると、除湿運転における使用モ
ードの選択（２０１）が行われ、この選択に基づいて快
適な除湿運転（２１０）、カビ・ダニ防止の除湿運転
（２２０）、おやすみ・おめざめ除湿運転（２３０）、
ランドリー除湿運転（２４０）等のうちの１つが選択さ
れる。この時、選択モードの指定がないときには、自動
的に快適な除湿運転（２１０）のモードが選択される。The dehumidifying operation methods for various purposes described above will be described below with reference to FIG. 2 which is a flow chart of the operation modes. As shown in FIG. 2, when an instruction to start the dehumidifying operation (200) is issued by a forced operation or an automatic operation that detects the temperature and humidity inside and outside the room, a use mode selection (201) in the dehumidifying operation is performed. Dehumidifying operation (210), mildew / mite prevention dehumidifying operation (220), good night / wake up dehumidifying operation (230),
One of the laundry dehumidifying operation (240) and the like is selected. At this time, when the selection mode is not designated, a comfortable dehumidifying operation (210) mode is automatically selected.

【００２２】まず、快適除湿運転（２１０）では、温度
センサ１７、湿度センサ１８により室内空気の温湿度の
検出（２１１）、希望する室内温湿度の設定（２１２）
が行われる。次に低風量で除湿運転を行うかあるいは高
風量で除湿運転を行うかの室内ファン１２の送風状態の
設定（２１３）が行われ、この設定（２１３）に基づい
て低風量除湿運転（２１４）または高風量除湿運転（２
１５）が選択される。また、快適除湿運転を行う場合、
室内の温湿度は人が快適に感じるように設定する必要が
あるが、ＰＭＶ（Ｐｒｅｄｉｃｔｅｄ Ｍｅａｎ Ｖｏ
ｔｅの略で予測平均申告を意味する）等の温熱環境評価
指標に基づいて制御するようになっており、この温熱環
境評価指標に基づいて制御される場合には、室内の気温
や湿度だけでなく輻射温度、風速、着衣量、活動量も考
慮して温冷感の快適条件を求め、季節や衣服状態、活動
状態等を考慮して、自動的に温度や湿度を設定すること
ができる。First, in the comfortable dehumidifying operation (210), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the indoor air (211), and the desired indoor temperature and humidity are set (212).
Is done. Next, the blowing condition of the indoor fan 12 is set (213), which indicates whether to perform the dehumidifying operation with a low air volume or the high air volume, and based on this setting (213), the low air volume dehumidifying operation (214). Or high air volume dehumidification operation (2
15) is selected. In addition, when performing comfortable dehumidification operation,
It is necessary to set the room temperature and humidity to make people feel comfortable, but PMV (Predicted Mean Vo)
It is designed to be controlled based on a thermal environment evaluation index such as te), which means a predicted average declaration). When controlled based on this thermal environment evaluation index, only the indoor temperature and humidity are used. Instead, it is possible to obtain comfortable conditions of thermal sensation by considering radiation temperature, wind speed, clothing amount, and activity amount, and automatically set temperature and humidity in consideration of season, clothes condition, activity condition, and the like.

【００２３】カビ・ダニ防止除湿運転（２２０）では、
快適除湿運転（２１０）の場合と同様に、温度センサ１
７、湿度センサ１８により室内空気の温湿度の検出（２
２１）、希望する室内温湿度の設定（２２２）が行われ
る。次に低風量で除湿運転を行うかあるいは高風量で除
湿運転を行うかの室内ファン１２の送風状態の設定（２
２３）が行われ、この設定（２２３）に基づいて低風量
除湿運転（２２４）または高風量除湿運転（２２５）が
選択される。なお、カビやダニの繁殖を防止するには相
対湿度を４０〜６０％位にすれば良いことがわかってお
り、従ってカビ、ダニ防止の除湿運転では、例えば湿度
を５０％位に自動的に固定して設定してもよい。このよ
うな除湿運転を行うことにより、体感温度をよく保てる
状態で除湿運転が行える。In the dehumidifying operation (220) for preventing mold and ticks,
As in the comfortable dehumidification operation (210), the temperature sensor 1
7. The humidity sensor 18 detects the temperature and humidity of indoor air (2
21) The desired indoor temperature and humidity are set (222). Next, whether the dehumidifying operation is performed with a low air volume or the dehumidifying operation is performed with a high air volume is set for the blowing state of the indoor fan 12 (2
23) is performed, and the low air flow dehumidifying operation (224) or the high air flow dehumidifying operation (225) is selected based on this setting (223). It is known that the relative humidity should be set to about 40 to 60% to prevent the reproduction of mold and mite. Therefore, in the dehumidifying operation for preventing mold and mite, for example, the humidity is automatically set to about 50%. It may be fixed and set. By performing such a dehumidifying operation, the dehumidifying operation can be performed in a state where the sensible temperature can be maintained well.

【００２４】おやすみ・おめざめ除湿運転（２３０）で
は、温度センサ１７、湿度センサ１８により室内空気の
温湿度の検出（２３１）、希望する室内温湿度の設定
（２３２）が行われる。次に、睡眠時において特に寝初
めや朝起きる時には、気流感や騒音が高いと寝苦しいた
め、室内ファン１２の送風能力を下げた低風量の除湿運
転（２３３）が行われる。なお、睡眠時における室内の
快適な温湿度についてはおおよその値が分かっており、
例えば梅雨時や夏の蒸し暑い時には、室温を余り下げず
に湿度を十分下げた方が快適で健康的な睡眠環境にな
る。従って、おやすみ・おめざめ除湿運転では、室内の
温度及び湿度をこのような値に自動的に固定して設定し
てもよい。さらにこの運転モードは、寝初め、熟睡時、
朝起きる時など人間の睡眠パターンに合わせてプログラ
ムされた自動運転モードにして使うこともできる。In the good night / whale dehumidifying operation (230), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the room air (231) and set the desired room temperature and humidity (232). Next, during sleep, especially at the beginning of bedtime or when waking up in the morning, if the feeling of airflow and noise are high, it is difficult to sleep, so the dehumidifying operation of low air volume (233) in which the blowing capacity of the indoor fan 12 is lowered is performed. In addition, about the comfortable temperature and humidity in the room during sleep, we know the approximate value,
For example, during the rainy season or in the hot and humid summer, it is better to keep the room temperature at a proper level and lower the humidity to create a comfortable and healthy sleeping environment. Therefore, in the good night / desired dehumidifying operation, the room temperature and humidity may be automatically fixed and set to such values. In addition, this operation mode is
It can also be used in an automatic driving mode programmed according to human sleep patterns such as when waking up in the morning.

【００２５】ランドリー除湿運転（２４０）では、温度
センサ１７、湿度センサ１８により室内空気の温湿度の
検出（２４１）、希望する室内温湿度の設定（２４２）
が行われる。次に、洗濯物の乾燥時には、気流が広い範
囲までゆき渡り除湿能力が十分高い必要があるため、室
内ファン１２の送風能力を上げた高風量除湿運転（２４
３）が行われる。また、洗濯物の乾燥時における温湿度
は、微妙に変わる人間の体感と違い、大体一定に設定す
ることができる。従って、ランドリー除湿運転でも室内
の温度及び湿度を自動的に固定して設定することができ
る。In the laundry dehumidifying operation (240), the temperature sensor 17 and the humidity sensor 18 detect the temperature and humidity of the indoor air (241), and the desired indoor temperature and humidity are set (242).
Is done. Next, when the laundry is dried, it is necessary for the air flow to spread over a wide range and to have a sufficiently high dehumidifying ability. Therefore, a high air flow dehumidifying operation (24
3) is performed. In addition, the temperature and humidity when the laundry is dried can be set to be approximately constant, unlike the human sensation that slightly changes. Therefore, even in the laundry dehumidifying operation, the room temperature and humidity can be automatically fixed and set.

【００２６】なお、図２に示す各使用目的の運転モード
において、室内温湿度検出（２１１）、（２２１）、
（２３１）、（２４１）、室内温湿度設定（２１２）、
（２２２）、（２３２）、（２４２）、室内送風状態設
定（２１３）、（２２３）は必ずしもこの順に行う必要
はなく、任意に設定することができる。In the operation modes for each purpose shown in FIG. 2, the indoor temperature / humidity detection (211), (221),
(231), (241), indoor temperature and humidity setting (212),
(222), (232), (242), indoor air-blowing state setting (213), (223) do not necessarily need to be performed in this order, and can be set arbitrarily.

【００２７】以上述べたような使用目的のそれぞれにお
いて、運転モードは大きく分けて、低風量除湿運転と高
風量除湿運転になる。空気調和機自体は、これらの低風
量除湿運転と高風量除湿運転を快適な除湿運転、カビ・
ダニ防止の除湿運転、おやすみ・おめざめ除湿運転、ラ
ンドリー除湿運転等の各使用目的モードに合わせて使う
ことができる。In each of the above-mentioned purposes of use, the operation modes are roughly classified into a low air flow dehumidifying operation and a high air flow dehumidifying operation. The air conditioner itself uses these low air volume dehumidification operation and high air volume dehumidification operation for comfortable dehumidification operation, mold and
It can be used according to each purpose mode, such as dehumidifying operation to prevent ticks, good night / awakening dehumidifying operation, and laundry dehumidifying operation.

【００２８】以上述べた低風量除湿運転及び高風量除湿
運転においては、室温の検出値と設定値が異なる場合に
は、この温度差ΔＴ（ΔＴ＝検出室温−設定室温で表さ
れる）に応じて、検出室温の方が高くΔＴがプラスの場
合には冷房気味、両者がほぼ等しくΔＴがゼロ近傍の場
合には等温気味、検出温度の方が低くΔＴがマイナスの
場合には暖房気味の除湿運転を行う必要がある。以下こ
れらの運転方法について述べる。In the low air volume dehumidifying operation and the high air volume dehumidifying operation described above, when the detected value of the room temperature is different from the set value, the temperature difference ΔT (ΔT = detected room temperature−set room temperature) is used. When the detected room temperature is higher and ΔT is positive, cooling is likely to occur, when both are almost equal, ΔT is near isothermal, and when detected temperature is lower and ΔT is negative, heating is dehumidified. You need to drive. These operating methods will be described below.

【００２９】低風量除湿運転（３００）での運転方法を
示す図３から分かるように、まず室内ファンを低風量運
転に設定（３０１）する。次に室内において温度センサ
１７で検出した検出室温と設定室温とを比較（３０２）
し、温度差ΔＴがプラスの場合には、低風量冷房気味除
湿運転（３１０）を行う。この場合には、圧縮機１は、
能力を下げても十分な除湿能力が得られることから、低
能力運転（３１１）に設定し、さらに冷房気味運転を行
うためには、室外熱交換器３での放熱能力を増して加熱
器として使用する室内熱交換器６ａによる空気流１５に
対する加熱能力を下げる必要があり、このために室外フ
ァン１０の送風能力を増大（３１２）させる。As can be seen from FIG. 3 showing the operating method in the low air flow dehumidifying operation (300), first, the indoor fan is set to the low air flow operation (301). Next, the detected room temperature detected by the temperature sensor 17 in the room is compared with the set room temperature (302).
However, when the temperature difference ΔT is positive, the low air flow cooling / dehumidifying operation (310) is performed. In this case, the compressor 1
Even if the capacity is lowered, sufficient dehumidifying capacity can be obtained. Therefore, in order to set the low capacity operation (311) and perform the air-conditioning operation, the heat dissipation capacity of the outdoor heat exchanger 3 is increased to serve as a heater. It is necessary to reduce the heating capacity of the used indoor heat exchanger 6a for the air flow 15, and for this reason, the blowing capacity of the outdoor fan 10 is increased (312).

【００３０】温度差ΔＴがほぼゼロの場合には、低風量
等温気味除湿運転（３２０）を行う。この運転では、圧
縮機１は、能力を下げても十分な除湿能力が得られるこ
とから、低能力運転（３２１）にし、さらに等温気味運
転にするには、室外熱交換器３での放熱能力を中くらい
にして、加熱器として使用する室内熱交換器６ａによる
空気流１５に対する加熱能力を中くらいにする必要があ
り、このために室外ファン１０の送風能力を中くらい
（３２２）に設定する。When the temperature difference ΔT is almost zero, the low air flow isothermal dehumidifying operation (320) is performed. In this operation, the compressor 1 can obtain a sufficient dehumidifying capacity even if the capacity is reduced. Therefore, in order to perform the low capacity operation (321) and further to perform the isothermal operation, the heat dissipation capacity of the outdoor heat exchanger 3 is required. Is set to be medium, and the heating capacity for the air flow 15 by the indoor heat exchanger 6a used as a heater needs to be medium. Therefore, the blowing capacity of the outdoor fan 10 is set to medium (322). .

【００３１】温度差ΔＴがマイナスの場合には、低風量
暖房気味除湿運転（３３０）を行う。この運転では、室
外熱交換器３での放熱量を減らして加熱器として使用す
る室内熱交換器６ａにより、空気流１５に対する加熱能
力を大きくする必要がある。このために室外ファン１０
の送風能力を極力減らし、必要に応じて室外ファンを停
止（３３２）する。又、圧縮機１は、能力を下げても十
分な除湿能力が得られるが、圧縮機１の能力を増すに従
って加熱器６ａの能力が増し、より暖房気味にすること
ができる。従って、圧縮機１の能力は、暖房気味の程度
にしたがって能力を増大（３３１）させる。When the temperature difference ΔT is negative, a low air flow heating dehumidifying operation (330) is performed. In this operation, it is necessary to reduce the heat radiation amount in the outdoor heat exchanger 3 and increase the heating capacity for the air flow 15 by the indoor heat exchanger 6a used as a heater. For this purpose, the outdoor fan 10
The air-blowing capacity is reduced as much as possible, and the outdoor fan is stopped (332) if necessary. Further, the compressor 1 can obtain a sufficient dehumidifying capacity even if the capacity is reduced, but as the capacity of the compressor 1 is increased, the capacity of the heater 6a is increased, and the compressor 1 can be more heated. Therefore, the capacity of the compressor 1 increases (331) according to the degree of heating.

【００３２】ここで、低風量除湿運転の具体的な運転例
としては、例えば室内温湿度２４℃、６０％、室外温湿
度２４℃、８０％の条件おいて、標準冷房能力２．８ｋ
Ｗのルームエアコンを用い、室外風量を十分下げ、室内
風量を約２ｍ3／ｍｉｎとした場合、圧縮機の理論押除
量を０．９８ｍ3／ｈとすると吹出温度が約２１℃の冷
房気味運転、圧縮機の理論押除量を１．５ｍ3／ｈとす
ると吹出温度が約２７℃の暖房気味運転とすることがで
きる。すなわち、室内ユニットの吹出空気温度が室温−
３℃の冷房気味除湿運転から室温＋３℃までの暖房気味
除湿運転を行うことが出来る。Here, as a concrete operation example of the low air flow dehumidifying operation, for example, the standard cooling capacity is 2.8 k under the conditions of indoor temperature and humidity of 24 ° C. and 60% and outdoor temperature and humidity of 24 ° C. and 80%.
When a room air conditioner of W is used and the outdoor air volume is sufficiently reduced and the indoor air volume is set to about 2 m 3 / min, if the theoretical displacement of the compressor is set to 0.98 m 3 / h, the outlet temperature tends to be about 21 ° C. When the operation and the theoretical displacement amount of the compressor are set to 1.5 m 3 / h, it is possible to perform a heating-like operation in which the blowout temperature is about 27 ° C. That is, the temperature of the air blown out from the indoor unit is room temperature-
It is possible to perform a cooling dehumidifying operation at 3 ° C and a heating dehumidifying operation up to room temperature + 3 ° C.

【００３３】なお、以上述べた低風量除湿運転において
は、除湿量が十分とれることから、圧縮機１の能力を低
く設定したが、これに限るものではなく、圧縮機の能力
を上げていっても良く、この場合には入力が大幅に増大
するが、除湿能力は徐々に増えてゆく。In the low air volume dehumidifying operation described above, the capacity of the compressor 1 is set low because a sufficient dehumidifying amount can be obtained, but the capacity of the compressor is not limited to this, and the capacity of the compressor is increased. The input is significantly increased in this case, but the dehumidification capacity gradually increases.

【００３４】次に図４により高風量除湿運転（３５０）
の運転方法を説明する。まず、室内ファン１２を高風量
運転に設定（３５１）する。次に室内において温度セン
サ１７で検出した検出室温と設定室温とを比較（３５
２）し、温度差ΔＴがプラスの場合には、高風量冷房気
味除湿運転（３６０）を行う。この運転では、室内ファ
ン１２が高風量運転であることから、蒸発器として作用
する室内熱交換器６ｂの蒸発温度を下げて十分な除湿能
力を得るために圧縮機１を高能力運転（３６１）にし、
さらに冷房気味運転にするには、室外熱交換器３での放
熱能力を増して加熱器として作用する室内熱交換器６ａ
による空気流１５に対する加熱能力を下げてやる必要が
ある。このために室外ファン１０の送風能力を増大（３
６２）させる。Next, referring to FIG. 4, a high air flow dehumidifying operation (350)
The driving method of is explained. First, the indoor fan 12 is set to high air volume operation (351). Next, the detected room temperature detected by the temperature sensor 17 in the room is compared with the set room temperature (35
2) Then, when the temperature difference ΔT is positive, a high air flow cooling / dehumidifying operation (360) is performed. In this operation, since the indoor fan 12 is in high air volume operation, the compressor 1 is operated in high capacity to lower the evaporation temperature of the indoor heat exchanger 6b acting as an evaporator and obtain sufficient dehumidifying capacity (361). West,
In order to perform cooling-like operation further, the indoor heat exchanger 6a which increases the heat radiation capacity of the outdoor heat exchanger 3 and acts as a heater
It is necessary to reduce the heating capacity for the air flow 15 due to. For this reason, the blowing capacity of the outdoor fan 10 is increased (3
62) Allow.

【００３５】温度差ΔＴがほぼゼロの場合には、高風量
等温気味除湿運転（３７０）を行う。この運転では、上
述した冷房気味運転と同じ理由により、圧縮機１は高能
力運転（３７１）にする。さらに等温気味運転にするに
は、室外熱交換器３での放熱能力を中くらいにして、加
熱器として作用する室内熱交換器６ａによる空気流１５
に対する加熱能力を中くらいにする必要がある。このた
めに室外ファン１０の送風能力を中くらい（３７２）に
する。温度差ΔＴがマイナスの場合には、高風量暖房気
味除湿運転（３８０）を行う。この運転では、圧縮機１
は、上述した冷房気味運転や等温気味運転と同じ理由
で、高能力運転（３８１）にする。さらに暖房気味運転
にするには、室外熱交換器３での放熱量を減らして加熱
器として作用する室内熱交換器６ａによる空気流１５に
対する加熱能力を大きくする必要がある。このために室
外ファン１０の送風能力を極力減らし、必要に応じて室
外ファン１０を停止（３８２）する。When the temperature difference ΔT is substantially zero, the high air flow isothermal dehumidifying operation (370) is performed. In this operation, the compressor 1 is set to the high capacity operation (371) for the same reason as the above-mentioned cooling operation. For further isothermal operation, the heat dissipation capacity of the outdoor heat exchanger 3 is set to a medium level and the air flow 15 by the indoor heat exchanger 6a acting as a heater is increased.
It is necessary to have a medium heating capacity for. For this reason, the blowing capacity of the outdoor fan 10 is set to a medium level (372). When the temperature difference ΔT is negative, the high air volume heating dehumidifying operation (380) is performed. In this operation, the compressor 1
Is set to the high capacity operation (381) for the same reason as the above-mentioned cooling operation or isothermal operation. Further, in order to perform the heating-like operation, it is necessary to reduce the heat radiation amount in the outdoor heat exchanger 3 and increase the heating capacity for the air flow 15 by the indoor heat exchanger 6a acting as a heater. Therefore, the blowing capacity of the outdoor fan 10 is reduced as much as possible, and the outdoor fan 10 is stopped (382) if necessary.

【００３６】ここで、高風量除湿運転の具体的な運転例
としては、例えば室内温湿度２４℃、６０％、室外温湿
度２４℃、８０％の条件で、標準冷房能力２．８ｋＷの
ルームエアコンを用い、室外風量を十分下げ、室内風量
を約６ｍ3／ｍｉｎとした場合、圧縮機の理論押除量を
１．９ｍ3／ｈとすると吹出温度が約２６．５℃の暖房
気味運転とすることができる。すなわち室内ユニットの
吹出空気温度が室温＋３℃までの暖房気味を行うことが
出来る。Here, as a specific operation example of the high air volume dehumidifying operation, for example, a room air conditioner having a standard cooling capacity of 2.8 kW under conditions of indoor temperature and humidity of 24 ° C. and 60% and outdoor temperature and humidity of 24 ° C. and 80%. When the outdoor air volume is sufficiently reduced and the indoor air volume is set to about 6 m 3 / min, and the theoretical pushing amount of the compressor is set to 1.9 m 3 / h, the blowout temperature is about 26.5 ° C and the operation tends to be heating. can do. That is, the temperature of the air blown out from the indoor unit can be heated to room temperature + 3 ° C.

【００３７】ところで上記した高風量除湿運転では、圧
縮機１を高能力運転に設定することから入力が大きくな
る。この入力が大きくなる問題を解決できる室内ユニッ
トの構造を示す側断面図を図５に、この場合の高風量除
湿運転方法の流れ図を図６に示す。By the way, in the high air volume dehumidifying operation described above, the input becomes large because the compressor 1 is set to the high capacity operation. FIG. 5 shows a side sectional view showing the structure of the indoor unit that can solve the problem of large input, and FIG. 6 shows a flowchart of the high air flow dehumidifying operation method in this case.

【００３８】図５において、６ａ、６ｂ、１２は、それ
ぞれ図１に示したサイクル構成と同一のものであり、そ
れぞれ風下側の室内熱交換器、風上側の室内熱交換器、
室内ファンである。また、３１は吸い込みグリル、３２
は通風路を形成している背面側のケーシング、３３は凝
縮水を受ける露受皿、３４は開閉可能なダンパ、３５は
ケーシング３２の上部に設けた通風路である。このよう
な構成にすることにより、除湿運転時には室内熱交換器
６ｂが蒸発器、室内熱交換器６ａが加熱器となり、室内
ファン１２を運転して室内空気を矢印で示すように空気
流３６から空気流３７のように流すことにより、空気流
３６は、吸込みグリル３１を通り、蒸発器６ｂで冷却・
除湿された後、加熱器６ａで加熱されて、室内ファン１
２を通って矢印の方向に吹き出される。また、蒸発器６
ｂで生じた凝縮水は、露受皿３３に一旦受けられた後、
室外へ排出される。In FIG. 5, reference numerals 6a, 6b and 12 respectively have the same cycle configurations as those shown in FIG.
It is an indoor fan. In addition, 31 is a suction grill, 32
Is a casing on the back side forming an air passage, 33 is a dew tray for receiving condensed water, 34 is an openable / closable damper, and 35 is an air passage provided above the casing 32. With such a configuration, during the dehumidifying operation, the indoor heat exchanger 6b serves as an evaporator and the indoor heat exchanger 6a serves as a heater, and the indoor fan 12 is operated to move the indoor air from the air flow 36 as indicated by an arrow. By flowing like the air flow 37, the air flow 36 passes through the suction grill 31 and is cooled by the evaporator 6b.
After being dehumidified, the indoor fan 1 is heated by the heater 6a.
It is blown out through 2 in the direction of the arrow. Also, the evaporator 6
After the condensed water generated in b is once received by the dew tray 33,
It is discharged outdoors.

【００３９】次に、以下に図５に示す室内ユニットを用
いた場合の高風量除湿運転の方法を図１に示すサイクル
構成を参照しながら、図６に示す流れ図により説明す
る。Next, a method of high air flow dehumidifying operation using the indoor unit shown in FIG. 5 will be described below with reference to the cycle configuration shown in FIG. 1 with reference to the flow chart shown in FIG.

【００４０】高風量除湿運転モードが選択（４００）さ
れると、まず吸込みダンパ３４が３４ａに示すように開
き（４０１）、室内ファン１２を高風量の状態で運転
（４０２）する。次に図１に示す温度センサ１７で検出
した検出室温を設定室温と比較（４０３）し、温度差Δ
Ｔがプラスの場合には、高風量冷房気味除湿運転（４１
０）を行う。この運転では、室内ファン１２は高風量の
運転であるが、この風量は通風路３５を通る風量と室内
熱交換器６ｂ及び６ａを通る風量との和であり、室内熱
交換器６ｂ及び６ａを通る風量は少風量となり、圧縮機
１を低能力運転（４１１）にしても蒸発器６ｂの蒸発温
度が下がり十分な除湿能力が得られる。さらに冷房気味
運転にするには、室外熱交換器３での放熱能力を増して
加熱器として作用する室内熱交換器６ａによる空気流３
６に対する加熱能力を下げてやる必要がある。このため
に、室外ファン１０の送風能力を増大ぎみ（４１２）に
する。When the high air volume dehumidifying operation mode is selected (400), first, the suction damper 34 is opened as shown at 34a (401), and the indoor fan 12 is operated in a high air volume state (402). Next, the detected room temperature detected by the temperature sensor 17 shown in FIG. 1 is compared with the set room temperature (403), and the temperature difference Δ
If T is positive, high air volume cooling dehumidifying operation (41
0) is performed. In this operation, the indoor fan 12 operates at a high air volume, and this air volume is the sum of the air volume passing through the ventilation passage 35 and the air volume passing through the indoor heat exchangers 6b and 6a. The amount of air passing through becomes small, and even if the compressor 1 is operated at a low capacity (411), the evaporation temperature of the evaporator 6b is lowered and a sufficient dehumidifying capacity is obtained. Further, in order to perform cooling-like operation, the air flow 3 by the indoor heat exchanger 6a which functions as a heater by increasing the heat radiation capacity of the outdoor heat exchanger 3
It is necessary to lower the heating capacity for 6. For this reason, the blowing capacity of the outdoor fan 10 is increased to the limit (412).

【００４１】温度差ΔＴがほぼゼロの場合には、高風量
等温気味除湿運転（４２０）を行う。この運転では、上
述した冷房気味運転と同じ理由により、圧縮機１は低能
力運転（４２１）にする。さらにこの等温気味運転で
は、室外熱交換器３での放熱能力を中くらいにして加熱
器として作用する室内熱交換器６ａによる空気流３６に
対する加熱能力を中くらいにする必要がある。このため
に、室外ファン１０の送風能力を中位（４２２）にす
る。When the temperature difference ΔT is substantially zero, the high air flow isothermal dehumidifying operation (420) is performed. In this operation, the compressor 1 is set to the low capacity operation (421) for the same reason as the above-described cooling operation. Further, in this isothermal operation, it is necessary to set the heat radiation capacity of the outdoor heat exchanger 3 to be medium and the heating capacity for the air flow 36 by the indoor heat exchanger 6a acting as a heater to be medium. For this reason, the blowing capacity of the outdoor fan 10 is set to the middle level (422).

【００４２】温度差ΔＴがマイナスの場合には、高風量
暖房気味除湿運転（４３０）を行う。この運転でも、圧
縮機１は、上述した冷房気味運転や等温気味運転と同じ
理由により、低能力運転（４３１）にする。さらにこの
暖房気味運転を行うには、室外熱交換器３での放熱量を
減らして加熱器として作用する室内熱交換器６ａによる
空気流３６に対する加熱能力を大きくする必要がある。
このために、室外ファン１０の送風能力を極力減らし、
必要に応じて室外ファン１０を停止（４３２）する。When the temperature difference ΔT is negative, a high air volume heating dehumidifying operation (430) is performed. Even in this operation, the compressor 1 is set to the low capacity operation (431) for the same reason as the above-described cooling operation or isothermal operation. Further, in order to perform this heating-like operation, it is necessary to reduce the heat radiation amount in the outdoor heat exchanger 3 and increase the heating capacity for the air flow 36 by the indoor heat exchanger 6a acting as a heater.
For this reason, the blowing capacity of the outdoor fan 10 is reduced as much as possible,
The outdoor fan 10 is stopped (432) if necessary.

【００４３】なお、図５において低風量の除湿運転は、
ダンパ３４を閉じることにより、図３に示した運転方法
と同様にして行うことができる。又、図５において、３
４は回転開閉可能なダンパとしたが、これに限るもので
はなく、開閉可能な構造であればよい。また、これまで
の説明においては、室内温湿度の検出は、図２について
説明した手順で行っているが、これに限らず、図３、図
４、図６において検出室温と設定室温の比較（３０
２）、（３５２）、（４０３）の前で行うことも可能で
ある。In FIG. 5, the dehumidifying operation with a low air flow is as follows.
By closing the damper 34, the same operation method as shown in FIG. 3 can be performed. Also, in FIG.
Although 4 is a damper that can be opened and closed by rotation, the damper is not limited to this and may be any structure that can be opened and closed. Further, in the above description, the detection of the room temperature and humidity is performed by the procedure described with reference to FIG. 2, but the present invention is not limited to this, and the comparison between the detected room temperature and the set room temperature in FIG. 3, FIG. 4 and FIG. Thirty
It is also possible to perform before 2), (352), and (403).

【００４４】又、本発明による他の実施例を図７及び図
８に示す。図７は本実施例のサイクルの室外側部分を示
す構成図、図８は室外熱交換器３の放熱量調節方法をに
示す図である。Another embodiment according to the present invention is shown in FIGS. 7 and 8. FIG. 7 is a configuration diagram showing an outdoor portion of the cycle of the present embodiment, and FIG. 8 is a diagram showing a method of adjusting the heat radiation amount of the outdoor heat exchanger 3.

【００４５】図７に示すサイクルの室外側部分は、図１
において二点鎖線で囲んだ部分４０に相当し、図１に示
すサイクル構成において、室外熱交換器３をバイパスさ
せて二方弁４１を介してバイパス管４２を設けている。
また、図７において、図１と同一番号をつけたものは、
同一部分を示す。The outdoor portion of the cycle shown in FIG. 7 is as shown in FIG.
In the cycle configuration shown in FIG. 1, the outdoor heat exchanger 3 is bypassed and the bypass pipe 42 is provided via the two-way valve 41.
Further, in FIG. 7, those having the same numbers as in FIG.
The same part is shown.

【００４６】図７に示すサイクル構成を有する本実施例
の空気調和機では、その運転方法は、図１に示すサイク
ル構成の場合とほぼ同様であるが、図３に示す低風量暖
房気味除湿運転（３３０）におけるステップ３３２、図
４に示す高風量暖房気味除湿運転（３８０）におけるス
テップ３８２及び図５に示す室内ユニットの構造に対応
する図６に示した高風量暖房気味除湿運転（４３０）に
おけるステップ４３２での室外熱交換器３の放熱能力を
調節する方法において次のように異なっている。In the air conditioner of this embodiment having the cycle configuration shown in FIG. 7, the operating method is almost the same as in the case of the cycle configuration shown in FIG. 1, but the low air flow heating dehumidifying operation shown in FIG. In step 332 in (330), in step 382 in the high air volume heating / dehumidifying operation shown in FIG. 4 and in in the high air volume heating / dehumidifying operation (430) shown in FIG. 6 corresponding to the structure of the indoor unit shown in FIG. The method of adjusting the heat radiation capacity of the outdoor heat exchanger 3 in step 432 is different as follows.

【００４７】暖房気味除湿運転おいては、図８に示す室
外熱交換器３の放熱量調節方法により、まず図１に示す
実施例において加熱器として作用する室内熱交換器６ａ
の加熱能力を増すために、室外ファン１０の送風能力を
極力落とすか、さらには室外ファン１０を停止（５０
１）する。次に再度室温を検知して設定室温と比較（５
０２）し、検出室温が設定室温より低ければ二方弁４１
を開く（５０３）。また、検出室温が設定室温より低く
なければ設定を終了（５０４）する。この結果、ステッ
プ５０３において二方弁４１を開いた場合には、圧縮機
１から吐出された高温高圧の冷媒流のほとんどが室外熱
交換器３を通らず加熱器として作用する室内熱交換器６
ａに流入するため、二方弁４１を閉じ室外ファン１０を
止めた場合に、自然対流により外気へ放熱されていた熱
量も加熱器として作用する室内熱交換器６ａへ運ばれて
室内熱交換器６ａで加熱量がさらに増し、より暖房気味
の除湿運転を行うことができる。In the heating / dehumidifying operation, the indoor heat exchanger 6a which functions as a heater in the embodiment shown in FIG. 1 is first prepared by the heat radiation amount adjusting method of the outdoor heat exchanger 3 shown in FIG.
In order to increase the heating capacity of the outdoor fan 10, the blowing capacity of the outdoor fan 10 is reduced as much as possible, or the outdoor fan 10 is stopped (50
1) Do. Next, the room temperature is detected again and compared with the set room temperature (5
02) and if the detected room temperature is lower than the set room temperature, the two-way valve 41
Open (503). If the detected room temperature is not lower than the set room temperature, the setting is finished (504). As a result, when the two-way valve 41 is opened in step 503, most of the high-temperature and high-pressure refrigerant flow discharged from the compressor 1 does not pass through the outdoor heat exchanger 3 and acts as a heater.
When the two-way valve 41 is closed and the outdoor fan 10 is stopped, the amount of heat radiated to the outside air by natural convection is also carried to the indoor heat exchanger 6a, which acts as a heater. In 6a, the heating amount is further increased, and the dehumidifying operation more like heating can be performed.

【００４８】これまで図１に示す実施例のサイクル構成
において、除湿運転の場合について説明してきたが、冷
房、暖房の各運転に対してもサイクル性能及び室内熱交
換器６ａ、６ｂでの熱交換性能を確保して効率良く運転
する必要がある。以下、この方法について説明する。In the cycle configuration of the embodiment shown in FIG. 1, the case of the dehumidifying operation has been described so far, but the cycle performance and the heat exchange in the indoor heat exchangers 6a and 6b are also applicable to the cooling and heating operations. It is necessary to ensure performance and operate efficiently. Hereinafter, this method will be described.

【００４９】まず、図１に示す実施例では、室内熱交換
器を６ａと６ｂに二分割し、これらを二方弁８を介して
直列に接続してあるため、冷房運転及び暖房運転、特に
冷房運転においては、室内熱交換器６ａ及び６ｂとも低
圧であり、ガス冷媒の比容積が大きく体積流量として大
きくなる蒸発器であるため、室内熱交換器での圧力損失
が大きくなってサイクルの性能が低下する。First, in the embodiment shown in FIG. 1, the indoor heat exchanger is divided into two parts, 6a and 6b, which are connected in series via the two-way valve 8, so that the cooling operation and the heating operation, especially In the cooling operation, both the indoor heat exchangers 6a and 6b are at a low pressure, and since the evaporator has a large specific volume of the gas refrigerant and a large volume flow rate, the pressure loss in the indoor heat exchanger increases and the cycle performance increases. Is reduced.

【００５０】この問題を解決できる一実施例を図９及び
図１０に示す。図９及び図１０に示す実施例は、図１に
示す実施例において、一点鎖線で囲んだ室内側部分９０
の熱交換器部分に相当し、図１０は、図９において矢印
Ｐの方向からみた正面図である。図９及び図１０におい
て、５１ａ、５１ｂは、それぞれ図１に示す６ａ、６ｂ
に相当する二分割された室内熱交換器であり、室内熱交
換器５１ａは、Ａ点で冷媒配管５２と冷媒配管５３の二
系統の冷媒配管に分かれた後、Ｂ点で再び一系統に合流
する配管構成を有し、室内熱交換器５１ｂも同様に、Ｃ
点で冷媒配管５４と冷媒配管５５の二系統の冷媒配管に
分かれた後、Ｄ点で再び一系統に合流する配管構成にし
てある。また、５６は放熱フィンである。その他の図１
と同一番号を付したものは同一部分を示す。An embodiment capable of solving this problem is shown in FIGS. 9 and 10. The embodiment shown in FIGS. 9 and 10 is different from the embodiment shown in FIG. 1 in that the indoor side portion 90 surrounded by the alternate long and short dash line.
10 is a front view seen from the direction of arrow P in FIG. 9. 9 and 10, 51a and 51b are 6a and 6b shown in FIG. 1, respectively.
The indoor heat exchanger 51a is a two-divided indoor heat exchanger, and the indoor heat exchanger 51a is divided into two lines of refrigerant pipes, a refrigerant pipe 52 and a refrigerant pipe 53, at point A, and then merges again into one system at point B. The indoor heat exchanger 51b similarly has a piping configuration
At a point, the refrigerant pipe 54 and the refrigerant pipe 55 are divided into two systems of refrigerant pipes, and then at a point D, they are joined again into one system. Further, reference numeral 56 is a radiation fin. Other Figure 1
The same numbers as in the above indicate the same parts.

【００５１】以上のように構成された空気調和機におい
て、冷房運転時及び暖房運転時には、二方弁８を開くこ
とにより室内熱交換器５１ａおよび５１ｂにおいて、冷
媒はそれぞれ二系統に分かれて流れるため、各系統を流
れる冷媒流量は半分になり、室内熱交換器５１ａ及び５
１ｂでの冷媒流圧力損失が低減するので、性能の低下を
防止できる。In the air conditioner configured as described above, during the cooling operation and the heating operation, the two-way valve 8 is opened so that the refrigerant flows in two systems in the indoor heat exchangers 51a and 51b. , The flow rate of the refrigerant flowing through each system is halved, and the indoor heat exchangers 51a and 5a
Since the refrigerant flow pressure loss in 1b is reduced, it is possible to prevent performance deterioration.

【００５２】なお、図９及び図１０に示す実施例では、
室内熱交換器５１ａ及び５１ｂの冷媒配管を二系統に分
けた場合を示したが、これに限られるものではなく、さ
らに多くの系統に分ける事も可能であり、この場合も室
内熱交換器５１ａ及び５１ｂでの冷媒流圧力損失を低減
し、性能の低下を防止できる。但し、冷媒流をあまり多
系統にすると、冷媒流の圧力損失は低下するが、熱伝達
率の低下が著しく、冷房能力や動作係数といった空気調
和機全体の性能が低下してしまうため、最適な系統数に
設定する必要があり、この系統数は冷媒配管の内径によ
って決定される。In the embodiment shown in FIGS. 9 and 10,
Although the case where the refrigerant pipes of the indoor heat exchangers 51a and 51b are divided into two systems is shown, the present invention is not limited to this, and it is also possible to divide into more systems, and in this case also the indoor heat exchanger 51a. It is possible to reduce the pressure loss of the refrigerant flow at 51 and 51b and prevent the performance from deteriorating. However, if the refrigerant flow is too multi-system, the pressure loss of the refrigerant flow will decrease, but the heat transfer coefficient will decrease significantly, and the overall performance of the air conditioner, such as the cooling capacity and coefficient of operation, will decrease. It is necessary to set the number of systems, and this number of systems is determined by the inner diameter of the refrigerant pipe.

【００５３】次に、暖房運転においては、暖房能力や動
作係数といった性能を向上するためには、凝縮器として
作用する室内熱交換器において、その入口での高温のガ
ス冷媒流が流れる熱交換器部分を、その風下側で熱交換
する熱交換器部分のない位置で空気流と熱交換させ、さ
らに冷媒流の出口にあたる熱交換器部分を十分にサブク
ールがとれるように、比較的低温の風上側の空気流と熱
交換させる必要がある。このように構成した例を図１１
に示す。図１１において、６０ａは点Ｅ、点Ｆで結合し
た二系統の冷媒配管６１、６２からなる室内熱交換器、
６０ｂはＧ点で結合した二系統の冷媒配管６３、６４か
らなる室内熱交換器、６０ｃは暖房運転時には冷媒流が
室内熱交換器６０ｂの上流側で、かつ空気流１５が室内
熱交換器６０ｂ通過後の風下側になる位置に設けたＨ点
で結合した二系統の冷媒配管６６、６７からなる室内熱
交換器、６０ｄは暖房運転時には冷媒流が室内熱交換器
６０ａの下流側で、かつ空気流１５が直接当たりしかも
室内熱交換器６０ｂの上方になる位置に設けた冷媒の流
れを一系統にした冷媒配管６５を有する室内熱交換器で
あり、基本的には図９に示す実施例に対して、さらに室
内熱交換器６０ｃ、６０ｄを設けた構成としたものであ
る。Next, in the heating operation, in order to improve the performance such as the heating capacity and the coefficient of operation, in the indoor heat exchanger acting as a condenser, the heat exchanger through which a high temperature gas refrigerant flow flows The part is heat-exchanged with the air flow at a position where there is no heat-exchanger part on the leeward side, and the heat-exchanger part, which is the outlet of the refrigerant flow, is sufficiently subcooled so that the part is relatively cool on the windward side. Need to exchange heat with the air flow. An example of such a configuration is shown in FIG.
Shown in. In FIG. 11, reference numeral 60a denotes an indoor heat exchanger including two systems of refrigerant pipes 61 and 62 connected at points E and F,
60b is an indoor heat exchanger consisting of two systems of refrigerant pipes 63 and 64 connected at the G point, 60c is a refrigerant flow upstream of the indoor heat exchanger 60b during heating operation, and the air flow 15 is the indoor heat exchanger 60b. An indoor heat exchanger consisting of two systems of refrigerant pipes 66, 67 connected at a point H provided at a position on the leeward side after passing, 60d is a refrigerant flow at the downstream side of the indoor heat exchanger 60a during heating operation, and An indoor heat exchanger having a refrigerant pipe 65 in which the air flow 15 is directly contacted and is located above the indoor heat exchanger 60b and which has a single refrigerant flow system. Basically, the embodiment shown in FIG. On the other hand, the indoor heat exchangers 60c and 60d are further provided.

【００５４】以上のように構成されたものにおいては、
暖房運転時には冷媒が二方弁８を介して室内熱交換器を
６０ｃ、６０ｂ、６０ａ、６０ｄの順に流れ、破線の矢
印で示したように高温のガス冷媒流は、室内熱交換器６
０ｃで室内熱交換器６０ｂと熱交換した後の空気流１５
ａと熱交換し、さらに室内熱交換器６０ｂで比較的温度
の低い空気流１５と熱交換して、室内熱交換器６０ａで
室内熱交換器６０ｂと熱交換した後の空気流１５ａと熱
交換されることによって放熱、冷却され、室内熱交換器
６０ａの出口で十分に凝縮される。次に、この凝縮した
液冷媒流は、一系統の室内熱交換器６０ｄに流入して高
速となり、管内熱伝達率が十分高くなるとともに、比較
的低温の空気流１５と熱交換して、サブクールが十分に
とれた状態になる。この場合、室内熱交換器６０ｃから
６０ｂへかけての冷媒流は、空気流１５及び空気流１５
ａと対向流となり、さらに室内熱交換器６０ａから室内
熱交換器６０ｄに流れる冷媒流も空気流１５及び１５ａ
と対向流となり、いずれの場合も効率のよい熱交換状態
となっている。In the structure constructed as described above,
During heating operation, the refrigerant flows through the two-way valve 8 through the indoor heat exchanger in the order of 60c, 60b, 60a, 60d, and as shown by the broken arrow, the high-temperature gas refrigerant flow is generated by the indoor heat exchanger 6
Air flow 15 after heat exchange with the indoor heat exchanger 60b at 0c
a, heat exchange with the air flow 15 having a relatively low temperature in the indoor heat exchanger 60b, and heat exchange with the air flow 15a after heat exchange with the indoor heat exchanger 60b in the indoor heat exchanger 60a. As a result, the heat is dissipated and cooled, and it is sufficiently condensed at the outlet of the indoor heat exchanger 60a. Next, the condensed liquid refrigerant flow flows into the indoor heat exchanger 60d of one system to have a high speed, the heat transfer coefficient in the pipe is sufficiently high, and the heat exchange is performed with the air flow 15 having a relatively low temperature to generate a subcool. Will be fully removed. In this case, the refrigerant flow from the indoor heat exchangers 60c to 60b is the air flow 15 and the air flow 15
The refrigerant flow that is a counter flow to a and that flows from the indoor heat exchanger 60a to the indoor heat exchanger 60d is also the air flows 15 and 15a.
And a counter flow, and in each case, the heat exchange state is efficient.

【００５５】又、冷房運転時には、冷媒が実線の矢印で
示すように、室内熱交換器６０ｄ、室内熱交換器６０
ａ、二方弁８、室内熱交換器６０ｂ、室内熱交換器６０
ｃの順に流れ、これら全ての室内熱交換器が蒸発器とし
て作用する。During the cooling operation, the refrigerant is the indoor heat exchanger 60d and the indoor heat exchanger 60 as indicated by the solid line arrow.
a, two-way valve 8, indoor heat exchanger 60b, indoor heat exchanger 60
Flowing in the order of c, all of these indoor heat exchangers act as an evaporator.

【００５６】除湿運転時には、冷媒が一点鎖線の矢印で
示すように、室内熱交換器６０ｄ、室内熱交換器６０
ａ、除湿湿絞り装置７、室内熱交換器６０ｂ、室内熱交
換器６０ｃの順に流れ、室内熱交換器６０ｄ、室内熱交
換器６０ａが加熱器として、室内熱交換器６０ｂ、室内
熱交換器６０ｃが冷却・除湿器として作用する。この場
合、冷却・除湿器として作用する室内熱交換器６０ｃ
は、加熱器として作用する室内熱交換器６０ａの下方に
位置するため、室内熱交換器６０ｃで生じた除湿水が、
室内熱交換器６０ａで加熱されて再び蒸発することはな
い。また、加熱器として作用する室内熱交換器６０ｄは
冷却・除湿器となる室内熱交換器６０ｂの上方に位置し
ているため、室内熱交換器６０ｂで生じた除湿水が室内
熱交換器６０ｄで加熱されて再び蒸発することもない。During the dehumidifying operation, the refrigerant is the indoor heat exchanger 60d and the indoor heat exchanger 60 as indicated by the one-dot chain line arrow.
a, the dehumidifying / humidifying expansion device 7, the indoor heat exchanger 60b, and the indoor heat exchanger 60c in this order, and the indoor heat exchanger 60d and the indoor heat exchanger 60a serve as heaters, and the indoor heat exchanger 60b and the indoor heat exchanger 60c are used. Acts as a cooler / dehumidifier. In this case, the indoor heat exchanger 60c acting as a cooling / dehumidifier
Is located below the indoor heat exchanger 60a acting as a heater, the dehumidified water generated in the indoor heat exchanger 60c is
It is not heated by the indoor heat exchanger 60a and evaporated again. Further, since the indoor heat exchanger 60d that functions as a heater is located above the indoor heat exchanger 60b that serves as a cooling / dehumidifying device, the dehumidified water generated in the indoor heat exchanger 60b is absorbed in the indoor heat exchanger 60d. It will not be heated and evaporated again.

【００５７】これまで述べたことから分かるように、図
１１において、室内熱交換器６０ｃは、必ずしも室内熱
交換器６０ａの下にある必要はなく、６８の一点鎖線で
示す位置であって室内熱交換器６０ｂの下方あるいは６
８ａの一点鎖線で示す位置であって室内熱交換器６０ａ
の風下側等も含め、風下側に室内熱交換器部分がないよ
うな位置で除湿運転時に室内熱交換器６０ｃで生じた除
湿水が加熱器となる室内熱交換器に垂れない位置なら任
意の位置におくことができる。また、室内熱交換器６０
ｄは、必ずしも室内熱交換器６０ｂの上にある必要はな
く、６９の二点鎖線で示す位置であって室内熱交換器６
０ａの上方あるいは６９ａの二点鎖線で示す位置であっ
て室内熱交換器６０ｂの前方等も含め、比較的低温の空
気流１５が直接当り除湿運転時に除湿水がかからない位
置なら任意の位置におくことができる。As can be seen from the above description, in FIG. 11, the indoor heat exchanger 60c does not necessarily have to be under the indoor heat exchanger 60a, and is located at the position indicated by the alternate long and short dash line 68 and the indoor heat Below the exchanger 60b or 6
The indoor heat exchanger 60a at the position indicated by the alternate long and short dash line 8a
Including the leeward side, etc., if the dehumidified water generated in the indoor heat exchanger 60c during the dehumidifying operation at a position where there is no indoor heat exchanger part on the leeward side does not drip into the indoor heat exchanger that is the heater, Can be placed in position. In addition, the indoor heat exchanger 60
d does not necessarily have to be on the indoor heat exchanger 60b, and is the position indicated by the two-dot chain line 69 and is the indoor heat exchanger 6
0a or a position indicated by a chain double-dashed line of 69a, including the front of the indoor heat exchanger 60b, is placed at an arbitrary position as long as the relatively low temperature air flow 15 directly hits the dehumidifying water during the dehumidifying operation. be able to.

【００５８】又、図１１においては、暖房運転時に冷媒
流の入口高温ガス域側に室内熱交換器６０ｃ、出口サブ
クール域側に室内熱交換器６０ｄの両方を設けたが、こ
れに限らずどちらか一方にしてもよく、この場合には、
室内側熱交換器６０ｃ、６０ｄのそれぞれの作用による
効果を得ることができる。Further, in FIG. 11, both the indoor heat exchanger 60c is provided on the inlet high temperature gas area side of the refrigerant flow and the indoor heat exchanger 60d is provided on the outlet subcool area side during the heating operation, but the invention is not limited to this. Either way, in this case,
The effects of the respective actions of the indoor heat exchangers 60c and 60d can be obtained.

【００５９】またさらに詳細にいえば、図９において室
内熱交換器５１ａ、５１ｂを二系統の冷媒流路にした
り、あるいは図１１において室内熱交換器６０ａ、６０
ｂ，６０ｃを二系統の冷媒流路、室内熱交換器６０ｄを
一系統の冷媒流路としたが、これに限らず、各室内熱交
換器５１ａ、５１ｂあるいは６０ａ、６０ｂ，６０ｃ，
６０ｄの冷媒流路を、冷媒流量や構成の簡単さ等から判
断して、一系統あるいは多系統にすることができる。例
えば、冷媒流量が比較的多い場合には、ガス流の混じる
室内熱交換器となる図９の５１ａ、５１ｂあるいは図１
１の６０ａ，６０ｂ，６０ｃは、圧力損失を減らすため
に複数系統の冷媒流路にした方がよく、また暖房運転時
にほとんど液流状態になる図１１の室内熱交換器６０ｄ
では、管内の流速を高めて伝熱性能を上げるために一系
統の冷媒流路にしたほうがよい。冷媒流量が比較的少な
い場合には、冷房運転時に上流側で冷媒乾き度が比較的
低い室内熱交換器となる図９の５１ａや図１１の６０ａ
を一系統の冷媒流路にしても（図示省略）、ここでの圧
力損失が比較的少なく性能の低下がほとんど問題になら
ず、しかも配管構成が簡単になる。さらに冷媒流量が少
ない場合には、すべての室内熱交換器（図９の５１ａ、
５１ｂあるいは図１１の６０ａ、６０ｂ、６０ｃ、６０
ｄ）を一系統の冷媒配管にしても（図示省略）、性能の
低下が問題にならず、配管構成がさらに簡単になる。More specifically, in FIG. 9, the indoor heat exchangers 51a and 51b are used as two-system refrigerant flow paths, or in FIG. 11, the indoor heat exchangers 60a and 60b are used.
Although b and 60c are two-system refrigerant flow paths and the indoor heat exchanger 60d is one-system refrigerant flow path, the present invention is not limited to this, and each indoor heat exchanger 51a, 51b or 60a, 60b, 60c,
The refrigerant flow path of 60d can be made into one system or multiple systems by judging from the flow rate of the refrigerant, the simplicity of the configuration, and the like. For example, when the flow rate of the refrigerant is relatively large, the indoor heat exchanger mixed with the gas flow becomes 51a, 51b in FIG. 9 or FIG.
In order to reduce the pressure loss, 60a, 60b, and 60c of No. 1 are better to be the refrigerant flow paths of plural systems, and the indoor heat exchanger 60d of FIG.
Then, in order to increase the flow velocity in the pipe and improve the heat transfer performance, it is better to use a single-system refrigerant flow path. When the flow rate of the refrigerant is relatively small, the indoor heat exchanger having a relatively low refrigerant dryness on the upstream side during the cooling operation becomes 51a in FIG. 9 or 60a in FIG.
Even if the refrigerant flow path is a single system (not shown), the pressure loss here is relatively small and the deterioration of the performance is hardly a problem, and the piping configuration is simple. Further, when the refrigerant flow rate is small, all indoor heat exchangers (51a in FIG. 9,
51b or 60a, 60b, 60c, 60 of FIG.
Even if d) is a single-system refrigerant pipe (not shown), performance degradation does not pose a problem, and the pipe configuration is further simplified.

【００６０】ところで小形の空気調和機であるルームエ
アコン等では、室内熱交換器の構造が制約されてほぼ決
まっており、配管構成等の自由度が少ないため、この点
も考慮する必要がある。以下、このような場合につい
て、図１１に示す実施例について配管列を二列にした場
合の室内熱交換器を例にとって、具体例を説明する。By the way, in a room air conditioner or the like which is a small air conditioner, the structure of the indoor heat exchanger is limited and is almost fixed, and the degree of freedom of the piping configuration and the like is small. Hereinafter, with respect to such a case, a specific example will be described by taking the indoor heat exchanger in the case where the pipe rows are two in the embodiment shown in FIG. 11 as an example.

【００６１】図１２は、配管列を二列に配管の段数を９
段に構成した場合の室内熱交換器７０の側面図であり、
室内熱交換器７の回りの配管の構成例を合わせて示して
いる。図１２において、○印で示したものは、複数枚の
放熱フィン７１を貫通するように設けられた伝熱管７
３、破線及び実線で示すものは接続配管、７、８は、図
１あるいは図１１と同様にそれぞれ除湿絞り装置、二方
弁を示す。また、室内熱交換器７０は、線７２で示す部
分で放熱フィン７１を切断することにより、二つのＬ形
熱交換器７０ａ及び７０ｂに分離されており、伝熱管７
３ａ、７３ｂは一系統の冷媒流となるように、それ以外
の伝熱管は除湿絞り装置７及び二方弁８をはさんで二系
統の冷媒流になるように配管してある。In FIG. 12, there are two rows of pipes and the number of stages of the pipes is nine.
It is a side view of the indoor heat exchanger 70 when it is configured in a tier,
The structural example of the piping around the indoor heat exchanger 7 is also shown. In FIG. 12, what is indicated by a circle is a heat transfer tube 7 provided so as to penetrate a plurality of heat radiation fins 71.
3, those indicated by broken lines and solid lines are connection pipes, and 7 and 8 are dehumidifying throttle devices and two-way valves, respectively, as in FIG. 1 or FIG. Further, the indoor heat exchanger 70 is separated into two L-shaped heat exchangers 70a and 70b by cutting the radiating fin 71 at the portion indicated by the line 72, and the heat transfer tube 7
3a and 73b have a one-system refrigerant flow, and the other heat transfer tubes are arranged so as to have a two-system refrigerant flow with the dehumidifying throttle device 7 and the two-way valve 8 interposed therebetween.

【００６２】以上のように構成することにより、冷媒流
は、冷房、暖房、除湿の各運転において、それぞれ実線
で示す矢印、破線で示す矢印、一点鎖線で示す矢印の方
向に流れる。このため、冷房運転時には全ての伝熱管が
低圧の蒸発器になるが、７３ａ、７３ｂを除く全ての伝
熱管が二系統の冷媒流になることから、圧力損失は小さ
く問題ない。又、暖房運転時には、高温ガス冷媒流は、
室内熱交換器７０の入口側で伝熱管７３ｃ、７３ｄから
それぞれ後流側の伝熱管７３ｅ、７３ｆに流れ、空気流
１５と対向流となるため、効率の良い熱交換状態が実現
でき、出口側の伝熱管である７３ｂ、７３ａの伝熱管で
は、比較的温度の低い空気流１５と風上側で熱交換する
とともに、冷媒流が一系統であるため高速になり管内の
伝熱性能が向上するため、十分なサブクールをとること
ができる。除湿運転時には、空気流１５に対して、室内
熱交換器７０ｂが風上側の冷却・除湿器（すなわち蒸発
器）、室内熱交換器７０ａが風下側の加熱器（すなわち
凝縮器）となり、空気流１５を冷却、除湿したあと再び
加熱する。この場合、切断された７２を境に高温となる
室内熱交換器７０ａと低温となる室内熱交換器７０ｂと
に分離されているため、互いの熱交換器は直接干渉しな
いため熱ロスがなく、効率の良い除湿運転を行うことが
できる。また、加熱器として作用する室内熱交換器７０
ａが、冷却・除湿器として作用する室内熱交換器７０ｂ
の上方にあり、下方に流れる除湿水が加熱されて再び蒸
発することもない。With the above structure, the refrigerant flow in the cooling, heating, and dehumidifying operations flows in the directions of the arrows indicated by the solid line, the arrows indicated by the broken line, and the arrow indicated by the alternate long and short dash line, respectively. For this reason, all the heat transfer tubes become low-pressure evaporators during the cooling operation, but since all the heat transfer tubes except 73a and 73b become the two-system refrigerant flow, the pressure loss is small and there is no problem. Also, during heating operation, the hot gas refrigerant flow is
On the inlet side of the indoor heat exchanger 70, the heat transfer tubes 73c and 73d flow to the heat transfer tubes 73e and 73f on the downstream side, respectively, and become a counterflow with the air flow 15, so that an efficient heat exchange state can be realized and the outlet side. In the heat transfer tubes 73b, 73a, which are the heat transfer tubes of No. 3, heat is exchanged on the windward side with the air flow 15 having a relatively low temperature, and since the refrigerant flow is one system, the speed is high and the heat transfer performance in the tubes is improved. , Can take enough subcool. During the dehumidification operation, the indoor heat exchanger 70b serves as a cooling / dehumidifier (ie, an evaporator) on the windward side, and the indoor heat exchanger 70a serves as a heater (ie, a condenser) on the leeward side with respect to the air flow 15. After cooling and dehumidifying No. 15, it is heated again. In this case, since the indoor heat exchanger 70a having a high temperature and the indoor heat exchanger 70b having a low temperature are separated from each other by the cut 72, there is no heat loss because the heat exchangers do not directly interfere with each other, Efficient dehumidification operation can be performed. In addition, the indoor heat exchanger 70 that functions as a heater
a is an indoor heat exchanger 70b that functions as a cooling / dehumidifier
The dehumidified water that flows above and does not evaporate again due to being heated.

【００６３】また、図１３は、伝熱管が二列で９段に配
列した図１２に示す室内熱交換器の実施例の変形例であ
り、図１２に示す実施例と比較して、暖房運転時に、冷
媒流の出口側でサブクールをとるために、冷媒流が一系
統になるようにした伝熱管７４ａ、７４ｂを一段上方側
にずらし、高温ガスの冷媒流の流入する入口伝熱管が空
気流１５に対して風上側の伝熱管７４ｃと風下側の伝熱
管７４ｄとを有する配管構成にしたものであり、９６で
示す切断線で２分割されている。この配管構成では、暖
房運転時に高温ガス域の伝熱管７４ｃとその風下側の凝
縮域の伝熱管７４ｅ、７４ｆとは、空気流１５と対向流
にならないが、除湿運転時に、冷却、除湿した後、再び
加熱する熱交換器部分の高さｈ2が、図１２に示すｈ1に
比べて長くなっており、図１２に示す実施例より多くの
除湿量をとることができる。FIG. 13 shows a modified example of the embodiment of the indoor heat exchanger shown in FIG. 12 in which the heat transfer tubes are arranged in two rows and in nine stages. Compared with the embodiment shown in FIG. At times, in order to take a subcool on the outlet side of the refrigerant flow, the heat transfer tubes 74a and 74b that are arranged so that the refrigerant flow is in one system are shifted to the upper side by one stage, and the inlet heat transfer tube into which the refrigerant flow of the high temperature gas flows is the air flow. The pipe structure has a heat transfer pipe 74c on the windward side and a heat transfer pipe 74d on the leeward side with respect to 15, and is divided into two by a cutting line indicated by 96. In this piping configuration, the heat transfer tubes 74c in the high-temperature gas region and the heat transfer tubes 74e, 74f in the condensation region on the leeward side of the pipes do not form a counter flow with the air flow 15 during the heating operation, but after cooling and dehumidifying during the dehumidifying operation. The height h 2 of the heat exchanger portion to be heated again is longer than the height h 1 shown in FIG. 12, and a larger amount of dehumidification can be obtained than in the embodiment shown in FIG.

【００６４】図１４は、伝熱管が二列で９段に配列した
図１２に示す室内熱交換器のさらに他の変形例であり、
暖房運転時に、冷媒流の出口側でサブクールをとるため
に冷媒流を一系統にした伝熱管７５ａ、７５ｂを最上段
の二列とし、高温ガスの冷媒流の流入する入口伝熱管を
空気流１５に対して両方とも風上側の伝熱管７５ｃ、７
５ｄになるように配管構成したものであり、８９で示す
位置で室内熱交換器８８を８８ａと８８ｂに二分割して
いる。この配管構成では、暖房運転時に高温ガス域の入
口伝熱管７５ｃ、７５ｄとその風下側のより温度の低い
伝熱管７５ｂ、７５ｅ、７５ｆ、７５ｇが空気流１５と
対向流にならないが、除湿運転時に、冷却、除湿したあ
と再加熱する熱交換器部分の高さｈ3が図１３に示す実
施例よりさらに長くでき、より多くの除湿量をとること
ができる。FIG. 14 shows still another modification of the indoor heat exchanger shown in FIG. 12 in which the heat transfer tubes are arranged in two rows and nine stages.
During the heating operation, the heat transfer tubes 75a and 75b in which the refrigerant flow is made into one system for taking subcool on the outlet side of the refrigerant flow are arranged in the uppermost two rows, and the inlet heat transfer tube into which the refrigerant flow of the high temperature gas flows is set to the air flow 15 On the other hand, both are heat transfer tubes 75c, 7 on the windward side.
The indoor heat exchanger 88 is divided into two parts, 88a and 88b, at a position indicated by 89. With this piping configuration, the inlet heat transfer tubes 75c, 75d in the high temperature gas region and the heat transfer tubes 75b, 75e, 75f, 75g having a lower temperature on the leeward side thereof during the heating operation do not flow counter to the air flow 15, but during the dehumidification operation. The height h 3 of the heat exchanger portion that is cooled and dehumidified and then reheated can be made longer than that of the embodiment shown in FIG. 13, and a greater amount of dehumidification can be taken.

【００６５】図１５は、伝熱管が二列で１０段に配管さ
れた室内熱交換器８０の一実施例の側面図であり、室内
熱交換器８０の回りの配管構成を合わせて示している。
図１２に示す実施例と同様に、図１５において○印で示
したものは複数枚の放熱フィン８１を貫通するように設
けた伝熱管、破線及び実線で示すものは接続配管、７、
８はそれぞれ除湿絞り装置、二方弁である。また、室内
熱交換器８０は、分離線８２により示される部分で放熱
フィン８１を切断することにより、二つのＬ形熱交換器
８０ａ及び８０ｂに分離されており、伝熱管８３ａ、８
３ｂは一系統の冷媒流、それ以外の伝熱管は除湿絞り装
置７及び二方弁８をはさんで二系統の冷媒流になるよう
に配管してある。又、Ｌ形熱交換器８０ｂは、分岐する
Ｉ点とＪ点の間が矢印８４で示す系統と矢印８５で示す
系統の二系統の冷媒配管構成としてあるが、８４で示す
系統の配管の方が８５で示す系統の配管に比べて伝熱管
の本数（この場合は、２本）が少ないため、冷媒流の流
通抵抗が同じになるように、８４で示す系統の配管にお
ける伝熱管８３ｃとＪ点の間に抵抗管８６を設けてあ
る。FIG. 15 is a side view of an embodiment of the indoor heat exchanger 80 in which the heat transfer tubes are arranged in two rows and arranged in 10 stages, and the piping configuration around the indoor heat exchanger 80 is also shown. .
Similar to the embodiment shown in FIG. 12, the circles in FIG. 15 indicate heat transfer tubes provided so as to penetrate a plurality of heat radiation fins 81, the broken lines and solid lines indicate connection pipes, 7,
Reference numeral 8 is a dehumidifying throttle device and a two-way valve, respectively. Further, the indoor heat exchanger 80 is separated into two L-shaped heat exchangers 80a and 80b by cutting the radiating fin 81 at a portion indicated by a separation line 82, and the heat transfer tubes 83a, 8
3b is a refrigerant flow of one system, and the other heat transfer pipes are arranged so as to be a refrigerant flow of two systems with the dehumidifying expansion device 7 and the two-way valve 8 interposed therebetween. Further, the L-shaped heat exchanger 80b has a two-system refrigerant piping configuration of a system shown by an arrow 84 and a system shown by an arrow 85 between the branching I point and J point. Since the number of heat transfer tubes (two in this case) is smaller than that of the system piping indicated by 85, the heat transfer tubes 83c and J in the system piping indicated by 84 and J are arranged so that the flow resistance of the refrigerant flow becomes the same. A resistance tube 86 is provided between the points.

【００６６】以上の構成により、冷媒流は、冷房、暖
房、除湿の各運転において、それぞれ実線で示す矢印、
破線で示す矢印、一点鎖線で示す矢印の方向に流れ、冷
房運転における低圧力損失の冷媒流状態、暖房運転にお
ける入口部高温ガス冷媒流と空気流との対向流による熱
交換状態および出口部での一系統の冷媒流で十分なサブ
クール化、除湿運転における空気流１５に対する冷却、
除湿と再加熱の作用を、図１２に示す実施例と同様に効
率よく、問題なく行うことができる。With the above-described structure, the refrigerant flows in the cooling, heating, and dehumidifying operations by the arrows indicated by solid lines,
Flow in the direction of the arrow indicated by the broken line, the arrow indicated by the alternate long and short dash line, the refrigerant flow state of low pressure loss in the cooling operation, the heat exchange state by the counter flow of the inlet high temperature gas refrigerant flow and the air flow in the heating operation, and the outlet portion Sufficient subcooling with one system of refrigerant flow, cooling for air flow 15 in dehumidification operation,
The operations of dehumidification and reheating can be performed efficiently and without any problem as in the embodiment shown in FIG.

【００６７】なお、抵抗管８６は、８４で示す系統の配
管におけるＩ、Ｊ点間であればどこに設けてもよい。さ
らに、複数の系統にした各冷媒流路で流通抵抗の少ない
方に抵抗管を設けて各流路の流通抵抗を等しくすること
を適用してもよい。例えば、図９あるいは図１１に示す
実施例において、複数の系統にした各冷媒流路に対し、
流通抵抗の少ない流路に抵抗管を設けて流通抵抗を等し
くし、冷媒をバランス良く流すような時に適用できる。The resistance tube 86 may be provided anywhere between points I and J in the piping of the system shown by 84. Further, it may be applied that a resistance tube is provided in one of the plurality of channels having a smaller flow resistance to equalize the flow resistance of each flow path. For example, in the embodiment shown in FIG. 9 or FIG.
The present invention can be applied to a case where a resistance tube is provided in a flow path having a small flow resistance to make the flow resistance equal and the refrigerant flows in a well-balanced manner.

【００６８】図１６は、伝熱管が二列で１０段に配列し
た図１５に示す室内熱交換器の変形例であり、暖房運転
時に、冷媒流の出口側でサブクールを取るために冷媒流
が一系統になるようにした伝熱管を８７ａ、８７ｂ、８
７ｉの３本にし、高温ガスの冷媒流の流入する入口伝熱
管が空気流１５に対して両方とも風上側の伝熱管８７
ｃ、８７ｄになるように配管構成したものであり、同様
に９７で切断されている。この配管構成では、暖房運転
時に、高温ガス域の入口伝熱管８７ｃ、８７ｄとその風
下側のより低温度の伝熱管８７ｅ、８７ｆ、８７ｇ、８
７ｈが、空気流１５に対して対向流とはならないが、除
湿運転時に、冷却、除湿したあと再加熱する熱交換器部
分の高さｈ5が図１５のｈ5より長くなり、より多くの除
湿量を取ることができる。さらにＫ点とＬ点の間の冷媒
流は二系統の流れになっているが、各系統の伝熱管の長
さは同一に設定してあり、図１５に示す実施例のような
抵抗管８６を設ける必要がなくなる。FIG. 16 is a modification of the indoor heat exchanger shown in FIG. 15 in which the heat transfer tubes are arranged in two rows and in ten stages. During the heating operation, the refrigerant flow is changed so as to take subcool on the outlet side of the refrigerant flow. 87a, 87b, 8 heat transfer tubes designed to be one system
7i, and the inlet heat transfer tubes into which the refrigerant flow of the high temperature gas flows are both windward side heat transfer tubes 87 with respect to the air flow 15.
The pipes are configured to be c and 87d, and similarly cut at 97. In this piping configuration, during the heating operation, the heat transfer tubes 87c, 87d in the high temperature gas region and the heat transfer tubes 87e, 87f, 87g, 8g having a lower temperature on the leeward side thereof are provided.
7h is, but not a counter flow against the air flow 15, during dehumidifying operation, cooling, the height h 5 of the heat exchanger portion after reheating dehumidified longer than h 5 of Figure 15, many more Dehumidifying amount can be taken. Further, the refrigerant flow between the point K and the point L is a two-system flow, but the lengths of the heat transfer tubes of each system are set to be the same, and the resistance tube 86 as in the embodiment shown in FIG. It becomes unnecessary to provide.

【００６９】なお、図１２、図１３、図１４、図１６で
示す実施例においては、除湿運転時において加熱器とな
る伝熱管の本数を冷却・除湿器となる伝熱管の本数より
多くしてあるが、これは図３、図４、図６、図８で示す
実施例で述べた暖房気味の除湿運転を行ううえで有効と
なるからである。すなわち、除湿運転において、冷却・
除湿器の能力をより低くでき、加熱器の能力をより高く
できることから、暖房気味の除湿運転がやり易くなる。In the embodiments shown in FIGS. 12, 13, 14, and 16, the number of heat transfer tubes serving as heaters during the dehumidifying operation is set to be larger than the number of heat transfer tubes serving as cooling / dehumidifiers. This is because this is effective in performing the dehumidifying operation with a slight heating effect described in the embodiments shown in FIGS. 3, 4, 6, and 8. That is, in the dehumidifying operation, cooling /
Since the capacity of the dehumidifier can be made lower and the capacity of the heater can be made higher, the dehumidifying operation that tends to be heating becomes easier.

【００７０】ここで、図１２から図１６に示す室内熱交
換器においては、二分割した両方の熱交換器とも二系統
の冷媒流路を構成しているが、これは図１１に示す実施
例で説明したように、冷媒流量が比較的多い空気調和機
の配管構成として適切なものである。冷媒流量が比較的
少ない場合には、図１２から図１６に示す実施例におい
て、冷房運転時に上流側の蒸発器となる（例えば、図１
２においては７０ａ、図１５において８０ａで示され
る）室内熱交換器を一系統の冷媒流路にすることが可能
であり、さらに冷媒流量が少ない場合には、冷房運転時
に下流側の蒸発器として作用する室内熱交換器（例え
ば、図１２においては７０ｂ、図１５においては８０ｂ
で示される）も一系統の冷媒流路にすることができる。Here, in the indoor heat exchanger shown in FIGS. 12 to 16, both of the two divided heat exchangers constitute two channels of the refrigerant passage, which is the same as the embodiment shown in FIG. As described above, it is suitable as a piping configuration of an air conditioner having a relatively large refrigerant flow rate. When the flow rate of the refrigerant is relatively low, in the embodiment shown in FIGS. 12 to 16, it becomes the evaporator on the upstream side during the cooling operation (for example, FIG.
2 is 70a, and 80a in FIG. 15) can be used as a single-system refrigerant flow path, and when the refrigerant flow rate is low, it can be used as a downstream evaporator during cooling operation. An operating indoor heat exchanger (for example, 70b in FIG. 12 and 80b in FIG. 15)
Can also be a single-system refrigerant flow path.

【００７１】一例として、図１２に示す実施例に対応し
冷媒流量が比較的少ない場合の配管構成を行った実施例
として図１７を用いて説明する。ここで、図１７は、図
１２に示す熱交換器７０ａを一系統の冷媒流路にしたも
のである。図１７において、９８は、切断線７２により
二分割し、かつ冷房運転時に上流側の蒸発器となる冷媒
流路を一系統にした熱交換器９８ａと冷房運転時に下流
側の蒸発器となる冷媒流路を二系統にした熱交換器９８
ｂ（図１２に示す７０ｂと同一）とからなる室内熱交換
器である。また、図１７において、図１２と同一番号を
付けたものは同一部分を示す。As an example, FIG. 17 will be described as an example corresponding to the example shown in FIG. 12 and having a piping configuration for a relatively small refrigerant flow rate. Here, FIG. 17 shows the heat exchanger 70a shown in FIG. 12 as a single-system refrigerant flow path. In FIG. 17, reference numeral 98 denotes a heat exchanger 98a which is divided into two parts by a cutting line 72 and which has a refrigerant flow path serving as an evaporator on the upstream side during the cooling operation in one system and a refrigerant which serves as an evaporator on the downstream side during the cooling operation. Heat exchanger 98 with two channels
b (the same as 70b shown in FIG. 12). Further, in FIG. 17, the same reference numerals as those in FIG. 12 indicate the same parts.

【００７２】以上のように構成された場合、冷媒は、冷
房、暖房、除湿の各運転において、それぞれ実線で示す
矢印、破線で示す矢印、一点鎖線で示す矢印の方向に流
れる。冷房運転時には室内熱交換器９８ａ、９８ｂとも
低圧の蒸発器になるが、冷媒流量が比較的少ないことか
ら、乾き度が低い上流側の蒸発器９８ａでは、冷媒流路
が一系統でも圧力損失が比較的少なく、逆に図１２に示
す実施例に比べて冷媒流速が速くなることから管内熱伝
達率が大きくなる。また、下流側の蒸発器７３ｂでは、
乾き度が大きくなるが、冷媒流路を二系統にしてあるた
め、冷媒流速は十分低くなり圧力損失が小さい。In the case of the above configuration, the refrigerant flows in the directions of the arrow shown by the solid line, the arrow shown by the broken line, and the arrow shown by the one-dot chain line in each operation of cooling, heating and dehumidifying. Both the indoor heat exchangers 98a and 98b are low-pressure evaporators during the cooling operation, but since the refrigerant flow rate is relatively small, the upstream evaporator 98a having a low degree of dryness causes a pressure loss even with a single refrigerant flow path. It is comparatively small, and conversely, the refrigerant flow velocity is higher than that in the embodiment shown in FIG. 12, so that the heat transfer coefficient in the pipe is large. In the evaporator 73b on the downstream side,
Although the dryness is high, the refrigerant flow rate is sufficiently low and the pressure loss is small because the refrigerant flow path has two systems.

【００７３】又、暖房運転時には、室内熱交換器９８に
おいて、冷媒流が高圧のためガス冷媒の比容積が小さく
なって流速が遅くなるが、高温ガスの冷媒流は最初に冷
媒流路が二系統の室内熱交換器９８ｂに入って凝縮し、
冷媒乾き度が十分低くなってから冷媒流路が一系統の室
内熱交換器９８ａに入るため、問題となるほどの圧力損
失は生じない。従って、冷媒流量が比較的少ない場合に
は、図１７に示す実施例では、冷房及び暖房運転とも性
能上の問題はなく、室内熱交換器９８ａの冷媒流路を一
系統にしているため、配管構成が簡単になっている。な
お、冷房運転時及び暖房運転時、さらには除湿運転時に
おける室内熱交換器９８と空気流１５との熱交換状態
は、図１２に示す実施例と同様である。Further, during the heating operation, in the indoor heat exchanger 98, since the refrigerant flow has a high pressure, the specific volume of the gas refrigerant becomes small and the flow velocity becomes slow. Enters the indoor heat exchanger 98b of the system and condenses,
Since the refrigerant flow path enters the indoor heat exchanger 98a of one system after the degree of dryness of the refrigerant becomes sufficiently low, a problematic pressure loss does not occur. Therefore, when the refrigerant flow rate is relatively small, in the embodiment shown in FIG. 17, there is no performance problem in both the cooling and heating operations, and the refrigerant flow path of the indoor heat exchanger 98a is a single system. The configuration is simple. The heat exchange state between the indoor heat exchanger 98 and the airflow 15 during the cooling operation, the heating operation, and the dehumidifying operation is the same as that of the embodiment shown in FIG.

【００７４】ここで、図１２から図１６に示す実施例に
おいては、例えば図１２に示す切断線７２や図１４に示
す切断線８９により、室内熱交換器を完全に二分割して
二つの熱交換器間の熱移動を十分に遮断し、除湿運転時
における十分な冷却・除湿及び加熱を可能にしている。
しかし、反面熱交換器の組立が複雑になるという問題が
あり、これを解決するために、伝熱管を組み込む前の放
熱フィンは、図１８及び図１９に示すように構成するの
がよい。Here, in the embodiment shown in FIGS. 12 to 16, the indoor heat exchanger is completely divided into two by the cutting line 72 shown in FIG. 12 and the cutting line 89 shown in FIG. The heat transfer between the exchangers is sufficiently blocked, enabling sufficient cooling / dehumidification and heating during dehumidification operation.
However, on the other hand, there is a problem that the assembly of the heat exchanger becomes complicated, and in order to solve this, it is preferable that the heat radiation fin before the heat transfer tube is incorporated is configured as shown in FIGS. 18 and 19.

【００７５】図１８に示す放熱フィン９１は、図１２に
示す切断線７２に相当するところに、断続状のスリット
９２設けた構造にしている。このように構成した結果、
スリット９２により、図１２に示す切断線７２よりは多
少断熱性能は劣るが、放熱フィン９１の９１ａ側と９１
ｂ側との間の熱移動を遮断でき、さらに放熱フィンの９
１ａ側と９１ｂ側がつながっているので、熱交換器を組
み立てる時にこの組立を容易にできる。The radiation fin 91 shown in FIG. 18 has a structure in which an intermittent slit 92 is provided at a position corresponding to the cutting line 72 shown in FIG. As a result of this configuration,
Due to the slit 92, the heat insulation performance is slightly inferior to that of the cutting line 72 shown in FIG.
Heat transfer between the b side can be blocked, and the heat radiation fin 9
Since the 1a side and the 91b side are connected, this assembly can be facilitated when assembling the heat exchanger.

【００７６】又、図１９に示す放熱フィン９３は、図１
４に示す切断線８９に相当するところに、断続的なスリ
ット９４を設けた構造にしている。この場合も、図１８
に示す実施例と同様に、スリット９４により、放熱フィ
ン９３の９３ａ側と９３ｂ側との間の熱移動を遮断で
き、さらに放熱フィンの９３ａ側と９３ｂ側がつながっ
ているので、熱交換器を組み立てる時にこの組立を容易
にできる。Further, the radiation fin 93 shown in FIG.
4 has a structure in which an intermittent slit 94 is provided at a position corresponding to the cutting line 89 shown in FIG. Also in this case, FIG.
Similar to the embodiment shown in FIG. 5, the slit 94 can block heat transfer between the 93a side and the 93b side of the heat radiation fin 93, and the 93a side and the 93b side of the heat radiation fin are connected, so that the heat exchanger is assembled. Sometimes this assembly can be facilitated.

【００７７】又、以上説明した実施例においては、空気
調和機でよく使用されているＨＣＦＣ２２（ハイドロク
ロロフルオロカ-ボン２２の略）等の単一冷媒を使用す
る場合について説明してきた。しかし、最近は、オゾン
層破壊や地球温暖化の点からＨＣＦＣ２２に代わる代替
冷媒の研究が盛んになっている。また、代替冷媒として
は単一冷媒だけでなく、混合冷媒の使用が検討されてい
る。このうち単一冷媒については、圧力レベルの違いは
あるが、冷凍サイクルやその特性はＨＣＦＣ２２と同様
であり、又、混合冷媒の場合にも、これまでに図１から
図１９に示す実施例で述べてきたサイクル構成、室内ユ
ニット構造、運転の制御方法、室内熱交換器の配管構成
等を適用でき、同様の効果が得られる。In the above-described embodiments, the case where a single refrigerant such as HCFC22 (abbreviation of hydrochlorofluorocarbon 22) which is often used in air conditioners is used has been described. However, recently, from the viewpoint of ozone layer depletion and global warming, research on alternative refrigerants to replace HCFC22 has become active. Further, as an alternative refrigerant, use of not only a single refrigerant but also a mixed refrigerant is being considered. Of these, the single refrigerant has the same pressure level as the refrigeration cycle, but the characteristics thereof are the same as those of the HCFC22, and even in the case of the mixed refrigerant, the embodiment shown in FIGS. The cycle configuration, the indoor unit structure, the operation control method, the piping configuration of the indoor heat exchanger, and the like described above can be applied, and similar effects can be obtained.

【００７８】又、混合冷媒を用いた場合では、一般的
に、室内熱交換器を図１１から図１７に示す配管構成に
することにより、冷房運転において、単一冷媒を用いる
場合には得られない次のような効果が得られる。In the case of using a mixed refrigerant, it is generally possible to obtain an indoor heat exchanger in the case of using a single refrigerant in the cooling operation by using the piping configuration shown in FIGS. 11 to 17. The following effects are obtained.

【００７９】図２１は、単一冷媒と混合冷媒を用いた場
合時の冷凍サイクルについて、モデル化した温度−エン
トロピ線図を示している。この温度−エントロピ-線図
において、例えば図１１に示す配管構成において冷房運
転をした場合、蒸発器として作用する室内熱交換器にお
いて、単一冷媒の場合には圧力損失のために、冷媒流の
蒸発温度が、図２１にＴａ点からＰａ点として示したよ
うに、入口から出口に向かって低下し、室内熱交換器６
０ａが高温側の蒸発器、６０ｂが低温側の蒸発器となる
ため、冷媒流と空気流１５が対向流とならない。これに
対して、混合冷媒の場合、一般的に蒸発過程で気相と液
相における混合冷媒の組成比が変化し、これに伴って図
２１にＴ点からＰ点として示したように、室内熱交換器
の入口から出口に向かって蒸発温度が上昇して行く。こ
の結果、図１１に示す実施例において、室内熱交換器６
０ａの蒸発温度の方が室内熱交換器６０ｂの蒸発温度よ
り低くなるため、冷媒流と空気流１５が対向流状態とな
り、単一冷媒の場合に比べて、より効率の良い熱交換状
態となる。FIG. 21 shows a modeled temperature-entropy diagram of the refrigeration cycle when a single refrigerant and a mixed refrigerant are used. In this temperature-entropy diagram, for example, when the cooling operation is performed in the piping configuration shown in FIG. 11, in the indoor heat exchanger that acts as an evaporator, in the case of a single refrigerant, pressure loss occurs due to pressure loss. The evaporation temperature decreases from the inlet to the outlet, as shown from Ta point to Pa point in FIG. 21, and the indoor heat exchanger 6
Since 0a is an evaporator on the high temperature side and 60b is an evaporator on the low temperature side, the refrigerant flow and the air flow 15 do not become counter flows. On the other hand, in the case of the mixed refrigerant, the composition ratio of the mixed refrigerant in the gas phase and the liquid phase generally changes in the evaporation process, and as a result, as shown from point T to point P in FIG. The evaporation temperature rises from the inlet to the outlet of the heat exchanger. As a result, in the embodiment shown in FIG. 11, the indoor heat exchanger 6
Since the evaporation temperature of 0a is lower than the evaporation temperature of the indoor heat exchanger 60b, the refrigerant flow and the air flow 15 are in a counterflow state, and the heat exchange state is more efficient than in the case of a single refrigerant. .

【００８０】なお、暖房運転においては、凝縮側では、
それぞれ図２１にＱａ点からＲａ点さらにＳａ点、Ｑ点
からＲ点さらにＳ点として示したように単一冷媒、混合
冷媒とも室内熱交換器の入口から出口に向かって冷媒温
度が下がることから、室内熱交換器での冷媒流と空気流
との温度関係は、単一冷媒の場合と混合冷媒の場合とで
は同様の温度関係となる。In the heating operation, on the condensation side,
As shown in FIG. 21 as point Qa to point Ra and point Sa, point Q to point R and point S, the refrigerant temperature decreases from the inlet to the outlet of the indoor heat exchanger for both the single refrigerant and the mixed refrigerant. The temperature relationship between the refrigerant flow and the air flow in the indoor heat exchanger has the same temperature relationship between the single refrigerant and the mixed refrigerant.

【００８１】なおこれまでは、図１のように、二分割し
た室内熱交換器６ａ、６ｂを空気流１５に対して直列
（前後）に配置する構造を想定して説明してきたが、こ
れに限らず二分割した室内熱交換器を空気流に対して並
列（上下）に配置しても、除湿運転時に同様の作用及び
効果を得る事ができる。この一実施例である冷凍サイク
ルと制御の系統を示す図を図２２に示す。この図２２に
おいて、１１０ａ、１１０ｂは二分割した室内熱交換器
であり、空気流１５に対して並列（上下）に配置してあ
る。またそれ以外は図１と同様であり、図１と同一番号
を付けたものは同一部分を表し、圧縮機１は能力制御が
可能で、室外ファン１０及び室内ファン１２は能力制御
すなわち送風量制御が可能にしてある。Up to now, the description has been made assuming the structure in which the indoor heat exchangers 6a and 6b divided into two are arranged in series (front and rear) with respect to the air flow 15 as shown in FIG. Not limited to this, even if the indoor heat exchanger divided into two is arranged in parallel (upper and lower) with respect to the air flow, the same action and effect can be obtained during the dehumidifying operation. FIG. 22 is a diagram showing a refrigerating cycle and a control system according to this embodiment. In FIG. 22, reference numerals 110a and 110b denote indoor heat exchangers divided into two and arranged in parallel (up and down) with respect to the air flow 15. 1 is the same as that in FIG. 1 except that the same reference numerals as those in FIG. 1 represent the same parts. The compressor 1 is capable of capacity control, and the outdoor fan 10 and the indoor fan 12 are capacity control, that is, air flow rate control. Is possible.

【００８２】ここで、室内ファン１２は、室内熱交換器
６ａと６ｂとを並列的に空気を流す場合を図示している
が、室内熱交換器６ａと６ｂとをくの字状に曲げて構成
し、まず室内熱交換器６ｂに空気を流し、その後室内熱
交換器６ａに空気を流すように室内ファン１２を配置す
ることができ、このように構成することにより空気の流
入および流出を行う通路を形成しやすい。Here, the indoor fan 12 illustrates the case where air is flown in parallel through the indoor heat exchangers 6a and 6b. However, the indoor heat exchangers 6a and 6b are bent in a dogleg shape. The indoor fan 12 can be arranged so that air is first allowed to flow in the indoor heat exchanger 6b and then air is allowed to flow in the indoor heat exchanger 6a. With such a structure, inflow and outflow of air Easy to form a passage.

【００８３】図２２のサイクル構成においても、図１の
サイクル構成と同様に、冷房運転時には、二方弁５を閉
じ二方弁８を開くことにより、冷媒を、実線矢印で示す
ように循環させ、室外熱交換器３を凝縮器、室内熱交換
器６ａ及び６ｂを蒸発器として室内を冷房する。暖房運
転時には、四方弁２を切り替え二方弁５を閉じ二方弁８
を開くことにより、冷媒を破線矢印で示すように循環さ
せ、室内熱交換器６ａ及び６ｂを凝縮器、室外熱交換器
１０を蒸発器として室内を暖房する。Also in the cycle configuration of FIG. 22, as in the cycle configuration of FIG. 1, during the cooling operation, the two-way valve 5 is closed and the two-way valve 8 is opened to circulate the refrigerant as shown by the solid line arrow. The outdoor heat exchanger 3 is used as a condenser, and the indoor heat exchangers 6a and 6b are used as evaporators to cool the room. During heating operation, the four-way valve 2 is switched, the two-way valve 5 is closed, and the two-way valve 8
By opening, the refrigerant is circulated as indicated by the dashed arrow, and the indoor heat exchangers 6a and 6b are used as condensers and the outdoor heat exchanger 10 is used as an evaporator to heat the room.

【００８４】又、除湿運転時には、四方弁２を冷房運転
と同様に切り換え、二方弁５を開き二方弁８を閉じるこ
とにより、冷媒を、一点鎖線で示すように圧縮機１、四
方弁２、室外熱交換器３、二方弁５、室内熱交換器１１
０ａ、除湿絞り装置７、室内熱交換器１１０ｂ、四方弁
２、アキュムレータ９、圧縮機１の順に循環させ、室外
熱交換器３を上流側の凝縮器、室内熱交換器６ａを下流
側の凝縮器、室内熱交換器６ｂを蒸発器とする。そし
て、室内空気を室内ファン１２により矢印１５のように
流すと、空気流の一部は蒸発器となる室内熱交換器１１
０ｂで冷却・除湿されると共に残りの空気流は凝縮器で
加熱器となる室内熱交換器１１０ａで加熱されて室内に
吹き出される。この場合、圧縮機１の能力や室内ファン
１２及び室外ファン１０の送風能力を制御することによ
り蒸発器１１０ｂ及び加熱器１１０ａの能力を調節する
ことができ、最終的には除湿量や吹き出し空気温度を使
用目的に合わせて制御することができる。During the dehumidifying operation, the four-way valve 2 is switched in the same manner as the cooling operation, the two-way valve 5 is opened and the two-way valve 8 is closed, so that the refrigerant is compressed by the compressor 1 and the four-way valve as shown by the one-dot chain line. 2, outdoor heat exchanger 3, two-way valve 5, indoor heat exchanger 11
0a, the dehumidification expansion device 7, the indoor heat exchanger 110b, the four-way valve 2, the accumulator 9, and the compressor 1 in this order, the outdoor heat exchanger 3 is condensed on the upstream side, and the indoor heat exchanger 6a is condensed on the downstream side. The container and the indoor heat exchanger 6b are used as an evaporator. Then, when the indoor air is made to flow by the indoor fan 12 as indicated by the arrow 15, a part of the air flow becomes the evaporator, and the indoor heat exchanger 11
While being cooled and dehumidified at 0b, the remaining air flow is heated by the indoor heat exchanger 110a that serves as a heater in the condenser and blown out into the room. In this case, the capacities of the evaporator 110b and the heater 110a can be adjusted by controlling the capacities of the compressor 1 and the blowing capacities of the indoor fan 12 and the outdoor fan 10, and finally the dehumidifying amount and the blown air temperature. Can be controlled according to the purpose of use.

【００８５】従って、除湿運転において、図２２のよう
に空気流１５に対して二分割した室内熱交換器１１０ａ
と１１０ｂを並列（上下）に並べた場合にも、図１のよ
うに空気流１５に対して二分割した室内熱交換器６ａと
６ｂを直列（前後）に並べた場合と同様な種々の運転が
可能で、図２から図４と同一の運転方法を行う事がで
き、さらに同様な効果を得る事ができる。すなわち図１
の実施例において述べた、快適除湿運転、おやすみ・お
めざめ除湿運転、カビ・ダニ防止除湿運転、ランドリー
除湿運転、等の種々の使用目的に応じた除湿運転、さら
にこれらの種々の除湿運転に応じた低風量除湿運転と高
風量除湿運転の使い分けや室温に応じて冷房気味、等温
気味あるいは暖房気味の除湿運転を行う事ができる。Therefore, in the dehumidifying operation, the indoor heat exchanger 110a divided into two parts with respect to the air flow 15 as shown in FIG.
And 110b arranged in parallel (upper and lower), the same various operations as in the case where the indoor heat exchangers 6a and 6b divided into two with respect to the air flow 15 are arranged in series (front and rear) as shown in FIG. The same operating method as in FIGS. 2 to 4 can be performed, and the same effect can be obtained. That is, FIG.
Dehumidifying operation according to various purposes such as comfortable dehumidifying operation, good night / wake up dehumidifying operation, mold / tick preventing dehumidifying operation, laundry dehumidifying operation, etc., which are described in the examples It is possible to selectively use the low air volume dehumidifying operation and the high air volume dehumidifying operation, and perform the cooling, isothermal or heating dehumidifying operation depending on the room temperature.

【００８６】ところで上記の高風量除湿運転では、圧縮
機を高能力運転にすることから入力が多くなる。この問
題を解決できる実施例を図２３に示す。図２３は、先の
図５の実施例に比べて、室内熱交換器を上下に二分割し
た場合の室内ユニットの側断面を示す図であり、１１０
ａ、１１０ｂ，１２はそれぞれ図２２のサイクル構成の
所で述べたものと同一で、それぞれ上側の室内熱交換
器、下側の室内熱交換器、室内ファンである。又図５と
同一番号を付けたものは同一部分を示す。By the way, in the above high air flow dehumidification operation, since the compressor is operated in high capacity, the input becomes large. An embodiment capable of solving this problem is shown in FIG. FIG. 23 is a view showing a side cross section of the indoor unit when the indoor heat exchanger is divided into upper and lower parts, as compared with the embodiment of FIG.
Reference numerals a, 110b, and 12 are the same as those described in the cycle configuration of FIG. 22, and are an upper indoor heat exchanger, a lower indoor heat exchanger, and an indoor fan, respectively. Further, the same parts as those in FIG. 5 are designated by the same reference numerals.

【００８７】以上の構成により、除湿運転時には室内熱
交換器６ｂが蒸発器、室内熱交換器６ａが加熱器とな
り、室内ファン１２を運転して室内空気を矢印３６から
３７のように流すことにより、空気流３６は、吸い込み
グリル３１を通り一部は蒸発器６ｂで冷却・除湿される
と共に一部は加熱器６ａで加熱されて、さらに室内ファ
ン１２を通って矢印３７の方向に吹き出される。また蒸
発器６ｂで生じた凝縮水は、露受皿３３に一旦受けられ
たのち室外へ排出される。With the above configuration, during dehumidifying operation, the indoor heat exchanger 6b serves as an evaporator and the indoor heat exchanger 6a serves as a heater, and the indoor fan 12 is operated to flow indoor air as indicated by arrows 36 to 37. The airflow 36 passes through the suction grill 31, part of which is cooled and dehumidified by the evaporator 6b, part of which is heated by the heater 6a, and is further blown through the indoor fan 12 in the direction of arrow 37. . Further, the condensed water generated in the evaporator 6b is once received by the dew tray 33 and then discharged outside the room.

【００８８】なお図２３に示す室内ユニットを用いた場
合の種々の運転方法は、先に述べた図５の室内ユニット
の場合と同一であり、高風量除湿運転の方法は図６に示
した流れ図になり、図５の実施例の場合と同様な効果を
得る事ができる。The various operating methods using the indoor unit shown in FIG. 23 are the same as those of the indoor unit shown in FIG. Thus, it is possible to obtain the same effect as that of the embodiment of FIG.

【００８９】また図２２の場合においても、図１の場合
と同様に、図７の実施例を適用し同様の効果が得られる
事は明かである。すなわち図２２の二点鎖線で囲んだ部
分４０を図７の構成にし、図８に示す暖房気味除湿運転
方法により室外熱交換器３での放熱量を調整することに
より、図２２のサイクル構成の場合よりもさらに暖房気
味の除湿運転を行う事ができる。Also in the case of FIG. 22, it is apparent that the same effect can be obtained by applying the embodiment of FIG. 7 as in the case of FIG. That is, the portion 40 surrounded by the alternate long and two short dashes line in FIG. 22 is configured as shown in FIG. 7 and the heat radiation amount in the outdoor heat exchanger 3 is adjusted by the heating dehumidifying operation method shown in FIG. It is possible to perform a dehumidifying operation slightly more like heating than in the case.

【００９０】なおこれまでの図２、図３、図４、図６、
図８に示す除湿運転時の運転方法は、図１、図７あるい
は図２２に示すサイクル構成を想定して説明してきた
が、これに限らず、室内熱交換器を二分割してその間に
除湿絞り装置を設け、除湿運転時に、二分割した室内熱
交換器のうちの冷媒流の上流側を加熱器、下流側を冷却
・除湿器とするサイクル構成を有する空気調和機に対し
ては、上述したように、室内熱交換器を前後に並べて空
気流をこれらの室内熱交換器に順に流す場合、あるいは
上下に並べて空気流をこれらの熱交換器に並列に流す場
合を含め、共通に適用することができ、同様の効果を得
ることができる。It is to be noted that FIGS.
The operating method during the dehumidifying operation shown in FIG. 8 has been described assuming the cycle configuration shown in FIG. 1, FIG. 7 or FIG. 22, but the present invention is not limited to this, and the indoor heat exchanger is divided into two and dehumidifying is performed between them. For an air conditioner that has a throttle device and has a cycle configuration in which the upstream side of the refrigerant flow of the indoor heat exchanger divided into two is a heater and the downstream side is a cooling / dehumidifier during dehumidifying operation, As described above, it is commonly applied to the case where the indoor heat exchangers are arranged in front and back to allow the airflow to flow through these indoor heat exchangers in sequence, or the case where the indoor heat exchangers are arranged vertically to allow the airflow to flow in parallel to these heat exchangers. It is possible to obtain the same effect.

【００９１】ところで図２２に示す実施例のサイクル構
成に対して除湿運転の場合を説明したが、図１のサイク
ル構成の場合と同様に、さらに冷房、暖房の各運転に対
してもサイクル性能及び室内熱交換器１１０ａ、１１０
ｂでの熱交換性能を確保して効率良く運転する必要があ
る。以下この方法について述べる。 まず図２２に示す
実施例では、室内熱交換器を１１０ａと１１０ｂに二分
割し、さらに冷房運転及び暖房運転では、これらを二方
弁８を介して直列に接続してあるため、特に冷房運転に
おいては、室内熱交換器１１０ａ及び１１０ｂとも低圧
でガス冷媒の比容積が大きく体積流量が多くなる蒸発器
となり、室内熱交換器での圧力損失が大きくなってサイ
クルの性能が低下する。The case of the dehumidifying operation has been described with respect to the cycle configuration of the embodiment shown in FIG. 22. However, as in the case of the cycle configuration of FIG. Indoor heat exchangers 110a, 110
It is necessary to ensure the heat exchange performance in b and operate efficiently. This method will be described below. First, in the embodiment shown in FIG. 22, the indoor heat exchanger is divided into 110a and 110b, and in the cooling operation and the heating operation, these are connected in series via the two-way valve 8. In the above, both the indoor heat exchangers 110a and 110b are evaporators in which the specific volume of the gas refrigerant is large and the volume flow rate is large at low pressure, resulting in a large pressure loss in the indoor heat exchanger and a reduction in cycle performance.

【００９２】この問題を解決できる一実施例を図２４に
示す。この実施例は、図２２に示す実施例において、一
点鎖線で囲んだ室内側部分１１１の熱交換器部分に相当
する。図２４において、１００ａ、１００ｂはそれぞれ
図２２の１１０ａ、１１０ｂに相当する二分割された室
内熱交換器であり、さらに室内熱交換器１００ａは、Ｐ
点で１０１と１０２の二系統の冷媒配管に分かれたあと
Ｑ点で再び一系統に合流する配管構成とし、室内熱交換
器１００ｂは、同様に、Ｒ点で１０３と１０４の二系統
の冷媒配管に分かれたあとＳ点で再び一系統に合流する
配管構成にしてある。また図２２と同一番号を付したも
のは同一部分を示す。FIG. 24 shows an embodiment capable of solving this problem. This embodiment corresponds to the heat exchanger portion of the indoor side portion 111 surrounded by the alternate long and short dash line in the embodiment shown in FIG. 24, 100a and 100b are indoor heat exchangers divided into two parts corresponding to 110a and 110b in FIG. 22, respectively, and the indoor heat exchanger 100a is P
At the point, the indoor heat exchanger 100b similarly has a two-system refrigerant pipe divided into two systems of 101 and 102 and then merges into one system at the Q point. The pipe configuration is such that after it is divided into two, it joins again into the system at point S. Further, the same parts as those in FIG. 22 are designated by the same reference numerals.

【００９３】以上の構成において、冷房運転及び暖房運
転時には、二方弁８を開くことにより、室内熱交換器１
００ａおよび１００ｂにおいて冷媒はそれぞれ二系統に
分かれて流れるため、各系統を流れる冷媒流量は半分に
なり、室内熱交換器１００ａ及び１００ｂでの冷媒流圧
力損失が低減し、性能の低下を防止できる。In the above structure, the indoor heat exchanger 1 is opened by opening the two-way valve 8 during the cooling operation and the heating operation.
Since the refrigerant flows in two systems in each of 00a and 100b, the flow rate of the refrigerant flowing in each system is halved, the refrigerant flow pressure loss in the indoor heat exchangers 100a and 100b is reduced, and the deterioration of the performance can be prevented.

【００９４】なお、図２４に示す実施例では、室内熱交
換器１００ａ及び１００ｂの冷媒配管を二系統に分けた
が、これに限らずさらに多くの系統に分けることも可能
であり、この場合も室内熱交換器１００ａ及び１００ｂ
での冷媒流圧力損失を低減し、性能の低下を防止でき
る。但し、冷媒流をあまり多系統にすると、冷媒流の圧
力損失は低下するが、熱伝達率が低下し過ぎて、冷房能
力や動作係数といった全体の性能が低下してしまうた
め、最適な系統数があり、またこの値は冷媒配管の内径
によって変化する。In the embodiment shown in FIG. 24, the refrigerant pipes of the indoor heat exchangers 100a and 100b are divided into two systems, but not limited to this, it is possible to divide into more systems, and in this case as well. Indoor heat exchangers 100a and 100b
It is possible to reduce the pressure loss of the refrigerant flow in the above and prevent the deterioration of the performance. However, if the refrigerant flow is made too multi-system, the pressure loss of the refrigerant flow will decrease, but the heat transfer coefficient will decrease too much, and the overall performance such as cooling capacity and coefficient of operation will decrease. And this value changes depending on the inner diameter of the refrigerant pipe.

【００９５】さらに暖房運転においては、暖房能力や動
作係数といった性能を向上するために、凝縮器となる室
内熱交換器において、冷媒流出口に当たる熱交換器部分
で十分サブクールが取れるようにする必要がある。これ
を実現できる一実施例を図２５に示す。図２５におい
て、１００ｃは一系統の冷媒配管１０５と点Ｔで結合し
た二系統の冷媒配管１０６、１０７から成る暖房運転時
に冷媒流の下流側となる室内熱交換器であり、また図２
４と同一番号を付けたものは同一部分を示す。すなわち
図２５の実施例は、図２４において、冷媒配管が二系統
の室内熱交換器１００ａを一系統の冷媒配管と二系統の
冷媒配管を複合した室内熱交換器１００ｃに置き換えた
ものである。Further, in the heating operation, in order to improve the performance such as the heating capacity and the coefficient of operation, in the indoor heat exchanger serving as the condenser, it is necessary to obtain sufficient subcool in the heat exchanger portion corresponding to the refrigerant outlet. is there. FIG. 25 shows an embodiment capable of realizing this. In FIG. 25, reference numeral 100c is an indoor heat exchanger that is on the downstream side of the refrigerant flow during the heating operation, which is composed of two lines of refrigerant pipes 106 and 107 that are connected to the one line of refrigerant pipe 105 at a point T.
The same number as 4 indicates the same part. That is, in the embodiment of FIG. 25, the indoor heat exchanger 100a having two systems of refrigerant pipes in FIG. 24 is replaced with an indoor heat exchanger 100c having a combination of one system of refrigerant pipes and two systems of refrigerant pipes.

【００９６】以上の構成において、暖房運転時には、冷
媒が、室内熱交換器１００ｂ、二方弁８、室内熱交換器
１００ｃの順に流れるが、この場合、破線矢印のように
入った高温のガス冷媒流は、空気流１５と熱交換して、
冷媒配管が１０３、１０４の二系統の室内熱交換器１０
０ｂから室内熱交換器１００ｃの冷媒配管が１０６、１
０７の二系統の部分で十分凝縮する。次に、この凝縮し
た液冷媒流は、室内熱交換器１００ｃの一系統の冷媒配
管１０５に入って高速となり、管内熱伝達率が十分高く
なることにより、サブクールが十分取れた状態になり
る。この結果、効率のよい熱交換状態となる。In the above structure, during the heating operation, the refrigerant flows in the order of the indoor heat exchanger 100b, the two-way valve 8 and the indoor heat exchanger 100c. The stream exchanges heat with the air stream 15,
Two-system indoor heat exchanger 10 with refrigerant pipes 103 and 104
0b to the refrigerant pipes of the indoor heat exchanger 100c are 106, 1
It is fully condensed in the two system part of 07. Next, the condensed liquid refrigerant flow enters the refrigerant pipe 105 of the one system of the indoor heat exchanger 100c to have a high speed, and the heat transfer coefficient in the pipe is sufficiently high, so that a sufficient subcool is obtained. As a result, an efficient heat exchange state is achieved.

【００９７】また、冷房運転時には、冷媒が、実線矢印
で示すように、室内熱交換器１００ｃの一系統の冷媒配
管１０５から二系統の冷媒配管１０６、１０７、二方弁
８、室内熱交換器１００ｂの二系統の冷媒配管１０３、
１０４の順に流れるが、この場合、一系統の冷媒配管１
０５では、冷媒流の乾き度が低いことから圧力損失がそ
れほどは大きくならない。さらには一系統の冷媒配管１
０５では、冷媒流の流速が速くなることから、管内熱伝
達率が高くなって伝熱性能が向上するという効果もあ
る。Further, during the cooling operation, as shown by the solid line arrow, the refrigerant flows from the refrigerant pipe 105 of one system of the indoor heat exchanger 100c to the refrigerant pipes 106 and 107 of two systems, the two-way valve 8, the indoor heat exchanger. 100b two-system refrigerant pipe 103,
Flows in the order of 104, but in this case, one line of the refrigerant pipe 1
In No. 05, the pressure loss is not so large because the dryness of the refrigerant flow is low. Furthermore, one system of refrigerant piping 1
In No. 05, since the flow velocity of the refrigerant flow is increased, there is also an effect that the heat transfer coefficient in the tube is increased and the heat transfer performance is improved.

【００９８】またさらに詳細にいえば、図２４において
室内熱交換器１００ａ、１００ｂを二系統の冷媒流路に
したり、あるいは図２５において室内熱交換器１００ｂ
を二系統の冷媒流路にすると共に室内熱交換器１００ｃ
を一系統の冷媒流路と二系統の冷媒流路を複合した流路
構成としたが、これに限らず、各室内熱交換器１００
ａ、１００ｂあるいは１００ｃの冷媒流路を、冷媒流量
や構成の簡単さ等から判断して、一系統あるいは多系統
にすることができる。例えば、冷媒流量が比較的多い場
合には、ガス流の混じる室内熱交換器となる図２４の１
００ａ、１００ｂあるいは図２５の１００ｃ、１００ｂ
は、圧力損失を減らすために複数系統の冷媒流路にした
方がよい（図２５の室内熱交換器１００ｃは一系統と複
数系統の複合でもよい）。冷媒流量が比較的少ない場合
には、冷房運転時に上流側で冷媒乾き度が比較的低い室
内熱交換器となる図２４の１００ａや図２５の１００ｃ
を一系統の冷媒流路にしても（図示省略）、ここでの圧
力損失が比較的少なく性能の低下がほとんど問題になら
ず、しかも配管構成が簡単になる。冷媒流量がさらに少
ない場合には、すべての室内熱交換器（図２４の１００
ａ、１００ｂあるいは図２５の１００ｃ、１００ｂ）を
一系統の冷媒配管にしても（図示省略）、性能の低下が
問題にならず、配管構成がさらに簡単になる。More specifically, in FIG. 24, the indoor heat exchangers 100a and 100b are used as two systems of refrigerant flow paths, or in FIG. 25, the indoor heat exchanger 100b is used.
As a two-way refrigerant flow path and the indoor heat exchanger 100c
Has a flow path configuration in which a single-system refrigerant flow path and a dual-system refrigerant flow path are combined, but the present invention is not limited to this, and each indoor heat exchanger 100
The refrigerant flow path a, 100b, or 100c can be made into one system or multiple systems by judging from the refrigerant flow rate, the simplicity of the configuration, and the like. For example, when the flow rate of the refrigerant is relatively large, the indoor heat exchanger mixed with the gas flow becomes 1 in FIG.
00a, 100b or 100c, 100b in FIG.
In order to reduce the pressure loss, it is better to use a plurality of systems of refrigerant flow paths (the indoor heat exchanger 100c in FIG. 25 may be a combination of one system and a plurality of systems). When the refrigerant flow rate is relatively low, 100a in FIG. 24 or 100c in FIG. 25 becomes an indoor heat exchanger having a relatively low refrigerant dryness on the upstream side during the cooling operation.
Even if the refrigerant flow path is a single system (not shown), the pressure loss here is relatively small and the deterioration of the performance is hardly a problem, and the piping configuration is simple. When the refrigerant flow rate is lower, all indoor heat exchangers (100 in FIG.
Even if (a, 100b or 100c, 100b in FIG. 25) is used as a single-system refrigerant pipe (not shown), the deterioration in performance does not pose a problem and the pipe configuration is further simplified.

【００９９】また図２２の冷凍サイクル内を流れる冷媒
の種類については、図１の実施例の場合と同様に、ＨＣ
ＦＣ２２等の単一冷媒あるいは種々の混合冷媒に対し
て、これまでに述べてきたサイクル構成、室内ユニット
構造、運転の制御方法、室内熱交換器の配管構成等を適
用でき、同様の効果が得られることは明かである。Regarding the type of the refrigerant flowing in the refrigeration cycle shown in FIG. 22, as in the case of the embodiment shown in FIG.
For the single refrigerant such as FC22 or various mixed refrigerants, the cycle configuration, indoor unit structure, operation control method, indoor heat exchanger piping configuration, etc. described above can be applied and similar effects can be obtained. It is clear that it will be done.

【０１００】ところでこれまでに述べた図１、図２２等
のサイクル構成における圧縮機や室内ファン、室外ファ
ンの能力制御方法として、代表的なインバータや直流モ
ータを用いて回転数制御する方式について説明してきた
が、この他にも種々の方式が考えられる。例えば、圧縮
機については、機械的に能力制御を行う方式、送風機に
ついては、交流モータのタップを切り替える方式や通風
路を絞る方式、通風抵抗を増大させる方式など種々の方
式を用いることができる。また、これまで使用されてい
る除湿運転における室内ファンの高風量は、一般的に言
って冷房運転や暖房運転時の風量と同等以下である。By the way, as a capacity control method of the compressor, the indoor fan, and the outdoor fan in the cycle configurations shown in FIGS. However, various methods other than this are conceivable. For example, various methods such as a method of mechanically controlling the capacity of a compressor, a method of switching taps of an AC motor, a method of narrowing a ventilation path, a method of increasing ventilation resistance can be used for a blower. Further, the high air volume of the indoor fan in the dehumidifying operation which has been used so far is generally equal to or less than the air volume in the cooling operation or the heating operation.

【０１０１】又、図１、図９、図１１、図１２、図１
３、図１４、図１５、図１６、図１７、図２２、図２
４、図２５に示す実施例において、これまで説明したよ
うに、主絞り装置４あるいは除湿絞り装置７としては、
キャピラリチューブのような固定絞り装置に限らず、膨
張弁や電動膨張弁のような可変絞り装置を用いることが
でき、この場合にはさらに細かい制御を行うことができ
る。特に、流通抵抗の少ない全開状態が可能な電動膨張
弁を用いた場合には、二方弁５、あるいは二方弁８が不
要となり、例えば、図１及び図２２に破線で囲んで示し
たように、並列に設けた絞り装置４と二方弁５及び絞り
装置７と二方弁８の部分４５及び４６を、図２０に示す
ように、全開可能電動膨張弁９５だけで置き換えること
ができる。Further, FIGS. 1, 9, 11, 12 and 1
3, FIG. 14, FIG. 15, FIG. 16, FIG. 17, FIG. 22, and FIG.
4, in the embodiment shown in FIG. 25, as described above, as the main expansion device 4 or the dehumidification expansion device 7,
Not only a fixed throttle device such as a capillary tube but also a variable throttle device such as an expansion valve or an electric expansion valve can be used. In this case, finer control can be performed. In particular, when an electrically driven expansion valve having a small flow resistance and capable of being fully opened is used, the two-way valve 5 or the two-way valve 8 becomes unnecessary, and for example, as shown by the broken lines in FIGS. 1 and 22. In addition, the parts 45 and 46 of the throttle device 4 and the two-way valve 5 and the throttle device 7 and the two-way valve 8 which are provided in parallel can be replaced only by the fully openable electric expansion valve 95 as shown in FIG.

【０１０２】又、これまでは冷房、暖房、除湿の三つの
運転状態が可能な冷凍サイクルについて説明してきた
が、本発明はこれに限るものではなく、他の冷凍サイク
ルについてもこれまでに説明してきた運転方法及び室内
熱交換器の構成を適用できる。例えば、図１あるいは図
２２に示す実施例において、四方弁２を取り去り、圧縮
機１とアキュムレータ９を、室内熱交換器６ｂあるいは
１１０ｂ、アキュムレータ９、圧縮機１、室外熱交換器
３が直列になるように接続した（図示せず）場合には、
実線の矢印で示す冷媒流れの冷房運転と一点鎖線で示す
冷媒流れの除湿運転が可能な冷凍サイクルとなる。この
ような冷凍サイクルの除湿運転において、図２、図３、
図４に示す運転方法、図５あるいは図２３に示す室内ユ
ニット構造における図６に示す運転方法あるいは図７に
示す実施例における図８に示す運転方法を行うことによ
り、同様の効果を得ることができる。Although the refrigerating cycle capable of operating in three cooling, heating and dehumidifying states has been described above, the present invention is not limited to this, and other refrigerating cycles have been described so far. The operating method and the configuration of the indoor heat exchanger can be applied. For example, in the embodiment shown in FIG. 1 or 22, the four-way valve 2 is removed and the compressor 1 and the accumulator 9 are connected in series with the indoor heat exchanger 6b or 110b, the accumulator 9, the compressor 1, and the outdoor heat exchanger 3. When connected as shown in the figure (not shown),
The refrigeration cycle enables the cooling operation of the refrigerant flow indicated by the solid arrow and the dehumidifying operation of the refrigerant flow indicated by the alternate long and short dash line. In the dehumidifying operation of such a refrigeration cycle, as shown in FIGS.
The same effect can be obtained by performing the operating method shown in FIG. 4, the operating method shown in FIG. 6 in the indoor unit structure shown in FIG. 5 or 23, or the operating method shown in FIG. 8 in the embodiment shown in FIG. it can.

【０１０３】さらに、図１及び図２２等の冷凍サイクル
の構成において、アキュムレータは必ずしも必要ではな
く、使用する圧縮機の種類あるいは主絞り装置の種類や
制御方法によってはアキュムレータ無しの冷凍サイクル
構成とすることができる。Further, in the refrigeration cycle configuration shown in FIGS. 1 and 22, an accumulator is not always necessary, and a refrigeration cycle configuration without an accumulator may be used depending on the type of compressor used, the type of main expansion device and the control method. be able to.

【０１０４】次に本発明による除湿運転を中心としたさ
らに具体的な運転方法の一実施例を図２６、図２７、図
２８及び図２９を用いて説明する。Next, an example of a more specific operation method centering on the dehumidifying operation according to the present invention will be described with reference to FIGS. 26, 27, 28 and 29.

【０１０５】図２６は、サイクル系統図と各部の温度セ
ンサ（代表的なものはサーミスタである）や湿度検出手
段（代表的なものは湿度センサであり、さらには温度か
ら演算によって推定する場合もある）の位置を示す図で
ある。除湿運転時、圧縮機２０１より吐出された冷媒は
四方弁２０２、室外熱交換器２０３、バイパス用二方弁
（代表的なものは電磁弁）２０６を通り加熱器となる室
内熱交換器２０８に入り、更に除湿用絞り装置２１９で
減圧され、蒸発器となる室内熱交換器２０９を通り、再
び圧縮機２０１に戻る。又、室外ユニットには、外気温
度を検出する外気温センサ２１５が、室内ユニットに
は、湿度を検出する湿度センサ２１６、吸込空気温度を
検出する室内吸込温度センサ２１７、吹出空気温度を検
出する室内吹出温度センサ２１８が設けられている。こ
れらの温度センサ及び湿度センサは、制御部（図示省
略）に接続されている。FIG. 26 shows a cycle system diagram and temperature sensors (representative ones are thermistors) and humidity detecting means (representative ones are humidity sensors) of respective parts, and when temperature is estimated by calculation. FIG. During the dehumidifying operation, the refrigerant discharged from the compressor 201 passes through a four-way valve 202, an outdoor heat exchanger 203, a bypass two-way valve (a typical one is a solenoid valve) 206, and is supplied to an indoor heat exchanger 208 serving as a heater. After entering, it is further decompressed by the dehumidifying expansion device 219, passes through the indoor heat exchanger 209 serving as an evaporator, and returns to the compressor 201 again. Further, the outdoor unit has an outdoor air temperature sensor 215 that detects the outdoor air temperature, the indoor unit has a humidity sensor 216 that detects the humidity, an indoor intake temperature sensor 217 that detects the intake air temperature, and an indoor air temperature sensor that detects the blown air temperature. An outlet temperature sensor 218 is provided. These temperature sensor and humidity sensor are connected to a control unit (not shown).

【０１０６】本発明の制御方法の一実施例を図２７、図
２８を用いて説明する。図２７は、外気温センサ２１５
で検出した温度に対し、室外ファン２１１の制御方法を
示している。室外温度が低くなると、室外熱交換器２０
３で放熱される熱量が大となり、除湿運転時の加熱量が
少なくなり、室内吹出空気温度が低くなってしまうた
め、室外温度が下がった場合、室外ファン２１１の回転
数を低下させ室内吹出空気温度が低下することを防止す
る。又、室外ユニット側に電気品を具備し、室外ファン
２１１を運転することにより、室外ユニット側電気品の
温度上昇を防止する構造となっている室外ユニットで
は、室外温度が上昇すると、室外ユニット側電気品の温
度上昇も大きくなるため、室外温度の上昇に合わせて、
室外ファン２１１の回転数を上昇させ電気品の温度上昇
を低下させる。An embodiment of the control method of the present invention will be described with reference to FIGS. 27 and 28. FIG. 27 shows an outside air temperature sensor 215.
The control method of the outdoor fan 211 is shown with respect to the temperature detected by (3). When the outdoor temperature becomes low, the outdoor heat exchanger 20
Since the amount of heat radiated in 3 becomes large, the heating amount in the dehumidifying operation becomes small, and the temperature of the indoor blown air becomes low. Therefore, when the outdoor temperature drops, the rotation speed of the outdoor fan 211 is reduced and the indoor blown air is reduced. Prevents the temperature from dropping. In addition, in the outdoor unit having the structure in which the outdoor unit side is provided with electric components and the outdoor fan 211 is operated to prevent the temperature rise of the outdoor unit side electric components, when the outdoor temperature rises, the outdoor unit side Since the temperature rise of electrical products will also be large, as the outdoor temperature rises,
The number of rotations of the outdoor fan 211 is increased to reduce the temperature rise of the electric products.

【０１０７】この室外温度と室外ファン２１１の回転数
との制御方法をパターン化、又は、演算式として制御部
に記憶させておき、外気温センサ２１５で検出した室外
温度により、あらかじめ制御部に記憶させておいたパタ
ーンや演算式を用いて室外ファン２１１を制御する。
又、この時、室外温度によって室外ファン２１１の回転
数を変えるだけでなく、ＯＮ−ＯＦＦの断続運転を行
い、そのＯＮ−ＯＦＦ時間の比率を室外温度に合わせ
て、変化させても同じ効果が得られる。The control method of the outdoor temperature and the rotation speed of the outdoor fan 211 is patterned or stored in the control unit as an arithmetic expression, and stored in advance in the control unit according to the outdoor temperature detected by the outside air temperature sensor 215. The outdoor fan 211 is controlled by using the pattern and the arithmetic expression that have been set.
Further, at this time, the same effect can be obtained not only by changing the rotation speed of the outdoor fan 211 depending on the outdoor temperature but also by performing intermittent operation of ON-OFF and changing the ratio of the ON-OFF time according to the outdoor temperature. can get.

【０１０８】この制御方法によれば、室外温度が低下し
た場合でも室内吹出空気温度の低下がなく、快適性を向
上させるばかりでなく、室外温度が上昇した場合には、
室外ファン２１１の回転数を上昇させることにより、室
外ユニット側に具備した電気部品の温度上昇を抑えるこ
とができ電気部品の信頼性も確保できる。According to this control method, the indoor blown air temperature does not decrease even when the outdoor temperature decreases, and not only the comfort is improved, but also when the outdoor temperature increases,
By increasing the number of rotations of the outdoor fan 211, it is possible to suppress the temperature rise of the electric components provided on the outdoor unit side, and it is possible to secure the reliability of the electric components.

【０１０９】図２８は、湿度センサ２１６で検出した湿
度に対する圧縮機１の制御方法を示している。室内湿度
が高い場合は圧縮機２０１の回転数を増加させ冷凍サイ
クル内の冷媒循環量を増やし除湿量の多い運転を行い、
室内側湿度をすばやく低下させる。又、室内湿度が低い
場合は、圧縮機２０１の回転数を下げて運転を行い効率
の良い運転とする。この室内湿度と圧縮機２０１の制御
方法をパターン化又は演算式として制御部に記憶させて
おき、湿度センサ２１６で検出した室内湿度に対して、
圧縮機２０１の回転数を制御する。FIG. 28 shows a method of controlling the compressor 1 with respect to the humidity detected by the humidity sensor 216. When the indoor humidity is high, the number of rotations of the compressor 201 is increased to increase the refrigerant circulation amount in the refrigeration cycle to perform the operation with a large amount of dehumidification,
Quickly reduce indoor humidity. Further, when the indoor humidity is low, the number of rotations of the compressor 201 is reduced to perform the operation, and the operation is performed efficiently. This indoor humidity and the control method of the compressor 201 are stored in the control unit as a pattern or as an arithmetic expression, and with respect to the indoor humidity detected by the humidity sensor 216,
The number of rotations of the compressor 201 is controlled.

【０１１０】以上、室外ファン２１１と圧縮機２０１の
回転数の運転パターンをそれぞれ検出した室外温度と室
内湿度によって制御することにより、快適で効率の良い
除湿運転を行う。As described above, a comfortable and efficient dehumidifying operation is performed by controlling the operation patterns of the rotational speeds of the outdoor fan 211 and the compressor 201 according to the detected outdoor temperature and indoor humidity.

【０１１１】この制御方法によれば、室内の湿度が高い
場合、例えば運転開始時、圧縮機２０１の回転数を最大
として、除湿能力の大きな、除湿運転を行い、部屋の湿
度をすばやく任意の湿度まで低下する。又、室内湿度が
任意の湿度まで低下してきたら、圧縮機２０１の回転数
を低下させ比較的除湿量が少なく効率の高い運転とす
る。これらの制御方法により、より快適で効率の良い除
湿運転を行うことが可能となった。According to this control method, when the indoor humidity is high, for example, when the operation is started, the number of rotations of the compressor 201 is maximized to perform the dehumidifying operation with a large dehumidifying capacity, and the humidity in the room is quickly changed to an arbitrary humidity. Falls to. Further, when the indoor humidity decreases to an arbitrary humidity, the rotation speed of the compressor 201 is decreased to perform a highly efficient operation with a relatively small amount of dehumidification. With these control methods, more comfortable and efficient dehumidification operation can be performed.

【０１１２】本発明のもう一つの制御方法を図２９を用
いて説明する。Another control method of the present invention will be described with reference to FIG.

【０１１３】一つは室内吹出温度センサ２１８と室内吸
込温度センサ２１７で検出した温度の差により室外ファ
ン２１１と圧縮機２０１の回転数を制御する方法で、室
内吹出空気温度が室内吸込空気温度より低下した場合室
外ファン２１１の回転数を低下させ室外ユニット側での
放熱量を少なくすることにより、室内吹出空気温度を上
昇させる。又、圧縮機２０１の回転数を変化させる（増
加させたり減少させたりする）ことにより、室内吹出空
気温度を変える事ができる。圧縮機２０１の回転数の増
加あるいは減少については、冷凍サイクルの室内熱交換
器２０９、加熱用熱交換器２０８及び室外熱交換器２０
３の大きさの比率によって変わってくる。（圧縮機２０
１の回転数の制御方法が実線や一点鎖線の様になる）
又、室内温度と任意に設定された温度（在室者の希望温
度）の差により、室内吹出空気温度と室内吸込空気温度
との温度差を決定する様な場合、例えば、室内温度が任
意に設定された温度より高い場合には、室内吹出空気温
度-室内吸込空気温度≦０の様な制御とし、室外ファン
２１１を比較的高い回転数とし、圧縮機２０１は適当に
制御して運転する。室内温度が任意に設定された温度よ
り低い場合は、室内吹出空気温度-室内吸込空気温度＞
０の制御とし、室外ファン２１１を低い回転数で運転
し、圧縮機２０１は適当に制御して運転する。One is a method of controlling the number of revolutions of the outdoor fan 211 and the compressor 201 by the difference between the temperatures detected by the indoor outlet temperature sensor 218 and the indoor inlet temperature sensor 217. The indoor outlet air temperature is higher than the indoor inlet air temperature. When the temperature decreases, the rotation speed of the outdoor fan 211 is decreased to reduce the heat radiation amount on the outdoor unit side, thereby increasing the indoor blown air temperature. Further, the temperature of the indoor blown air can be changed by changing (increasing or decreasing) the rotation speed of the compressor 201. Regarding the increase or decrease of the rotation speed of the compressor 201, the indoor heat exchanger 209, the heating heat exchanger 208, and the outdoor heat exchanger 20 of the refrigeration cycle are used.
It depends on the size ratio of 3. (Compressor 20
The control method of the number of rotations of 1 becomes like a solid line or a dashed line)
Further, in the case where the temperature difference between the indoor blown air temperature and the indoor suction air temperature is determined by the difference between the indoor temperature and the arbitrarily set temperature (desired temperature of the person in the room), for example, the indoor temperature is arbitrarily set. When the temperature is higher than the set temperature, the control is performed such that the indoor blown air temperature−the indoor suction air temperature ≦ 0, the outdoor fan 211 is set to a relatively high rotation speed, and the compressor 201 is appropriately controlled to operate. If the room temperature is lower than the set temperature, the room outlet air temperature-the room intake air temperature>
The control is set to 0, the outdoor fan 211 is operated at a low rotation speed, and the compressor 201 is appropriately controlled and operated.

【０１１４】これらの場合、室外ファン２１１を連続運
転するだけでなく、ＯＮ−ＯＦＦの断続運転を行い、そ
のＯＮ-ＯＦＦの時間比率を室内吹出空気温度と室内吸
込空気温度との差から決定することにより、更に効果が
ある。これら室内吹出空気温度と室内吸込空気温度との
差と、室外ファン２１１及び圧縮機２０１の運転パター
ンをあらかじめパターン化したり、演算式化して、制御
部に記憶させておく。In these cases, not only the outdoor fan 211 is continuously operated but also the ON-OFF intermittent operation is performed, and the ON-OFF time ratio is determined from the difference between the indoor blown air temperature and the indoor sucked air temperature. Therefore, it is more effective. The difference between the indoor blown air temperature and the indoor sucked air temperature and the operation patterns of the outdoor fan 211 and the compressor 201 are patterned in advance or made into an arithmetic expression and stored in the control unit.

【０１１５】これらの制御方法により、除湿運転時の快
適性をより向上することが可能となる。With these control methods, the comfort during dehumidifying operation can be further improved.

【０１１６】ここで室内温度と設定温度との温度差によ
り制御する場合の、制御部に記憶させておく室外ファン
２１１及び圧縮機２０１のパターン化する場合の運転パ
ターンの一実施例を図３２に示す。また図３２の各ブロ
ックには除湿運転モードだけでなく冷房運転及び暖房運
転のモードも記載して、冷房運転、除湿運転、暖房運転
の各運転モードも室外温度及び室内温度の範囲に応じて
適切に選択できるようにしてあることから、室外温度及
び室内温度のさらに広い範囲に渡って快適な運転を行う
事ができる。FIG. 32 shows an example of an operation pattern for patterning the outdoor fan 211 and the compressor 201, which is stored in the control section when controlling by the temperature difference between the indoor temperature and the set temperature. Show. In addition, not only the dehumidifying operation mode but also the modes of the cooling operation and the heating operation are described in each block of FIG. 32, and the operation modes of the cooling operation, the dehumidification operation, and the heating operation are appropriate according to the range of the outdoor temperature and the indoor temperature. Therefore, comfortable driving can be performed over a wider range of the outdoor temperature and the indoor temperature.

【０１１７】図３２においては横軸に室外温度、縦軸に
室内温度（室内吸込空気温度を使う事が可能）を取り、
室外温度範囲を４分割、室内温度範囲を５分割にして
〜の碁盤目状にブロック化し、各ブロックに対して一
定の運転条件とする。一定の運転条件としては、冷房・
除湿・暖房の運転モード、室外ファンの運転パターン、
圧縮機の運転パターン等である。このうち室外ファン２
１１の運転パターンとしては、図２７や図２９に示した
段階的回転速度におけるある回転速度での連続運転、Ｏ
Ｎ−ＯＦＦの時間比率を適当に変えた断続運転、さらに
はこれらの連続運転と断続運転の複合等、さまざまな運
転パターンがある。また圧縮機２０１の運転パターンに
ついても図２８や図２９に示した段階的回転速度におけ
る回転速度での連続運転、ＯＮ−ＯＦＦの時間比率を適
当に変えた断続運転、さらにはこれらの連続運転と断続
運転の複合等、さまざまな運転パターンがある。特に室
外ファンや圧縮機において回転数が２?３種類しか変え
られないような場合においても、これらの連続運転とＯ
Ｎ−ＯＦＦの時間比率をさまざまに変える事により多く
の運転パターンを設定する事ができる。In FIG. 32, the horizontal axis represents the outdoor temperature, and the vertical axis represents the indoor temperature (indoor intake air temperature can be used).
The outdoor temperature range is divided into four, and the indoor temperature range is divided into five, and the blocks are divided into blocks in a grid pattern of to make constant operating conditions for each block. The constant operating conditions are:
Dehumidification / heating operation mode, outdoor fan operation pattern,
The operation pattern of the compressor and the like. Of these, outdoor fan 2
As the operation pattern of 11, the continuous operation at a certain rotation speed in the stepwise rotation speed shown in FIG. 27 or 29, O
There are various operation patterns such as intermittent operation in which the N-OFF time ratio is appropriately changed, and further a combination of continuous operation and intermittent operation. Also regarding the operation pattern of the compressor 201, continuous operation at the rotation speed at the stepwise rotation speed shown in FIG. 28 and FIG. 29, intermittent operation in which the ON-OFF time ratio is appropriately changed, and further continuous operation There are various driving patterns such as intermittent driving. Even when the number of revolutions of an outdoor fan or compressor can be changed by only a few types, continuous operation and O
Many operation patterns can be set by changing the N-OFF time ratio variously.

【０１１８】そしてこれらの室外ファンあるいは圧縮機
における運転パターン、及び冷房・除湿・暖房の運転モ
ードを、図３２の各ブロックごとに、このブロックに対
応する室外温度及び室内温度に合わせて設定する。この
結果実際の運転においては、温度センサにより外気温度
や室内温度が検出されると、これらの検出された温度が
含まれる図３２のブロックに応じた（冷房・除湿・暖房
の）運転モード、室外ファンの運転パターン、圧縮機の
運転パターンで運転され、例えば?のブロックでは冷房
気味除湿運転となる。この結果、快適な運転を行う事が
できる。The operation patterns of these outdoor fans or compressors and the cooling / dehumidifying / heating operation modes are set for each block in FIG. 32 in accordance with the outdoor temperature and the indoor temperature corresponding to this block. As a result, in the actual operation, when the temperature sensor detects the outside air temperature and the indoor temperature, the operation mode (for cooling / dehumidifying / heating) according to the block of FIG. 32 including the detected temperature, the outdoor The operation is performed according to the operation pattern of the fan and the operation pattern of the compressor. For example, in block? As a result, comfortable driving can be performed.

【０１１９】なお室外温度及び室内温度の分割は必ずし
も図３２のようにする必要は無く、必要に応じて一個以
上適切に分割する事ができる。It is not always necessary to divide the outdoor temperature and the indoor temperature as shown in FIG. 32, and one or more can be appropriately divided as necessary.

【０１２０】又、室内温度と設定温度との温度差あるい
は室内吹出空気温度と室内吸込空気温度との温度差と、
室外ファン２１１及び圧縮機２０１の運転パターンとの
関係を演算式化して制御部に記憶させておく場合には、
さらにきめ細かい制御が可能になり、この制御方法は、
特に室外ファンや圧縮機の能力が連続制御可能な場合に
対して有効である。Further, the temperature difference between the room temperature and the set temperature or the temperature difference between the room blown air temperature and the room intake air temperature,
When the relation between the outdoor fan 211 and the operation pattern of the compressor 201 is calculated and stored in the control unit,
It enables finer control, and this control method
This is especially effective when the capabilities of the outdoor fan and compressor can be continuously controlled.

【０１２１】また室内温度あるいは室内湿度の設定値
を、例えば前に述べたＰＭＶ等の温熱環境評価手法に基
づいて決定するようにする事もでき、この場合にはより
快適な運転を自動的に行う事ができる。このような除湿
運転を行うことにより、体感温度のよい除湿運転が行え
る。It is also possible to determine the set value of the room temperature or the room humidity on the basis of the thermal environment evaluation method such as PMV described above. In this case, more comfortable driving is automatically performed. I can do it. By performing such a dehumidifying operation, a dehumidifying operation with a good sensible temperature can be performed.

【０１２２】ところでこれまでは湿度検出手段として湿
度センサを想定して説明してきたが、湿度センサは比較
的高価である事からサーミスタ等の安価な温度センサを
用いて簡易的に湿度を推定する事も行われる。特に室内
温度と熱交換器の蒸発温度と室内湿度の間には相関関係
があり、この関係を前もって実験的に求めておき、（精
度は落ちるが）室内温度と蒸発温度から湿度を求める事
ができる。またこの関係は湿度が目標値まで下がった場
合に運転を停止する場合等に有効に使用する事ができ
る。これまでの経験から、例えば室内湿度が約５０％と
なった時の室内温度Ｔ1と蒸発温度Ｔ2との間には、Ａ、
Ｂを定数として、次のような関係がある。Up to now, the description has been made assuming the humidity sensor as the humidity detecting means, but since the humidity sensor is relatively expensive, the humidity can be easily estimated by using an inexpensive temperature sensor such as a thermistor. Is also done. In particular, there is a correlation between the indoor temperature, the evaporation temperature of the heat exchanger, and the indoor humidity. It is possible to obtain this relationship experimentally in advance and obtain the humidity from the indoor temperature and the evaporation temperature (although the accuracy may drop). it can. Further, this relationship can be effectively used when the operation is stopped when the humidity drops to the target value. From the experience so far, for example, between the indoor temperature T 1 and the evaporation temperature T 2 when the indoor humidity becomes about 50%, A,
There is the following relationship with B as a constant.

【０１２３】Ｔ2＝Ａ×Ｔ1-Ｂ従って、温度センサによ
り室内温度と蒸発温度を検出して、蒸発温度が室内温度
Ｔ1に対応した室内湿度５０％の時の温度Ｔ2に成った
ら、運転を止める様な湿度制御を行う事ができる。この
場合、適切な湿度は５０％前後といわれており、また温
度の場合ほど敏感ではないため、こうした湿度制御でも
十分実用的である。しかも湿度センサを使う場合に比べ
て安価に実現できる。T 2 = A × T 1 -B Therefore, if the room temperature and the evaporation temperature are detected by the temperature sensor and the evaporation temperature reaches the temperature T 2 when the room humidity is 50% corresponding to the room temperature T 1 , The humidity can be controlled so that the operation is stopped. In this case, an appropriate humidity is said to be around 50%, and it is not as sensitive as temperature, so that such humidity control is sufficiently practical. In addition, it can be realized at a lower cost than when using a humidity sensor.

【０１２４】なお、これまでに述べてきたすべての実施
例は一般の建屋に用いられる空気調和機を想定して説明
してきたが、本発明はこれに限らず、除湿運転が必要な
他の用途の装置にも適用可能である。こうした場合、一
般に室内熱交換器を利用側熱交換器、室外熱交換器を熱
源側熱交換器、又、室内ファンを利用側ファン、室外フ
ァンを熱源側ファンといいかえることができる。Although all the embodiments described so far have been described on the assumption of an air conditioner used in a general building, the present invention is not limited to this, and other applications requiring dehumidifying operation are also possible. It is also applicable to the device. In such a case, generally, the indoor heat exchanger can be called the use side heat exchanger, the outdoor heat exchanger can be called the heat source side heat exchanger, the indoor fan can be called the use side fan, and the outdoor fan can be called the heat source side fan.

【０１２５】以上説明した各実施例を纏めて説明する
と、次の通りである。The respective embodiments described above will be summarized and described as follows.

【０１２６】上記実施例における目的は、種々の使用目
的の除湿運転ができる空気調和機を提供することにあ
る。The object of the above embodiment is to provide an air conditioner capable of dehumidifying operation for various purposes.

【０１２７】また、別の目的は、除湿運転を行うととも
に、冷房運転や暖房運転での性能を十分高性能に保てる
空気調和機を提供することにある。Another object of the present invention is to provide an air conditioner which can perform dehumidifying operation and can maintain sufficiently high performance in cooling operation and heating operation.

【０１２８】また、別の目的は、室外温度が変化しても
室内吹出空気温度や除湿量が所定の温度及び除湿量を確
保し、室内湿度をすばやく設定湿度にできる空気調和器
を提供する事にある。Another object of the present invention is to provide an air conditioner in which the indoor air temperature and the dehumidifying amount can be kept at a predetermined temperature and dehumidifying amount even if the outdoor temperature changes, and the indoor humidity can be quickly set to the set humidity. It is in.

【０１２９】また、別の目的は、室外ユニット側の電気
部品の温度が過度に高くならず十分な寿命を保てる空気
調和機を提供する事にある。Another object is to provide an air conditioner in which the temperature of the electric components on the outdoor unit side does not rise excessively and a sufficient life can be maintained.

【０１３０】上記１番目の目的を達成するために、上記
実施例の空気調和機は、少なくとも圧縮機と室内熱交換
器と絞り装置と室外熱交換器を備えた空気調和機におい
て、前記室内熱交換器が冷却・除湿部分と加熱部分とを
有し、除湿運転時に前記圧縮機の能力、室内熱交換器の
ファンの風量、室外熱交換器のファンの風量の制御を行
うことにより前記加熱部分の加熱能力、前記室外熱交換
器の放熱量を制御するものである。In order to achieve the first object, the air conditioner of the above embodiment is an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger. The exchanger has a cooling / dehumidifying portion and a heating portion, and the heating portion is controlled by controlling the capacity of the compressor, the air volume of the fan of the indoor heat exchanger, and the air volume of the fan of the outdoor heat exchanger during dehumidifying operation. The heating capacity and the heat radiation amount of the outdoor heat exchanger are controlled.

【０１３１】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が熱的に分割された冷却・除湿部分と加
熱部分と該冷却・除湿部分と加熱部分との間に設けられ
た第２の絞り装置を有するとともに、室内温度センサに
より検出された温度を入力する制御回路を有するもので
あって、該制御回路により前記圧縮機の能力、室内熱交
換器のファンの風量、室外熱交換器のファンの風量を制
御して冷房気味、等温気味、暖房気味の各除湿運転制御
を行うものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into a cooling / dehumidifying part and a heating part. A compressor having a second expansion device provided between a cooling / dehumidifying portion and a heating portion, and a control circuit for inputting a temperature detected by an indoor temperature sensor. , The air flow rate of the fan of the indoor heat exchanger, and the air flow rate of the fan of the outdoor heat exchanger to control the dehumidifying operation such as cooling, isothermal, and heating.

【０１３２】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、除
湿運転として快適除湿運転、おやすみ・おめざめ除湿運
転、カビ・ダニ防止除湿運転、ランドリー除湿運転等の
各運転モードを備えるものであって、おやすみ・おめざ
め除湿運転時には前記室内熱交換器のファンの風量を低
下させ、ランドリ-運転時には前記室内熱交換器のファ
ンの風量を高めた運転を行うものである。In an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, the dehumidifying operation includes a comfortable dehumidifying operation, a good night / smooth dehumidifying operation, and a mold / mite preventing dehumidifying operation. It has each operation mode such as laundry dehumidification operation, and lowers the air volume of the indoor heat exchanger fan during good night / whole night dehumidification operation, and increases the air volume of the indoor heat exchanger fan during landry operation. It is to drive the car.

【０１３３】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が室内湿度検出手段と該室内湿度検出手
段により検出された湿度を入力する制御回路を備えると
ともに、除湿運転時にダニ・カビ防止除湿運転モードを
備えるものであって、該運転モードが設定されたとき、
前記湿度検出手段により検出された湿度が４０％から６
０％の範囲になるように前記制御回路により、前記圧縮
機の能力、室内熱交換器のファンの風量、室外熱交換器
のファンの風量の制御を行うものである。Further, in an air conditioner having at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, the indoor heat exchanger has an indoor humidity detecting means and a humidity detected by the indoor humidity detecting means. In addition to having a control circuit for inputting, a dehumidification / duration prevention dehumidification operation mode is provided during dehumidification operation, and when the operation mode is set,
The humidity detected by the humidity detecting means is 40% to 6%.
The control circuit controls the capacity of the compressor, the air volume of the fan of the indoor heat exchanger, and the air volume of the fan of the outdoor heat exchanger so that the range is 0%.

【０１３４】又、前記湿度検出手段により検出された湿
度が約５０％になるように前記制御回路により、前記圧
縮機の能力、室内熱交換器のファンの風量、室外熱交換
器のファンの風量の制御を行うものである。Further, the control circuit controls the capacity of the compressor, the air volume of the fan of the indoor heat exchanger, and the air volume of the fan of the outdoor heat exchanger so that the humidity detected by the humidity detecting means becomes about 50%. Is to control.

【０１３５】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が冷却・除湿部分と加熱部分とを有する
とともに、室内温度センサにより検出された室温を入力
する制御回路を有し、該検出された室温と設定温度との
差が負と判断された時は、前記制御回路により室外熱交
換器の放熱量を低下させ、前記加熱部分の加熱能力を増
大させるように運転制御するものである。Further, in the air conditioner having at least the compressor, the indoor heat exchanger, the expansion device and the outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion, and an indoor temperature sensor. By having a control circuit for inputting the room temperature detected by, when the difference between the detected room temperature and the set temperature is determined to be negative, the control circuit reduces the heat radiation amount of the outdoor heat exchanger, The operation is controlled so as to increase the heating capacity of the heating portion.

【０１３６】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を具備した室内ユニットが室内空気を流
入させるための通風路が設けられ、かつ該通風路の開閉
を行うダンパの様な開閉口を具備するものであって、室
内ユニットを通る空気流を室内熱交換器を通過するもの
と室内熱交換器を通らず前記通風路を通過するものとの
二系統設け、除湿運転時において、室内ファンを低風量
にした場合には、圧縮機を低能力から高能力に制御する
とともに室外ファンを高風量から低風量に制御すること
により、室内ファンを高風量にする場合には、室内熱交
換器を通過する空気流と前記通風路に設けた開閉口を開
いて室内熱交換器を通らず通風路を通る空気流との両方
を合わせて高風量とし、さらに圧縮機能力を下げた状態
で低能力から高能力に制御すると共に室外ファンを高風
量から低風量に制御することにより、冷房気味、等温気
味、暖房気味の広い温度範囲にわたって低風量除湿運転
あるいは高風量除湿運転を行うものである。In an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, an indoor unit equipped with the indoor heat exchanger has a ventilation path for inflowing indoor air. An air flow that is provided and has an opening and closing port such as a damper that opens and closes the ventilation passage, and that allows the air flow passing through the indoor unit to pass through the indoor heat exchanger and the ventilation not passing through the indoor heat exchanger. When the indoor fan is set to a low air volume during dehumidification operation, the compressor is controlled from low capacity to high capacity and the outdoor fan is controlled from high air capacity to low air capacity during dehumidification operation. Thus, when the indoor fan has a high air flow, the air flow passing through the indoor heat exchanger and the air flow passing through the ventilation passage without opening the opening / closing port provided in the ventilation passage High air volume by combining both In addition, by controlling from low capacity to high capacity with the compression function lowered and controlling the outdoor fan from high air volume to low air volume, low air volume dehumidification over a wide temperature range such as cooling, isothermal, and heating. The operation is performed or a high air flow dehumidification operation is performed.

【０１３７】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を具備した室内ユニットが室内空気を流
入させるための通風路が設けられ、かつ該通風路の開閉
を行う開閉口を具備するものであって、室内温度センサ
により検出された室温と設定温度との差がほぼ零の時
は、開閉口を開き、室内温度センサにより検出された室
温と設定温度との差が負の時は開閉口を閉じるように制
御するものである。Further, in an air conditioner having at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, an indoor unit having the indoor heat exchanger has a ventilation path for inflowing indoor air. The indoor temperature sensor is provided and has an opening / closing port for opening / closing the ventilation passage, and when the difference between the room temperature detected by the indoor temperature sensor and the set temperature is substantially zero, the opening / closing port is opened. When the difference between the room temperature and the set temperature detected by is negative, the opening / closing port is controlled to be closed.

【０１３８】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が冷却・除湿部分と加熱部分とを有し、
かつ室外熱交換器が二方弁を備えたバイパス管を設けた
ものであって、室内温度センサにより検出された室温が
設定温度より低いと判断された時は、除湿運転時に前記
二方弁を開くように制御するものである。In an air conditioner having at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion,
And the outdoor heat exchanger is provided with a bypass pipe having a two-way valve, and when it is determined that the room temperature detected by the indoor temperature sensor is lower than the set temperature, the two-way valve is turned on during the dehumidifying operation. It controls to open.

【０１３９】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が熱的に分割された冷却・除湿部分と加
熱部分とを有するとともに、室内温度センサにより検出
された温度を入力する制御回路を有するものであって、
前記室内温度センサにより検出された温度と設定温度と
の差が正と判断された時は、該制御回路により室外熱交
換器のファンの風量を増大させるように制御するととも
に、室内熱交換器のファンの風量に応じて圧縮機の回転
数を制御するものである。Further, in an air conditioner having at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion which are thermally divided. In addition to having a control circuit for inputting the temperature detected by the indoor temperature sensor,
When it is determined that the difference between the temperature detected by the indoor temperature sensor and the set temperature is positive, the control circuit controls to increase the air volume of the fan of the outdoor heat exchanger and the indoor heat exchanger. The rotation number of the compressor is controlled according to the air volume of the fan.

【０１４０】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が熱的に分割された冷却・除湿部分と加
熱部分とを有するとともに、室内温度センサにより検出
された温度を入力する制御回路を有するものであって、
前記室内温度センサにより検出された温度と設定温度と
の差がほぼ零と判断された時は、該制御回路により室外
熱交換器のファンの風量を中くらいの範囲に制御すると
ともに、室内熱交換器のファンの風量に応じて圧縮機の
回転数を制御するものである。Further, in an air conditioner having at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger, the indoor heat exchanger has a cooling / dehumidifying portion and a heating portion which are thermally divided. In addition to having a control circuit for inputting the temperature detected by the indoor temperature sensor,
When it is determined that the difference between the temperature detected by the indoor temperature sensor and the set temperature is substantially zero, the control circuit controls the air volume of the fan of the outdoor heat exchanger to a medium range and the indoor heat exchange. The number of revolutions of the compressor is controlled according to the air volume of the fan of the container.

【０１４１】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が熱的に分割された冷却・除湿部分と加
熱部分とを有するとともに、室内温度センサにより検出
された温度を入力する制御回路を有するものであって、
前記室内温度センサにより検出された温度と設定温度と
の差が負と判断された時は、該制御回路により室外熱交
換器のファンの風量を低下させるように制御するととも
に、室内熱交換器のファンの風量に応じて圧縮機の回転
数を制御するものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger includes a cooling / dehumidifying part and a heating part which are thermally divided. In addition to having a control circuit for inputting the temperature detected by the indoor temperature sensor,
When it is determined that the difference between the temperature detected by the indoor temperature sensor and the set temperature is negative, the control circuit controls to reduce the air volume of the fan of the outdoor heat exchanger and the indoor heat exchanger. The rotation number of the compressor is controlled according to the air volume of the fan.

【０１４２】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器が熱的に分割された冷却・除湿部分と加
熱部分とを有するとともに、室内温度センサにより検出
された温度を入力する制御回路を有するものであって、
前記室内温度センサにより検出された温度と設定温度と
の差が負と判断された時は、設定温度となるように加熱
器の能力を制御するとともに、室内熱交換器のファンの
風量に応じて圧縮機の回転数を制御するものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger includes a cooling / dehumidifying portion and a heating portion which are thermally divided. In addition to having a control circuit for inputting the temperature detected by the indoor temperature sensor,
When it is determined that the difference between the temperature detected by the indoor temperature sensor and the set temperature is negative, the capacity of the heater is controlled so as to reach the set temperature, and according to the air volume of the fan of the indoor heat exchanger. It controls the rotation speed of the compressor.

【０１４３】又、前記室内熱交換器のファンの風量を低
風量に設定した時は、前記圧縮機の能力を低下させるよ
うに制御するものである。又、前記室内熱交換器のファ
ンの風量を高風量に設定した時は、前記圧縮機の能力を
増大させるように制御するものである。Further, when the air volume of the fan of the indoor heat exchanger is set to a low air volume, the capacity of the compressor is controlled to be reduced. Further, when the air volume of the fan of the indoor heat exchanger is set to a high air volume, control is performed so as to increase the capacity of the compressor.

【０１４４】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、室
外温度を検出する検出手段と、該検出手段からの信号に
応じて室外ファンモータの回転数を制御する手段と、室
内温度を検出する手段からの信号に応じて圧縮機の回転
数を制御する手段とを備え、室温と除湿能力を制御する
ものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, a detecting means for detecting an outdoor temperature and an outdoor fan motor according to a signal from the detecting means. And a means for controlling the number of revolutions of the compressor in response to a signal from the means for detecting the room temperature, to control the room temperature and the dehumidification capacity.

【０１４５】又、室内熱交換器が冷却器と加熱器とより
なる除湿機能を有する空気調和機において、室外ファン
モータの回転数を制御する手段と圧縮機の回転数を制御
する手段を備え、室外ファンモータの回転数と圧縮機の
回転数を制御して室温と除湿能力を制御するものであ
る。Further, in the air conditioner having the dehumidifying function in which the indoor heat exchanger is composed of the cooler and the heater, it is provided with means for controlling the rotation speed of the outdoor fan motor and means for controlling the rotation speed of the compressor, The temperature of the outdoor fan motor and the speed of the compressor are controlled to control the room temperature and the dehumidifying ability.

【０１４６】又、室内熱交換器が冷却器と加熱器とより
なる除湿機能を有する空気調和機において、室内温度制
御とは独立に室内熱交換器の除湿能力を体感温度がほぼ
一定に保ちながら制御する手段を有するものである。Further, in the air conditioner having the dehumidifying function in which the indoor heat exchanger is composed of the cooler and the heater, the dehumidifying capacity of the indoor heat exchanger is kept substantially constant regardless of the indoor temperature control. It has a means for controlling.

【０１４７】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、除
湿運転として、おやすみ運転、カビ、ダニ防止運転の各
運転モードを備えるものであって、前記室外熱交換器の
ファンの風量および圧縮機の回転数を段階的に制御する
ことにより、室温と除湿能力を制御するものである。An air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device, and an outdoor heat exchanger is provided with each operation mode of a good night operation, a mold operation, and a tick prevention operation as a dehumidifying operation. Then, the room temperature and the dehumidifying capacity are controlled by stepwise controlling the air flow rate of the fan of the outdoor heat exchanger and the rotation speed of the compressor.

【０１４８】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、室
外温度を検出する検出手段と、該検出手段からの信号に
応じて圧縮機の回転数を制御する手段と、室内温度を検
出する手段からの信号に応じて圧縮機の回転数を制御す
る手段を備え、設定温度に室温を近ずけるように制御す
るとともに、湿度が４０から６０％の範囲となるように
除湿能力を制御するものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, a detecting means for detecting an outdoor temperature and a compressor of the compressor in response to a signal from the detecting means. A means for controlling the number of rotations and a means for controlling the number of rotations of the compressor in response to a signal from the means for detecting the indoor temperature are provided, and the room temperature is controlled to approach the set temperature, and the humidity is controlled from 40. The dehumidifying ability is controlled so as to be in the range of 60%.

【０１４９】又、前記快適除湿運転、カビ・ダニ防止除
湿運転、おやすみ・おめざめ除湿運転、ランドリー除湿
運転のいずれかの運転モードにおいて、運転モードに適
した温度及び湿度を予め記憶しておくとともに、温度セ
ンサおよび湿度センサにより温度および湿度を検出し、
該検出した温度及び湿度が記憶されている温度及び湿度
に合致するように前記制御装置により除湿運転を行うよ
うにしたものである。In any one of the comfortable dehumidifying operation, the mold / mite preventing dehumidifying operation, the good night / sleeping dehumidifying operation, and the laundry dehumidifying operation, the temperature and humidity suitable for the operating mode are stored in advance. , Temperature sensor and humidity sensor to detect temperature and humidity,
The dehumidifying operation is performed by the control device so that the detected temperature and humidity match the stored temperature and humidity.

【０１５０】又、前記室内熱交換器の冷却・除湿部分が
加熱部分より風上側に設けられているものである。Further, the cooling / dehumidifying portion of the indoor heat exchanger is provided on the windward side of the heating portion.

【０１５１】又、前記室内熱交換機の加熱部分が冷却・
除湿部分の上側に設けられているものである。Further, the heating part of the indoor heat exchanger is cooled and
It is provided above the dehumidifying portion.

【０１５２】又、前記快適除湿運転が、ＰＭＶの温熱環
境評価手法に基づいて制御されるものであって、該ＰＭ
Ｖがほぼ零となるように除湿運転を行うようにしたもの
である。The comfortable dehumidifying operation is controlled on the basis of the PMV thermal environment evaluation method.
The dehumidifying operation is performed so that V becomes almost zero.

【０１５３】又、前記圧縮機あるいは送風機が回転数制
御を行うものである。The compressor or blower controls the number of revolutions.

【０１５４】又、前記主絞り装置あるいは除湿絞り装置
が全開可能な電動膨張弁であるものである。Further, the main expansion device or the dehumidification expansion device is an electric expansion valve capable of being fully opened.

【０１５５】又、前記空気調和機に封入される冷媒が混
合冷媒であるものである。The refrigerant enclosed in the air conditioner is a mixed refrigerant.

【０１５６】又、前記温度検出手段が、２つの温度セン
サにより検出された温度により換算されるものである。
又、前記室内熱交換器からの空気の吹き出し温度が前記
設定温度より３度以内高めに制御されるものである。Further, the temperature detecting means converts the temperature detected by the two temperature sensors.
Further, the temperature at which air is blown out from the indoor heat exchanger is controlled to be higher than the set temperature by 3 degrees or less.

【０１５７】又、前記室内熱交換器の冷却器と加熱器が
上下方向に配置されているものである。Also, the cooler and the heater of the indoor heat exchanger are arranged vertically.

【０１５８】上記２番目の目的を達成するために、本発
明の空気調和機は、少なくとも圧縮機と室内熱交換器と
絞り装置と室外熱交換器を備えた空気調和機において、
前記室内熱交換器が熱的に分割された冷却・除湿部分と
加熱部分とを有するとともに、該冷却・除湿部分と加熱
部分との間に除湿運転時に使用する除湿絞り装置を設
け、前記冷却・除湿部分と加熱部分の冷媒流路がそれぞ
れ二系統以上に構成されているものである。In order to achieve the second object, the air conditioner of the present invention is an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger,
The indoor heat exchanger has a thermally divided cooling / dehumidifying portion and a heating portion, and a dehumidifying expansion device used during dehumidifying operation is provided between the cooling / dehumidifying portion and the heating portion, and the cooling / dehumidifying portion is provided. The dehumidifying part and the heating part each have two or more refrigerant flow paths.

【０１５９】又、前記二系統以上に構成した各冷媒流路
の流通抵抗が等しくなるようにいずれか一方の冷媒流路
に抵抗管を設けたものである。Further, a resistance tube is provided in one of the refrigerant passages so that the flow passage resistances of the refrigerant passages having two or more systems are equal.

【０１６０】又、前記室内熱交換器のうち冷房運転時に
上流側となる熱交換器の冷媒流路を一系統にしたもので
ある。Further, the refrigerant flow path of the heat exchanger on the upstream side during the cooling operation of the indoor heat exchanger is integrated into one system.

【０１６１】又、前記室内熱交換器のうち暖房運転時の
冷媒流出口部分を一系統の冷媒流路にしたものである。Further, in the indoor heat exchanger, the refrigerant outlet portion at the time of heating operation is a single-system refrigerant passage.

【０１６２】又、前記室内熱交換器が放熱フィンにあけ
た孔の中に伝熱管を密着させて組み込むとともにこの放
熱フィンに切断線を入れて二分割する構造にしたもので
ある。 又、前記室内熱交換器が放熱フィンにあけた孔
の中に伝熱管を密着させて組み込むとともにこの放熱フ
ィンにスリットを設けて熱的に二分割する構造にしたも
のである。Further, the indoor heat exchanger has a structure in which a heat transfer tube is closely fitted in a hole formed in the heat radiation fin and a cutting line is inserted in the heat radiation fin to divide the heat radiation tube into two parts. Further, the indoor heat exchanger has a structure in which a heat transfer tube is closely fitted into a hole formed in a heat radiation fin and a slit is provided in this heat radiation fin to thermally divide the heat radiation tube into two.

【０１６３】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を熱的に二分割して二分割されたその間
に除湿運転時に使用する除湿絞り装置を設けるととも
に、該室内熱交換器の暖房運転時の冷媒流出口部分を空
気流に最も上流側に設けたものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into two and dehumidification operation is performed between them. A dehumidifying expansion device that is sometimes used is provided, and a refrigerant outlet port during heating operation of the indoor heat exchanger is provided on the most upstream side of the air flow.

【０１６４】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を熱的に二分割して、二分割されたその
間に除湿運転時に使用する除湿絞り装置を設けるととも
に、該室内熱交換器の暖房運転時の冷媒流出口部分を、
この冷媒流出口部分の下側に室内熱交換器の他の部分が
配置されないように構成したものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttling device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into two and dehumidified between the two divided parts. While providing a dehumidifying expansion device used during operation, the refrigerant outlet portion during heating operation of the indoor heat exchanger,
The other part of the indoor heat exchanger is not arranged below the refrigerant outlet part.

【０１６５】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、室
内熱交換器を熱的に二分割して、二分割されたその間に
除湿運転時に使用する除湿絞り装置を設けるとともに、
該室内熱交換器の暖房運転時の冷媒流入口部分を、この
入口部分の風下側に室内熱交換器の他の部分が配置され
ないように構成したものである。Further, in an air conditioner having at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into two parts, and dehumidification operation is performed between the two parts. With a dehumidifying squeezing device used at the time,
The refrigerant inlet port during the heating operation of the indoor heat exchanger is configured so that no other part of the indoor heat exchanger is arranged on the leeward side of the inlet part.

【０１６６】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、室
内熱交換器を二分割して、二分割されたその間に除湿運
転時に使用する除湿絞り装置を設けるとともに、該室内
熱交換器の暖房運転時の冷媒流入口部分を、この入口部
分の下方に室内熱交換器の他の部分が配置されないよう
に構成したものである。In an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device, and an outdoor heat exchanger, the indoor heat exchanger is divided into two parts, which are used during dehumidification operation. The dehumidifying expansion device is provided, and the refrigerant inlet portion of the indoor heat exchanger during the heating operation is configured so that other portions of the indoor heat exchanger are not arranged below the inlet portion.

【０１６７】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を熱的に二分割して、二分割されたその
間に除湿運転時に使用する除湿絞り装置を設けるととも
に、室内熱交換器を、放熱フィンにあけた孔の中に伝熱
管を密着させて組み込むと共にこの放熱フィンに切断線
を入れて二分割する構造にしたものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into two parts, and dehumidification is carried out between the two divided parts. A dehumidifying expansion device used during operation is provided, and an indoor heat exchanger is installed with a heat transfer tube in close contact with the holes formed in the radiating fins, and a cutting wire is inserted into the radiating fins to divide it into two parts. Is.

【０１６８】又、少なくとも圧縮機と室内熱交換器と絞
り装置と室外熱交換器を備えた空気調和機において、前
記室内熱交換器を熱的に二分割して二分割されたその間
に除湿運転時に使用する除湿絞り装置を設けるととも
に、室内熱交換器を、放熱フィンにあけた孔の中に伝熱
管を密着させて組み込むとともにこの放熱フィンにスリ
ットを設けて熱的に二分割する構造にしたものである。Further, in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger, the indoor heat exchanger is thermally divided into two parts, and dehumidification operation is performed between them. A dehumidifying expansion device that is used at times is installed, and an indoor heat exchanger is installed by closely fitting a heat transfer tube into the hole formed in the heat radiation fin and providing a slit in this heat radiation fin so that it is divided into two parts thermally. It is a thing.

【０１６９】上記３番目又は４番目の目的を達成するた
めに、本発明の空気調和機は、少なくとも圧縮機と室内
熱交換器と絞り装置と室外熱交換器を備えた空気調和機
において、除湿運転時に、前記室内熱交換器が熱的に分
割された冷却・除湿部分と加熱部分とを有し、室内ユニ
ットに室内湿度を検出する湿度検出手段と室外温度を検
出する温度センサを具備し、あらかじめ本体マイコンに
室外温度と室外ファンモータの制御パターンや室内吹出
空気温度と室外ファンモータの制御パターン及び室内湿
度と設定湿度の差を圧縮機回転数の制御パターンを入れ
ておき、除湿運転時、室内側の湿度状態や室外温度に対
応した最適運転を行う制御としたものである。In order to achieve the above-mentioned third or fourth object, the air conditioner of the present invention is a dehumidifier in an air conditioner equipped with at least a compressor, an indoor heat exchanger, a throttle device and an outdoor heat exchanger. During operation, the indoor heat exchanger has a thermally divided cooling and dehumidifying portion and a heating portion, the indoor unit is equipped with a humidity detecting means for detecting indoor humidity and a temperature sensor for detecting outdoor temperature, When the dehumidification operation is performed, the outdoor temperature and outdoor fan motor control pattern, the indoor blown air temperature and outdoor fan motor control pattern, and the difference between the indoor humidity and the set humidity are entered in the main unit microcomputer in advance to control the compressor rotation speed. This is a control for performing an optimum operation corresponding to the indoor humidity condition and the outdoor temperature.

【０１７０】以上の構成において、上記種々の使用目的
の除湿運転において、例えば、おやすみ・おめざめ除湿
運転では、特に気流感が無く低騒音でしかも除湿量の多
い低風量除湿運転が必要であり、ランドリー除湿運転で
は特に気流が広い範囲まで届き乾燥能力の高い高風量除
湿運転が必要である。快適除湿運転やカビ・ダニ除湿運
転では、低風量除湿運転や高風量除湿運転を適当に使い
分ける必要がある。又低風量除湿運転や高風量除湿運転
に対して、さらに室温に応じて冷房気味、等温気味ある
いは暖房気味の運転を行う必要がある。With the above configuration, in the dehumidifying operation for the various purposes described above, for example, in the good night / desireful dehumidifying operation, the low air flow dehumidifying operation which does not have a feeling of air flow and has a low noise and a large dehumidifying amount is required. In the laundry dehumidifying operation, a high air flow dehumidifying operation is required, which has a high airflow and reaches a wide range. For comfortable dehumidifying operation and mold / tick dehumidifying operation, it is necessary to properly use low air flow dehumidifying operation and high air flow dehumidifying operation. Further, in addition to the low air flow dehumidifying operation and the high air flow dehumidifying operation, it is necessary to further perform cooling, isothermal or heating operation depending on the room temperature.

【０１７１】低風量除湿運転は、室内ファンの風量を落
とすことにより実現でき、さらに圧縮機を低能力から高
能力に制御したりあるいは室外ファンを高風量から低風
量に制御することにより、冷房気味から等温気味に、さ
らに等温気味から暖房気味の広い温度範囲にわたって低
風量除湿運転を行うことができる。The low air volume dehumidifying operation can be realized by reducing the air volume of the indoor fan, and by controlling the compressor from a low capacity to a high capacity or by controlling the outdoor fan from a high air capacity to a low air capacity. Therefore, the low air flow dehumidification operation can be performed over a wide temperature range from the isothermal point to the heating point.

【０１７２】高風量除湿運転を行うには、室内ファンの
風量を増すと共に低風量除湿運転の場合に比べて圧縮機
の能力を同等以上にして運転する。一方室内ユニットに
前記開閉口を付けて室内側熱交換器を通らない通風路を
設けた場合には、圧縮機を低風量除湿運転の場合と同等
に低能力状態にして、さらにこの開閉口を開いて室内熱
交換器を通る空気流に通らない空気流を加えて高風量に
することにより、高風量除湿運転をより省エネルギ状態
で行うことができる。さらにこれらの高風量除湿運転に
おいて、圧縮機能力を高能力に制御したり、あるいは室
外ファンを高風量から低風量に制御することにより、冷
房気味から等温気味に、さらに等温気味から暖房気味の
広い温度範囲にわたって高風量除湿運転を行うことがで
きる。In order to perform the high air volume dehumidifying operation, the air volume of the indoor fan is increased and the capacity of the compressor is made equal to or higher than that in the low air volume dehumidifying operation. On the other hand, when the indoor unit is provided with the opening / closing port and an air passage is provided that does not pass through the indoor heat exchanger, the compressor is put in a low capacity state equivalent to the case of low air volume dehumidifying operation, and the opening / closing port is further opened. A high air flow dehumidifying operation can be performed in a more energy-saving state by adding an air flow that is not opened to the air flow passing through the indoor heat exchanger to increase the air flow. Furthermore, in these high air volume dehumidification operations, by controlling the compression function to a high capacity or by controlling the outdoor fan from a high air volume to a low air volume, it is possible to change from a cooling air to an isothermal air, and an isothermal air to a wide heating air. A high air flow dehumidifying operation can be performed over the temperature range.

【０１７３】又、二分割した各室内側熱交換器の冷媒流
路を複数化したことにより、除湿、冷房、暖房の各運転
において、各流路の冷媒流量が減少し、二分割した利用
側熱交換器を直列に接続したことによる圧力損失の増大
を防いで、性能の低下を防止できる。この効果は、特
に、両方の室内熱交換器が蒸発器となる冷房運転におい
て大きい。さらに室内熱交換器における暖房運転時の出
口流路部分を一系統にしたことにより、暖房運転時に、
適切な冷媒のサブクールが取れ、性能を確保できる。又
さらには室内熱交換器において、冷媒流と空気流とがで
きるだけ対向流にすることにより、伝熱性能が維持さ
れ、性能が確保される。In addition, since the refrigerant flow paths in each of the indoor heat exchangers divided into two are made plural, the refrigerant flow rate in each flow path decreases in each operation of dehumidification, cooling, and heating, and the two divided use sides It is possible to prevent the pressure loss from increasing due to the heat exchangers being connected in series, and prevent the performance from deteriorating. This effect is particularly great in the cooling operation in which both indoor heat exchangers are evaporators. Furthermore, by making the outlet flow path part of the indoor heat exchanger during heating operation into one system, during heating operation,
The proper subcool of the refrigerant can be taken and the performance can be secured. Furthermore, in the indoor heat exchanger, the heat transfer performance is maintained and the performance is ensured by making the refrigerant flow and the air flow as opposed as possible.

【０１７４】又、制御部は、温度センサで検出した外気
温度を用い、室外ファンモータの運転パターンと回転数
をあらかじめ記憶したデータテーブル、又は演算式によ
り、その室外温度にあった室外ファンの運転を行う。さ
らに湿度検出手段で検出した室内湿度を用い、設定され
た湿度との差によってあらかじめ記憶したデータテーブ
ル、又は演算式によりその湿度に応じた圧縮機の回転数
を決定する。Further, the control unit uses the outside air temperature detected by the temperature sensor and operates the outdoor fan at the outdoor temperature according to the data table or the arithmetic expression in which the operation pattern and the rotation speed of the outdoor fan motor are stored in advance. I do. Further, using the indoor humidity detected by the humidity detecting means, the number of revolutions of the compressor corresponding to the humidity is determined by a previously stored data table or an arithmetic expression based on the difference from the set humidity.

【０１７５】又、温度センサで検出した室内吹出空気温
度を用い、室外ファンモータと圧縮機の回転数の運転パ
ターンをあらかじめ記憶したデータテーブル、又は演算
式により、運転パターンと回転数を決定する。Further, using the indoor blown air temperature detected by the temperature sensor, the operation pattern and the rotation speed are determined by a data table in which the operation patterns of the rotation speed of the outdoor fan motor and the compressor are stored in advance, or an arithmetic expression.

【０１７６】以上説明した実施例の空気調和機によれ
ば、室内熱交換器のような利用側熱交換器を二分割して
そのあいだに除湿運転時に使用する除湿絞り装置を設
け、除湿運転時に、利用側熱交換器の一方を蒸発器、他
方を凝縮器として空気の冷却・除湿及び加熱を行う冷凍
サイクルにおいて、室内ファンの様な利用側ファン、室
外ファンのような熱源側ファン及び圧縮機を能力制御可
能なものとして、これらの機器の能力を適当に制御する
ことにより、除湿量を十分取れる状態で、低風量除湿運
転、高風量除湿運転を行ったり、さらにはこれらの各除
湿運転に対して暖房気味、等温気味、冷房気味の運転を
行うことができる。According to the air conditioner of the above-described embodiment, the use side heat exchanger such as the indoor heat exchanger is divided into two, and the dehumidifying expansion device used during the dehumidifying operation is provided between them, and the dehumidifying operation is performed during the dehumidifying operation. In a refrigeration cycle in which one of the use side heat exchangers is an evaporator and the other is a condenser for cooling / dehumidifying and heating air, a use side fan such as an indoor fan, a heat source side fan such as an outdoor fan, and a compressor. By controlling the capacity of these devices appropriately, it is possible to perform low air flow dehumidification operation, high air flow dehumidification operation, and further to these dehumidification operations by controlling the capacity of these devices appropriately. On the other hand, it is possible to perform a heating operation, an isothermal operation, and a cooling operation.

【０１７７】この結果、除湿運転を、その利用範囲を大
幅に拡大して、様々な使用目的の運転モード、例えば快
適な除湿運転、おやすみ・おめざめ除湿運転、カビ・ダ
ニ防止除湿運転、ランドリー除湿運転等に使うことが可
能になり、最近高まっている快適性や健康に対するニー
ズを満足でき、さらには空調以外の目的にも使用できる
空気調和機を提供することができる。As a result, the use range of the dehumidifying operation is greatly expanded, and various operating modes for various purposes, such as comfortable dehumidifying operation, good night / smooth dehumidifying operation, mold / mite prevention dehumidifying operation, and laundry dehumidifying operation are performed. It is possible to provide an air conditioner that can be used for driving or the like, can satisfy the needs for comfort and health that have recently been increasing, and can be used for purposes other than air conditioning.

【０１７８】又、それ程暑くない夏場に冷房運転の代わ
りに室温をそれ程下げずに湿度を下げて体感温度を同一
する除湿運転を行ったり、さらには高風量除湿運転を低
入力で行うことが出来るため、省エネルギを図ることが
できる。Further, in the summer when it is not so hot, instead of the cooling operation, the humidity can be reduced without lowering the room temperature to perform the dehumidifying operation in which the sensible temperature is the same, and further, the high air flow dehumidifying operation can be performed with a low input. Therefore, energy saving can be achieved.

【０１７９】又、二分割した各利用側熱交換器の冷媒流
路を二系統以上にして利用側熱交換器での冷媒流通抵抗
の増加を防止したり、利用側熱交換器の冷媒流路におけ
る暖房運転時の出口部分を一系統にして暖房運転時に十
分な冷媒サブクールが取れるようにしたり、さらには利
用側熱交換器における冷媒流と空気流とができるだけ対
向流になるようにしたこと等により、性能の低下を防ぐ
ことができる。Further, the refrigerant flow path of each of the two use side heat exchangers is divided into two or more systems to prevent an increase in the refrigerant flow resistance in the use side heat exchanger, and the refrigerant flow path of the use side heat exchanger. In order to obtain a sufficient refrigerant subcool during heating operation by making the outlet part during heating operation into one system, and to make the refrigerant flow and the air flow in the heat exchanger on the use side as counterflow as possible, etc. This makes it possible to prevent performance degradation.

【０１８０】又、二分割した各利用側熱交換器の冷媒流
路を冷媒流量に応じて一系統から複数系統にして利用側
熱交換器での冷媒流通抵抗の増加を防止したり、利用側
熱交換器の暖房運転時出口部分を一系統にして暖房運転
時に十分な冷媒サブクールが取れるようにしたり、さら
には利用側熱交換器における冷媒流と空気流とができる
だけ対向流になるようにしたこと等により、性能の低下
を防ぐことができる。Also, the refrigerant flow path of each of the two divided heat exchangers on the use side is changed from one system to a plurality of systems according to the flow rate of the refrigerant to prevent an increase in the refrigerant flow resistance in the heat exchanger on the use side, and to prevent the use side heat exchanger from increasing. The outlet part of the heat exchanger during heating operation was set to be a single system so that sufficient refrigerant subcool could be obtained during heating operation, and further, the refrigerant flow and the air flow in the heat exchanger on the use side could be counter flows as much as possible. As a result, it is possible to prevent performance deterioration.

【０１８１】又、室内ユニット側に吹出温度センサや湿
度検出手段を設け、室外ユニット側に外気温センサを設
けることにより、除湿運転時条件に合った快適な除湿運
転を行うことが可能となる。例えば、室外温度が低くな
る程、室外ファンの回転数を増して室内での空気加熱量
を増すように制御したり、また湿度が高い場合には、室
内ファンや圧縮機の回転数を増加し、除湿量の多い運転
を行って部屋を素速く所定の湿度にしたり、さらには室
温が低温の時、室内ユニットの吹出空気温度を吸込空気
温度より高くする除湿運転を行うことが出来る。Further, by providing the outlet temperature sensor and the humidity detecting means on the indoor unit side and the outdoor air temperature sensor on the outdoor unit side, it is possible to perform a comfortable dehumidifying operation that meets the dehumidifying operation condition. For example, as the outdoor temperature becomes lower, the rotation speed of the outdoor fan is increased to increase the amount of air heated in the room, and when the humidity is high, the rotation speed of the indoor fan or compressor is increased. Further, it is possible to perform the operation with a large amount of dehumidification to quickly bring the room to a predetermined humidity, and further, when the room temperature is low, perform the dehumidification operation in which the temperature of the air blown from the indoor unit is higher than the temperature of the suction air.

【０１８２】さらに又、以上のような除湿運転方法及び
利用側熱交換器の配管構成は、単一冷媒、混合冷媒を問
わず適用でき、同様の効果を得ることができる。Furthermore, the dehumidifying operation method and the piping configuration of the utilization side heat exchanger as described above can be applied to both single refrigerant and mixed refrigerant, and similar effects can be obtained.

【０１８３】[0183]

【発明の効果】以上説明したように、本発明によれば、
人が快適に感じる温湿度にする使用目的で用いる除湿運
転と、これ以外の使用目的で用いる他の除湿運転とを選
択指定して容易に行なうことができる空気調和機を提供
できる。また、本発明によれば、冷房、暖房及び除湿運
転の性能を向上しつつ、人が快適に感じる温湿度にする
使用目的で用いる除湿運転と、これ以外の使用目的で用
いる他の除湿運転とを選択指定して容易に行なうことが
できる空気調和機を提供できる。As described above, according to the present invention,
It is possible to provide an air conditioner that can selectively perform dehumidification operation used for the purpose of use to make the temperature and humidity comfortable for a person and other dehumidification operation used for purposes other than this. Further, according to the present invention, while improving the performance of cooling, heating and dehumidifying operation, the dehumidifying operation used for the purpose of making the temperature and humidity that people feel comfortable, and the other dehumidifying operation used for other purposes. It is possible to provide an air conditioner that can be easily selected and designated.

【図面の簡単な説明】[Brief description of drawings]

【図１】本発明の一実施例である空気調和機の構成を示
す図である。FIG. 1 is a diagram showing a configuration of an air conditioner that is an embodiment of the present invention.

【図２】様々な使用目的の除湿運転の運転方法を示す流
れ図である。FIG. 2 is a flow chart showing an operating method of dehumidifying operation for various purposes.

【図３】低風量除湿運転での圧縮機やファンの運転方法
を示す流れ図である。FIG. 3 is a flowchart showing a method of operating a compressor and a fan in a low air flow dehumidifying operation.

【図４】高風量除湿運転での圧縮機やファンの運転方法
を示す流れ図である。FIG. 4 is a flowchart showing a method of operating a compressor and a fan in a high air volume dehumidifying operation.

【図５】空気調和機の室内ユニット構造を示す側断面図
である。FIG. 5 is a side sectional view showing an indoor unit structure of the air conditioner.

【図６】高風量除湿運転での圧縮機やファンの運転方法
を示す流れ図である。FIG. 6 is a flowchart showing a method of operating a compressor and a fan in a high air volume dehumidifying operation.

【図７】本発明の他の実施例である空気調和機の熱源側
部分を示す図である。FIG. 7 is a diagram showing a heat source side portion of an air conditioner that is another embodiment of the present invention.

【図８】暖房気味除湿運転に対応した熱源側部分の運転
方法を示す流れ図である。FIG. 8 is a flowchart showing an operation method of a heat source side portion corresponding to a heating dehumidifying operation.

【図９】利用側熱交換器の配管系統を示す図である。FIG. 9 is a diagram showing a piping system of a utilization side heat exchanger.

【図１０】利用側熱交換器の正面図である。FIG. 10 is a front view of a utilization side heat exchanger.

【図１１】利用側熱交換器の配管系統を示す図である。FIG. 11 is a diagram showing a piping system of a utilization side heat exchanger.

【図１２】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 12 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１３】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 13 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１４】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 14 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１５】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 15 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１６】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 16 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１７】利用側熱交換器の配管構成を示す側面図であ
る。FIG. 17 is a side view showing a piping configuration of a utilization side heat exchanger.

【図１８】利用側熱交換器の放熱フィンの側面図であ
る。FIG. 18 is a side view of the radiation fins of the utilization side heat exchanger.

【図１９】利用側熱交換器の放熱フィンの側面図であ
る。FIG. 19 is a side view of the radiation fins of the utilization side heat exchanger.

【図２０】絞り装置部分の構成図である。FIG. 20 is a configuration diagram of a diaphragm device portion.

【図２１】冷凍サイクルの温度エントロピ線図である。FIG. 21 is a temperature entropy diagram of the refrigeration cycle.

【図２２】本発明のさらに他の実施例である空気調和機
の構成を示す図である。FIG. 22 is a diagram showing the configuration of an air conditioner that is yet another embodiment of the present invention.

【図２３】空気調和機の他の室内ユニット構造を示す側
断面図である。FIG. 23 is a side sectional view showing another indoor unit structure of the air conditioner.

【図２４】利用側熱交換器の配管系統を示す図である。FIG. 24 is a diagram showing a piping system of a utilization side heat exchanger.

【図２５】利用側熱交換器の配管系統を示す図である。FIG. 25 is a diagram showing a piping system of a utilization side heat exchanger.

【図２６】本発明の空気調和機の構成を示す図である。FIG. 26 is a diagram showing a configuration of an air conditioner of the present invention.

【図２７】室外ファンの制御方法を示す図である。FIG. 27 is a diagram showing a method of controlling the outdoor fan.

【図２８】圧縮機の制御方法を示す図である。FIG. 28 is a diagram showing a method of controlling the compressor.

【図２９】室外ファン-圧縮機の制御方法を示す図であ
る。FIG. 29 is a diagram showing a method of controlling the outdoor fan-compressor.

【図３０】従来技術による空気調和機の構成を示す図で
ある。FIG. 30 is a diagram showing a configuration of an air conditioner according to a conventional technique.

【図３１】従来技術の制御方法を示す図である。FIG. 31 is a diagram showing a conventional control method.

【図３２】本発明による運転パターンの一実施例を示す
図である。FIG. 32 is a diagram showing an example of an operation pattern according to the present invention.

【符号の説明】[Explanation of symbols]

１、２０１…圧縮機、２、２０２…四方弁、３、２０３
…室外熱交換器、４…主絞り装置、５、８、４１…二方
弁、６ａ、６ｂ、５１ａ、５１ｂ、６０ａ、６０ｂ、６
０ｃ、６０ｄ、６８、６８’、６９、６９’、７０、７
０ａ、７０ｂ、８０、８０ａ、８０ｂ、８８、８８ａ、
８８ｂ９８、９８ａ、９８ｂ、１００ａ、１００ｂ、１
００ｃ、１１０ａ、１１０ｂ、２０８、２０９…室内熱
交換器、７、２１０…除湿絞り装置、１０、２１１…室
外ファン、１１、２１２…室外ファンモータ、１２、２
１３…室内ファン、１３、２１４…室内ファンモータ、
１６…制御部、１７、２１６…温度センサ、１８、２１
６…湿度検出手段、３４…開閉ダンパ、３５…通風路、
５２、５３、５４、５５、６１、６２、６３、６４、６
５、６６、６７、１０１、１０２、１０３、１０４、１
０５、１０６、１０…冷媒配管、５６、７１、８１、９
１、９１ａ、９１ｂ、９３、９３ａ、９３ｂ…放熱フィ
ン、７２、８２、８９、９６、９７…切断線、７３ａ、
７３ｂ、７３ｃ、７３ｄ、７３ｅ、７３ｆ、７４ａ、７
４ｂ、７４ｃ、７４ｄ、７４ｅ、７４ｆ、７５ａ、７５
ｂ、７５ｃ、７５ｄ、７５ｅ、７５ｆ、７５ｇ、８３
ａ、８３ｂ、８３ｃ、８７ａ、８７ｂ、８７ｃ、８７
ｄ、８７ｅ、８７ｆ、８７ｇ、８７ｈ…伝熱管、８６…
抵抗管、９２、９４…スリット、９５…電動膨張弁、２
０４…暖房用絞り装置、２０５…冷暖房用絞り装置、２
０６…バイパス用電磁弁、２０７…逆止弁、２１０…除
湿用絞り装置、２１５…外気温センサ、２１７…室内吸
込温度センサ、２１８…室内吹出温度センサ。1, 201 ... Compressor, 2, 202 ... Four-way valve, 3, 203
... Outdoor heat exchanger, 4 ... Main throttling device, 5,8,41 ... Two-way valve, 6a, 6b, 51a, 51b, 60a, 60b, 6
0c, 60d, 68, 68 ', 69, 69', 70, 7
0a, 70b, 80, 80a, 80b, 88, 88a,
88b98, 98a, 98b, 100a, 100b, 1
00c, 110a, 110b, 208, 209 ... Indoor heat exchanger, 7, 210 ... Dehumidifying expansion device, 10, 211 ... Outdoor fan, 11, 212 ... Outdoor fan motor, 12, 2
13 ... Indoor fan, 13, 214 ... Indoor fan motor,
16 ... Control part, 17, 216 ... Temperature sensor, 18, 21
6 ... Humidity detecting means, 34 ... Opening / closing damper, 35 ... Ventilation path,
52, 53, 54, 55, 61, 62, 63, 64, 6
5, 66, 67, 101, 102, 103, 104, 1
05, 106, 10 ... Refrigerant piping, 56, 71, 81, 9
1, 91a, 91b, 93, 93a, 93b ... Radiating fins, 72, 82, 89, 96, 97 ... Cutting line, 73a,
73b, 73c, 73d, 73e, 73f, 74a, 7
4b, 74c, 74d, 74e, 74f, 75a, 75
b, 75c, 75d, 75e, 75f, 75g, 83
a, 83b, 83c, 87a, 87b, 87c, 87
d, 87e, 87f, 87g, 87h ... Heat transfer tube, 86 ...
Resistance tube, 92, 94 ... Slit, 95 ... Electric expansion valve, 2
04 ... Heating throttle device, 205 ... Cooling and heating throttle device, 2
06 ... By-pass solenoid valve, 207 ... Check valve, 210 ... Dehumidifying expansion device, 215 ... Outside air temperature sensor, 217 ... Indoor suction temperature sensor, 218 ... Indoor blowout temperature sensor.

───────────────────────────────────────────────────── フロントページの続き (72)発明者 森本 素生 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業部内 (72)発明者 川村 浩伸 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 (72)発明者 松尾 一也 茨城県土浦市神立町502番地 株式会社日 立製作所機械研究所内 (72)発明者 小暮 博志 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業部内 (72)発明者 岡村 哲信 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業部内 (72)発明者 小曽戸 荘一 栃木県下都賀郡大平町大字富田800番地 株式会社日立製作所リビング機器事業部内 Ｆターム(参考） 3L060 AA07 DD07 EE01    ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Sou Morimoto             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi, Ltd. Living Equipment Division (72) Inventor Hironobu Kawamura             502 Kintatemachi, Tsuchiura City, Ibaraki Japan             Tate Seisakusho Mechanical Research Center (72) Inventor Kazuya Matsuo             502 Kintatemachi, Tsuchiura City, Ibaraki Japan             Tate Seisakusho Mechanical Research Center (72) Inventor Hiroshi Kogure             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi, Ltd. Living Equipment Division (72) Inventor Tetsunobu Okamura             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi, Ltd. Living Equipment Division (72) Inventor Shoichi Ozodo             800 Tomita, Ohira-cho, Shimotsuga-gun, Tochigi             Hitachi, Ltd. Living Equipment Division F-term (reference) 3L060 AA07 DD07 EE01

Claims (12)

【特許請求の範囲】[Claims] 【請求項１】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とする除湿運転モードとを備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。1. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. And a dehumidifying operation mode and an air conditioner, characterized by selecting and designating one of these drying mode. 【請求項２】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とし、この室内ファンが高風量であっても除湿能力が
得られる能力で前記圧縮機を運転する除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。2. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. The indoor fan is provided with a dehumidifying operation mode in which the compressor is operated with the ability to obtain the dehumidifying ability even if the indoor fan has a high air flow rate, and any one of these dehumidifying operation modes is selectively designated. Machine. 【請求項３】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。3. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. And a dehumidifying operation mode in which the compressor and the outdoor fan are controlled to realize an operation that provides a comfortable environment during sleep, and the air volume of the indoor fan is a preset low air volume. Comprising, an air conditioner, characterized by selecting and designating one of these drying mode. 【請求項４】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 湿度が４０％〜６０％となる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を設定する機能を有する除湿運転モードとを備
え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。4. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttling device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. And a dehumidification operation mode having a function of controlling the compressor and the outdoor fan so as to realize an operation in which the humidity is 40% to 60% and setting the air volume of the indoor fan. , Air conditioner, characterized by selecting and designating one of these drying mode. 【請求項５】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とする除湿運転モードと、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。5. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate is controllable, a first indoor heat exchanger, a second indoor heat exchanger, and a throttling device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. And a dehumidifying operation mode in which the compressor and the outdoor fan are controlled to realize an operation that provides a comfortable environment during sleep and the air volume of the indoor fan is a preset low air volume. An air conditioner that is equipped with and selectively specifies any of these dehumidifying operation modes. 【請求項６】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とし、この室内ファンが高風量であっても除湿能力が
得られる能力で前記圧縮機を運転する除湿運転モード
と、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。6. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate is controllable, a first indoor heat exchanger, a second indoor heat exchanger, and a throttling device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. The dehumidifying operation mode of operating the compressor with the ability to obtain dehumidifying ability even when the indoor fan has a high air volume, and the compressor and the outdoor fan so as to realize an operation in which a comfortable environment is obtained during sleep. And a dehumidifying operation mode in which the air volume of the indoor fan is set to a preset low air volume, and any one of these dehumidifying operation modes is selected and designated. 【請求項７】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とする除湿運転モードと、 湿度が４０％〜６０％となる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を設定する機能を有する除湿運転モードとを備
え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。7. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate is controllable, a first indoor heat exchanger, a second indoor heat exchanger, and a throttling device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. And a dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize an operation in which the humidity is 40% to 60% and which has a function of setting the air volume of the indoor fan. An air conditioner characterized by selectively designating one of these dehumidifying operation modes. 【請求項８】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とし、この室内ファンが高風量であっても除湿能力が
得られる能力で前記圧縮機を運転する除湿運転モード
と、 湿度が４０％〜６０％となる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を設定する機能を有する除湿運転モードとを備
え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。8. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In the air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize operation of temperature and humidity that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. The dehumidifying operation mode in which the compressor is operated with the ability to obtain the dehumidifying ability even if the indoor fan has a high air flow rate, and the compressor and the so that the humidity is 40% to 60%. An air conditioner comprising: a dehumidifying operation mode in which an outdoor fan is controlled and a function of setting an air volume of the indoor fan is provided, and any one of these dehumidifying operation modes is selected and designated. 【請求項９】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、人が快適に感じる温湿度の運転
を実現するように前記圧縮機及び前記室外ファンが制御
され且つ前記室内ファンの風量を設定する機能を有する
除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とする除湿運転モードと、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モード
と、 湿度が４０％〜６０％となる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を設定する機能を有する除湿運転モードとを備
え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。9. A compressor whose capacity can be controlled, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In an air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize a temperature and humidity operation that a person feels comfortable. A dehumidifying operation mode having the following, and the compressor and the outdoor fan are controlled so as to realize an operation for drying the laundry, and a high airflow preset so that the airflow of the indoor fan is spread over a wide range. A dehumidifying operation mode, and a dehumidifying operation mode in which the compressor and the outdoor fan are controlled to realize an operation that provides a comfortable environment during sleep and the air volume of the indoor fan is a preset low air volume, A dehumidifying operation mode in which the compressor and the outdoor fan are controlled so as to realize an operation in which the humidity is 40% to 60% and the air volume of the indoor fan is set. An air conditioner characterized by selectively specifying. 【請求項１０】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器と、第２室内熱交換器と、除湿運転時に絞り装置とし
て機能する除湿絞り装置と、風量制御可能な室内ファン
とを備え、前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記除湿絞り装置、前記第２室内熱交換器
を順次管路によって接続された空気調和機において、 除湿運転モードとして、人が快適に感じる温湿度の運転
を実現するように前記圧縮機及び前記室外ファンが制御
され且つ前記室内ファンの風量を設定する機能を有する
除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とし、この室内ファンが高風量であっても除湿能力が
得られる能力で前記圧縮機を運転する除湿運転モード
と、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モード
と、 湿度が４０％〜６０％となる運転を実現するように前記
圧縮機及び前記室外ファンが制御され且つ前記室内ファ
ンの風量を設定する機能を有する除湿運転モードとを備
え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。10. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate can be controlled, a first indoor heat exchanger, a second indoor heat exchanger, and a throttle device during dehumidifying operation. A compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, and the second indoor heat exchanger in that order. In an air conditioner connected by a pipeline, a function to control the compressor and the outdoor fan and set the air volume of the indoor fan as a dehumidifying operation mode so as to realize a temperature and humidity operation that a person feels comfortable. The dehumidifying operation mode having the above, and the compressor and the outdoor fan are controlled so as to realize the operation of drying the laundry, and the air volume of the indoor fan is set to a preset high value so as to spread the airflow over a wide range. A dehumidifying operation mode in which the compressor is operated with the ability to obtain the dehumidifying capacity even when the indoor fan has a high air flow rate, and the compressor and the outdoor unit so as to realize an operation that provides a comfortable environment during sleep. The compressor and the outdoor fan are controlled so as to realize a dehumidification operation mode in which the fan is controlled and the air flow rate of the indoor fan is a preset low air flow rate, and an operation in which the humidity is 40% to 60%, and An air conditioner comprising: a dehumidifying operation mode having a function of setting an air flow rate of the indoor fan, and selectively designating any one of these dehumidifying operation modes. 【請求項１１】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器及び第２室内熱交換器を有する室内熱交換器と、除湿
運転時に絞り装置として機能する除湿絞り装置と、風量
制御可能な室内ファンとを備え、除湿運転時に前記圧縮
機、前記室外熱交換器、前記第１室内熱交換器、前記除
湿絞り装置、前記第２室内熱交換器の順に接続され、冷
房運転時に前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記第２室内熱交換器の順に接続され、暖
房運転時に前記圧縮機、前記第２室内熱交換器、前記第
１室内熱交換器、前記室外熱交換器の順に接続される空
気調和機において、 前記第１室内熱交換器及び前記第２室内熱交換器のそれ
ぞれの冷媒流路を二系統以上に分けて構成すると共に、 一方の前記室内熱交換器の冷媒流路の合流点と他方の前
記室内熱交換器の冷媒流路の分岐点との間に前記除湿絞
り装置を接続し、 暖房運転時に下流側となる方の前記室内熱交換器の出口
側を一系統の冷媒流路で構成し、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。11. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate is controllable, and an indoor heat exchanger having a first indoor heat exchanger and a second indoor heat exchanger. A dehumidifying throttle device that functions as a throttle device during a dehumidifying operation, and an indoor fan capable of controlling the air volume are provided, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, the A second indoor heat exchanger is connected in this order, the compressor, the outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger are connected in that order during cooling operation, and the compressor is used during heating operation. An air conditioner connected in the order of the second indoor heat exchanger, the first indoor heat exchanger, and the outdoor heat exchanger, wherein each of the first indoor heat exchanger and the second indoor heat exchanger Refrigerant flow path is divided into two or more systems and , Which is the downstream side during the heating operation by connecting the dehumidifying expansion device between the confluence of the refrigerant channels of the one indoor heat exchanger and the branch point of the refrigerant channels of the other indoor heat exchanger The outlet side of the indoor heat exchanger is configured with a single-system refrigerant flow path, and the compressor and the outdoor fan are controlled so as to realize a temperature / humidity operation that a person feels comfortable in a dehumidification operation mode. A dehumidifying operation mode having a function of setting the air volume of the indoor fan, and the compressor and the outdoor fan are controlled so as to realize an operation that provides a comfortable environment during sleep, and the air volume of the indoor fan is preset. An air conditioner comprising: a dehumidifying operation mode in which the air volume is low, and one of these dehumidifying operation modes is selectively designated. 【請求項１２】能力制御可能な圧縮機と、室外熱交換器
と、送風量制御が可能な室外ファンと、第１室内熱交換
器及び第２室内熱交換器を有する室内熱交換器と、除湿
運転時に絞り装置として機能する除湿絞り装置と、風量
制御可能な室内ファンとを備え、除湿運転時に前記圧縮
機、前記室外熱交換器、前記第１室内熱交換器、前記除
湿絞り装置、前記第２室内熱交換器の順に接続され、冷
房運転時に前記圧縮機、前記室外熱交換器、前記第１室
内熱交換器、前記第２室内熱交換器の順に接続され、暖
房運転時に前記圧縮機、前記第２室内熱交換器、前記第
１室内熱交換器、前記室外熱交換器の順に接続される空
気調和機において、 前記第１室内熱交換器及び前記第２室内熱交換器のそれ
ぞれの冷媒流路を二系統以上に分けて構成すると共に、 一方の前記室内熱交換器の冷媒流路の合流点と他方の前
記室内熱交換器の冷媒流路の分岐点との間に前記除湿絞
り装置を接続し、 暖房運転時に下流側となる方の前記室内熱交換器の出口
側を一系統の冷媒流路で構成し、 除湿運転モードとして、 人が快適に感じる温湿度の運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を設定する機能を有する除湿運転モードと、 洗濯物を乾燥させる運転を実現するように前記圧縮機及
び前記室外ファンが制御され且つ前記室内ファンの風量
を気流が広い範囲にゆき渡るように予め設定された高風
量とする除湿運転モードとを備え、 睡眠時に快適な環境となる運転を実現するように前記圧
縮機及び前記室外ファンが制御され且つ前記室内ファン
の風量を予め設定された低風量とする除湿運転モードと
を備え、 これら除湿運転モードの何れかを選択指定することを特
徴とする空気調和機。12. A compressor whose capacity is controllable, an outdoor heat exchanger, an outdoor fan whose air flow rate is controllable, an indoor heat exchanger having a first indoor heat exchanger and a second indoor heat exchanger, A dehumidifying throttle device that functions as a throttle device during a dehumidifying operation, and an indoor fan capable of controlling the air volume are provided, and the compressor, the outdoor heat exchanger, the first indoor heat exchanger, the dehumidifying throttle device, the A second indoor heat exchanger is connected in this order, the compressor, the outdoor heat exchanger, the first indoor heat exchanger, and the second indoor heat exchanger are connected in that order during cooling operation, and the compressor is used during heating operation. An air conditioner connected in the order of the second indoor heat exchanger, the first indoor heat exchanger, and the outdoor heat exchanger, wherein each of the first indoor heat exchanger and the second indoor heat exchanger Refrigerant flow path is divided into two or more systems and , Which is the downstream side during the heating operation by connecting the dehumidifying expansion device between the confluence of the refrigerant channels of the one indoor heat exchanger and the branch point of the refrigerant channels of the other indoor heat exchanger The outlet side of the indoor heat exchanger is configured with a single-system refrigerant flow path, and the compressor and the outdoor fan are controlled so as to realize a temperature / humidity operation that a person feels comfortable in a dehumidification operation mode. The compressor and the outdoor fan are controlled so that the dehumidifying operation mode having a function of setting the air volume of the indoor fan and the operation of drying the laundry are realized, and the air volume of the indoor fan is spread over a wide range. It has a dehumidifying operation mode with a preset high air volume so that the compressor and the outdoor fan are controlled and the air volume of the indoor fan is preset so as to realize an operation that provides a comfortable environment during sleep. It has been a dehumidifying operation mode and a low air volume, the air conditioner, characterized by selecting and designating one of these drying mode.
JP2002262509A 1993-06-01 2002-09-09 Air conditioner Expired - Lifetime JP3653261B2 (en)

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JP13025693 1993-06-01
JP5-225435 1993-09-10
JP22543593 1993-09-10
JP5-237635 1993-09-10
JP5-130256 1993-09-10
JP23763593 1993-09-24
JP2002262509A JP3653261B2 (en) 1993-06-01 2002-09-09 Air conditioner

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JP2007247986A (en) * 2006-03-16 2007-09-27 Daikin Ind Ltd Air-conditioning method and air conditioner
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CN111254642A (en) * 2018-11-30 2020-06-09 青岛海尔洗衣机有限公司 Control method for clothes care equipment and clothes care equipment

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007225159A (en) * 2006-02-22 2007-09-06 Sanyo Electric Co Ltd Dehumidifying air conditioning system and desiccant air conditioner
JP2007247986A (en) * 2006-03-16 2007-09-27 Daikin Ind Ltd Air-conditioning method and air conditioner
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CN110118394B (en) * 2018-02-05 2022-05-10 广州松下空调器有限公司 Air conditioner control method and air conditioner
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