JP2001124434A - Air conditioner - Google Patents

Air conditioner

Info

Publication number
JP2001124434A
JP2001124434A JP30854499A JP30854499A JP2001124434A JP 2001124434 A JP2001124434 A JP 2001124434A JP 30854499 A JP30854499 A JP 30854499A JP 30854499 A JP30854499 A JP 30854499A JP 2001124434 A JP2001124434 A JP 2001124434A
Authority
JP
Japan
Prior art keywords
heat exchanger
temperature
air
air conditioner
indoor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
JP30854499A
Other languages
Japanese (ja)
Inventor
Toru Suzuki
徹 鈴木
Takashi Tsuchino
隆志 土野
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries 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 Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to JP30854499A priority Critical patent/JP2001124434A/en
Priority to KR10-2002-7005192A priority patent/KR100491718B1/en
Priority to AT00969980T priority patent/ATE423949T1/en
Priority to DE60041649T priority patent/DE60041649D1/en
Priority to AU79536/00A priority patent/AU7953600A/en
Priority to EP00969980A priority patent/EP1227286B1/en
Priority to CNB008149356A priority patent/CN1196902C/en
Priority to ES00969980T priority patent/ES2321685T3/en
Priority to PCT/JP2000/007369 priority patent/WO2001033146A1/en
Publication of JP2001124434A publication Critical patent/JP2001124434A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0083—Indoor units, e.g. fan coil units with dehumidification means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F3/153—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02341—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02343—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during dehumidification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • F25B2313/02344—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements during heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0254—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in series arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/02—Humidity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Air Conditioning Control Device (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)
  • Drying Of Solid Materials (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioner capable of effectively conducting a reheating dry operation by enhancing a dehumidifying amount by controlling the temperature of an evaporator even by dehumidifying while operating a tendency to be heated in a room. SOLUTION: The air conditioner 1 comprises an indoor heat exchanger 5 having a first heat exchanger 10 and a second heat exchanger 11 connected in series, and a pressure reducing mechanism 12 interposed between the exchangers 10 and 11. The refrigerant from a compressor 2 is sequentially circulated through an outdoor heat exchanger 3, a pressure reducing mechanism 4 and an indoor heat exchanger 5. A reheating dry operation for functioning the exchanger 10 as a condenser, the exchanger 11 as an evaporator, cooling indoor air, dehumidifying the air, then again heating the air and returning the air into the room is conducted. In this case, the temperature of the exchanger 11 functioned as the evaporator is controlled by a control means 13.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】この発明は、再熱ドライ運転
が可能な空調装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air conditioner capable of performing a reheat dry operation.

【０００２】[0002]

【従来の技術】図１は、本発明の一実施の形態である空
調装置１の構成を示す冷媒回路図であるが、基本的な構
成は従来と同様であるので、図１を参照しながら従来の
技術を説明する。空調装置１は、圧縮機２、室外熱交換
器３、減圧機構４、室内熱交換器５を備えるヒートポン
プ式の空調装置であり、圧縮機２からの冷媒が循環され
るように冷媒回路が構成されている。すなわち、圧縮機
２の吐出側と吸込側とは、それぞれ四路切換弁６の１次
ポートに接続されている。そして、四路切換弁６の２次
ポートの一方から、室外ファン７を付設している室外熱
交換器３、減圧機構４、室内ファン８を付設している室
内熱交換器５をそれぞれ経由して四路切換弁６の他方の
２次ポートへ至る冷媒回路が冷媒配管によって構成され
ている。なお、四路切換弁６からは、アキュムレータ９
を介して圧縮機２の吸込側に戻るようになっている。ま
た室内熱交換器５は、直列に接続された第１熱交換器１
０と第２熱交換器１１とから成り、上記各熱交換器１
０、１１の間には減圧機構１２が介設されている。2. Description of the Related Art FIG. 1 is a refrigerant circuit diagram showing a configuration of an air conditioner 1 according to an embodiment of the present invention. A conventional technique will be described. The air conditioner 1 is a heat pump type air conditioner including a compressor 2, an outdoor heat exchanger 3, a decompression mechanism 4, and an indoor heat exchanger 5, and a refrigerant circuit is configured so that refrigerant from the compressor 2 is circulated. Have been. That is, the discharge side and the suction side of the compressor 2 are respectively connected to the primary ports of the four-way switching valve 6. Then, one of the secondary ports of the four-way switching valve 6 passes through the outdoor heat exchanger 3 provided with the outdoor fan 7, the pressure reducing mechanism 4, and the indoor heat exchanger 5 provided with the indoor fan 8, respectively. The refrigerant circuit leading to the other secondary port of the four-way switching valve 6 is constituted by a refrigerant pipe. Note that the accumulator 9 is output from the four-way switching valve 6.
And returns to the suction side of the compressor 2. The indoor heat exchanger 5 includes the first heat exchanger 1 connected in series.
0 and the second heat exchanger 11, each heat exchanger 1
A pressure reducing mechanism 12 is interposed between 0 and 11.

【０００３】上記冷媒回路による空調運転の種類には、
冷房運転、暖房運転、再熱ドライ運転等がある。冷房運
転及び暖房運転の際には、室内熱交換器５の減圧機構１
２を全開状態とする一方で、減圧機構４を所定の開度に
調整し、さらに室外ファン７及び室内ファン８を所定の
回転数で駆動する。そして、冷房運転の場合は、圧縮機
２からの吐出冷媒を実線矢印に示すように循環させるこ
とによって、室外熱交換器３を凝縮器として機能させる
と共に、室内熱交換器５を蒸発器として機能させること
で室内空気が冷却される。また暖房運転の場合は、圧縮
機２からの吐出冷媒を破線矢印に示すように循環させる
ことによって、室内熱交換器５を凝縮器として機能させ
ると共に、室外熱交換器３を蒸発器として機能させるこ
とで室内空気が加熱される。The types of air-conditioning operation by the refrigerant circuit include:
There are a cooling operation, a heating operation, a reheating dry operation, and the like. During the cooling operation and the heating operation, the pressure reducing mechanism 1 of the indoor heat exchanger 5 is used.
2, the pressure reducing mechanism 4 is adjusted to a predetermined opening while the outdoor fan 7 and the indoor fan 8 are driven at a predetermined rotation speed. In the case of the cooling operation, the refrigerant discharged from the compressor 2 is circulated as shown by a solid line arrow, so that the outdoor heat exchanger 3 functions as a condenser and the indoor heat exchanger 5 functions as an evaporator. By doing so, the room air is cooled. In the case of the heating operation, the refrigerant discharged from the compressor 2 is circulated as indicated by the dashed arrow, so that the indoor heat exchanger 5 functions as a condenser and the outdoor heat exchanger 3 functions as an evaporator. This heats the indoor air.

【０００４】一方、再熱ドライ運転の際には、室内熱交
換器５の減圧機構１２を所定の開度に調整する一方で、
減圧機構４を全開状態とし、さらに室内ファン８を所定
の回転数で駆動する一方で、室外ファン７を停止状態と
する。そして、圧縮機２からの吐出冷媒を実線矢印に示
すように冷房サイクルでもって循環させることによっ
て、室内熱交換器５の第１熱交換器１０を凝縮器として
機能させると共に、第２熱交換器１１を蒸発器として機
能させる。これによって、室内空気を蒸発器として機能
する第２熱交換器１１で冷却して除湿した後に、凝縮器
として機能する第１熱交換器１０で再び加熱して室内に
戻す再熱ドライ運転が行われる。On the other hand, during the reheat dry operation, while the pressure reducing mechanism 12 of the indoor heat exchanger 5 is adjusted to a predetermined opening,
The pressure reducing mechanism 4 is fully opened, and the indoor fan 8 is driven at a predetermined rotation speed, while the outdoor fan 7 is stopped. Then, the refrigerant discharged from the compressor 2 is circulated in the cooling cycle as shown by the solid line arrow, so that the first heat exchanger 10 of the indoor heat exchanger 5 functions as a condenser and the second heat exchanger 11 functions as an evaporator. Thereby, after the room air is cooled and dehumidified by the second heat exchanger 11 functioning as an evaporator, the reheat dry operation is performed by heating the room air again and returning the room air to the room by the first heat exchanger 10 functioning as a condenser. Will be

【０００５】[0005]

【発明が解決しようとする課題】上記の再熱ドライ運転
において述べたように、室内機に凝縮器としての機能を
備えた第１熱交換器１０と、蒸発器としての機能を備え
た第２熱交換器１１を有しているため、室内温度を略一
定に保ったまま除湿することが可能である。しかし肌寒
い季節等において室内を暖房ぎみにしながら除湿を行い
たい場合には、凝縮器である第１熱交換器１０における
凝縮温度を高くする必要があるが、上記凝縮温度が高く
なるように制御すれば、これに伴って蒸発温度も高くな
ってしまう。そしてこのように、上記第２熱交換器１１
の蒸発温度が高くなると、室内空気の露点温度との差が
小さくなるため、除湿量が極端に減少してしまうという
問題が生じる。As described above in the reheat dry operation, the first heat exchanger 10 having the function of the indoor unit as the condenser and the second heat exchanger 10 having the function of the evaporator in the indoor unit. Since it has the heat exchanger 11, it is possible to dehumidify while keeping the room temperature substantially constant. However, when it is desired to perform dehumidification while heating the room in a chilly season or the like, it is necessary to increase the condensation temperature in the first heat exchanger 10 which is a condenser. If this happens, the evaporation temperature will increase accordingly. And in this way, the second heat exchanger 11
If the evaporation temperature of the air becomes high, the difference from the dew point temperature of the indoor air becomes small, so that there is a problem that the amount of dehumidification decreases extremely.

【０００６】この発明は上記従来の欠点を解決するため
になされたものであり、その目的は、室内を暖房ぎみに
しながら除湿を行うような場合においても、蒸発器の温
度を制御することによって除湿量を高め、再熱ドライ運
転を確実に行うことができる空調装置を提供することに
ある。SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned conventional drawbacks, and an object of the present invention is to control the temperature of an evaporator to control the temperature of an evaporator even when performing dehumidification while heating the room. It is an object of the present invention to provide an air conditioner capable of increasing the amount and reliably performing a reheat dry operation.

【０００７】[0007]

【課題を解決するための手段】そこで請求項１の空調装
置は、直列に接続された第１熱交換器１０と第２熱交換
器１１とから成る室内熱交換器５と、上記各熱交換器１
０、１１の間に介設された減圧機構１２とを有する空調
装置であって、上記第１熱交換器１０を凝縮器として機
能させる一方、第２熱交換器１１を蒸発器として機能さ
せて、室内空気を冷却して除湿した後に再び加熱して室
内に戻す再熱ドライ運転が可能な空調装置において、上
記再熱ドライ運転時に、蒸発器として機能する第２熱交
換器１１の温度を制御する制御手段１３を設けたことを
特徴としている。Therefore, the air conditioner according to the present invention comprises an indoor heat exchanger 5 composed of a first heat exchanger 10 and a second heat exchanger 11 connected in series, and Vessel 1
An air conditioner having a pressure reducing mechanism 12 interposed between 0 and 11, wherein the first heat exchanger 10 functions as a condenser while the second heat exchanger 11 functions as an evaporator. In an air conditioner capable of reheating dry operation in which room air is cooled and dehumidified and then heated again to return to the room, the temperature of the second heat exchanger 11 functioning as an evaporator is controlled during the reheat dry operation. The control means 13 is provided.

【０００８】上記請求項１の空調装置では、室内機に、
蒸発器として機能する第２熱交換器１１の温度を制御す
る制御手段１３を設けている。これより、室内を暖房ぎ
みにしながら再熱ドライ運転を行うような場合におい
て、凝縮器として機能する第１熱交換器１０の凝縮温度
を上昇させても、上記制御手段１３を用いて第２熱交換
器１１の温度を低下させたり、あるいは温度上昇を抑制
することができるため、除湿量を減少させることなく確
実に再熱ドライ運転を実行することができる。なおこの
ように第２熱交換器１１の温度を制御すれば、通常の再
熱ドライ運転時においても、確実な除湿効果を得られる
という利点がある。In the air conditioner of the first aspect, the indoor unit includes:
Control means 13 for controlling the temperature of the second heat exchanger 11 functioning as an evaporator is provided. Accordingly, in a case where the reheat dry operation is performed while the room is being heated, even if the condensing temperature of the first heat exchanger 10 functioning as a condenser is increased, the second heat is controlled by using the control means 13. Since the temperature of the exchanger 11 can be lowered or the rise in temperature can be suppressed, the reheat dry operation can be executed reliably without reducing the amount of dehumidification. Controlling the temperature of the second heat exchanger 11 in this manner has the advantage that a reliable dehumidifying effect can be obtained even during a normal reheating dry operation.

【０００９】また請求項２の空調装置は、室内温度セン
サ２７と、湿度センサ２８とを設け、上記各センサ２
７、２８によって測定された温度と湿度とから露点温度
を求めると共に、上記露点温度から第２熱交換器１１の
温度制御を行うことを特徴としている。The air conditioner according to the second aspect of the present invention includes an indoor temperature sensor 27 and a humidity sensor 28.
The method is characterized in that the dew point temperature is obtained from the temperature and the humidity measured by 7 and 28, and the temperature of the second heat exchanger 11 is controlled from the dew point temperature.

【００１０】上記請求項２の空調装置では、室内温度セ
ンサ２７と湿度センサ２８とを設けたことによって、室
内の温度と湿度とを測定し、この測定結果より求めた露
点温度から、第２熱交換器１１の温度を上記制御手段１
３を用いて制御する。この結果、精度のよい除湿制御が
行える。In the air conditioner according to the second aspect of the present invention, by providing the indoor temperature sensor 27 and the humidity sensor, the indoor temperature and humidity are measured, and from the dew point temperature obtained from the measurement result, the second heat is measured. The temperature of the exchanger 11 is controlled by the control means 1
3 is used for control. As a result, accurate dehumidification control can be performed.

【００１１】さらに請求項３の空調装置は、上記制御手
段１３は、第２熱交換器１１への風量を制御する風量制
御手段であることを特徴としている。The air conditioner according to claim 3 is characterized in that the control means 13 is an air flow control means for controlling the air flow to the second heat exchanger 11.

【００１２】上記請求項３の空調装置では、風量制御手
段を用いて通過風量を減少させることによって、第２熱
交換器１１の温度を制御することができる。この結果、
簡素な構成でもって確実に除湿量を高めることができ
る。In the air conditioner according to the third aspect, the temperature of the second heat exchanger 11 can be controlled by reducing the amount of passing air using the air volume control means. As a result,
The amount of dehumidification can be reliably increased with a simple configuration.

【００１３】また請求項４の空調装置は、上記制御手段
１３は、上記減圧機構１２を開度可変に構成して成る圧
力制御手段であることを特徴としている。The air conditioner according to a fourth aspect of the present invention is characterized in that the control means 13 is a pressure control means comprising a variable opening of the pressure reducing mechanism 12.

【００１４】上記請求項４の空調装置では、上記圧力制
御手段を用いて上記第２熱交換器１１への減圧量を制御
することによって、第２熱交換器１１の温度を制御する
ことができる。この結果、簡素な構成でもって確実に除
湿量を高めることができる。In the air conditioner of the fourth aspect, the temperature of the second heat exchanger 11 can be controlled by controlling the amount of pressure reduction to the second heat exchanger 11 using the pressure control means. . As a result, the amount of dehumidification can be reliably increased with a simple configuration.

【００１５】[0015]

【発明の実施の形態】次に、この発明の空調装置の具体
的な実施の形態について、図面を参照しつつ詳細に説明
する。Next, specific embodiments of the air conditioner of the present invention will be described in detail with reference to the drawings.

【００１６】図１は本発明の一実施の形態である空調装
置１の構成を示す冷媒回路図である。図に示すように、
空調装置１は、圧縮機２、室外熱交換器３、減圧機構
４、室内熱交換器５を備えるヒートポンプ式の空調装置
であり、圧縮機２からの冷媒が循環されるように冷媒回
路が構成されている。すなわち、圧縮機２の吐出側と吸
込側とは、それぞれ四路切換弁６の１次ポートに接続さ
れている。そして、四路切換弁６の２次ポートの一方か
ら、室外ファン７を付設している室外熱交換器３、減圧
機構４、室内ファン８を付設している室内熱交換器５を
それぞれ経由して四路切換弁６の他方の２次ポートへ至
る冷媒回路が冷媒配管によって構成されている。なお、
四路切換弁６からは、アキュムレータ９を介して圧縮機
２の吸込側に戻るようになっている。また室内熱交換器
５は、直列に接続された第１熱交換器１０と第２熱交換
器１１とから成り、上記各熱交換器１０、１１の間には
減圧機構１２が介設されている。FIG. 1 is a refrigerant circuit diagram showing a configuration of an air conditioner 1 according to an embodiment of the present invention. As shown in the figure,
The air conditioner 1 is a heat pump type air conditioner including a compressor 2, an outdoor heat exchanger 3, a decompression mechanism 4, and an indoor heat exchanger 5, and a refrigerant circuit is configured so that refrigerant from the compressor 2 is circulated. Have been. That is, the discharge side and the suction side of the compressor 2 are respectively connected to the primary ports of the four-way switching valve 6. Then, one of the secondary ports of the four-way switching valve 6 passes through the outdoor heat exchanger 3 provided with the outdoor fan 7, the pressure reducing mechanism 4, and the indoor heat exchanger 5 provided with the indoor fan 8, respectively. The refrigerant circuit leading to the other secondary port of the four-way switching valve 6 is constituted by a refrigerant pipe. In addition,
The four-way switching valve 6 returns to the suction side of the compressor 2 via the accumulator 9. The indoor heat exchanger 5 includes a first heat exchanger 10 and a second heat exchanger 11 connected in series, and a decompression mechanism 12 is interposed between the heat exchangers 10 and 11. I have.

【００１７】上記冷媒回路による空調運転の種類には、
冷房運転、暖房運転、再熱ドライ運転等がある。上記冷
房運転及び暖房運転の際には、室内熱交換器５の減圧機
構１２を全開状態とする一方で、減圧機構４を所定の開
度に調整し、さらに室外ファン７及び室内ファン８を所
定の回転数で駆動する。そして、冷房運転の場合は、圧
縮機２からの吐出冷媒を実線矢印に示すように循環させ
ることによって、室外熱交換器３を凝縮器として機能さ
せると共に、室内熱交換器５を蒸発器として機能させる
ことで室内空気が冷却される。また暖房運転の場合は、
圧縮機２からの吐出冷媒を破線矢印に示すように循環さ
せることによって、室内熱交換器５を凝縮器として機能
させると共に、室外熱交換器３を蒸発器として機能させ
ることで室内空気が加熱される。The types of air conditioning operation by the refrigerant circuit include:
There are a cooling operation, a heating operation, a reheating dry operation, and the like. During the cooling operation and the heating operation, the decompression mechanism 12 of the indoor heat exchanger 5 is fully opened, the decompression mechanism 4 is adjusted to a predetermined opening degree, and the outdoor fan 7 and the indoor fan 8 are controlled to a predetermined degree. Drive at the rotation speed of. In the case of the cooling operation, the refrigerant discharged from the compressor 2 is circulated as shown by a solid line arrow, so that the outdoor heat exchanger 3 functions as a condenser and the indoor heat exchanger 5 functions as an evaporator. By doing so, the room air is cooled. In the case of heating operation,
By circulating the refrigerant discharged from the compressor 2 as shown by the dashed arrow, the indoor heat exchanger 5 functions as a condenser, and the outdoor heat exchanger 3 functions as an evaporator, thereby heating the indoor air. You.

【００１８】一方、再熱ドライ運転の際には、室内熱交
換器５の減圧機構１２を所定の開度に調整する一方で、
減圧機構４を全開状態とし、さらに室内ファン８を所定
の回転数で駆動する一方で、室外ファン７を停止状態と
する。そして、圧縮機２からの吐出冷媒を実線矢印に示
すように循環させることによって、室内熱交換器５の第
１熱交換器１０を凝縮器として機能させると共に、第２
熱交換器１１を蒸発器として機能させる。これによっ
て、室内空気を蒸発器として機能する第２熱交換器１１
で冷却して除湿した後に、再び凝縮器として機能する第
１熱交換器１０で加熱して室内に戻す再熱ドライ運転が
行われる。なお、再熱ドライ運転では室外熱交換器３も
凝縮器として機能し得るが、上記のように室外ファン７
を停止状態とすることによって室外熱交換器３の周囲の
外気が流通しないようにして室外熱交換器３ではできる
限り熱交換が行われないようにしている。On the other hand, during the reheat dry operation, while the pressure reducing mechanism 12 of the indoor heat exchanger 5 is adjusted to a predetermined opening,
The pressure reducing mechanism 4 is fully opened, and the indoor fan 8 is driven at a predetermined rotation speed, while the outdoor fan 7 is stopped. Then, by circulating the refrigerant discharged from the compressor 2 as shown by a solid arrow, the first heat exchanger 10 of the indoor heat exchanger 5 functions as a condenser,
The heat exchanger 11 functions as an evaporator. Thereby, the second heat exchanger 11 that functions as an evaporator using the indoor air
Then, the reheat dry operation is performed in which the first heat exchanger 10 functioning again as a condenser heats and returns to the room. In the reheat dry operation, the outdoor heat exchanger 3 can also function as a condenser.
Is stopped so that the outside air around the outdoor heat exchanger 3 does not flow, so that the outdoor heat exchanger 3 does not exchange heat as much as possible.

【００１９】ところで、上記再熱ドライ運転時に室内を
暖房ぎみにしながら除湿を行う場合、凝縮器である第１
熱交換器１０での凝縮温度を高くし、充分に熱交換（加
熱）を行う必要があるが、これに伴って蒸発温度も高く
なるため、除湿量が極端に減少してしまうことがある。
このため、上記空調装置１の室内機には、蒸発器として
機能する第２熱交換器１１の温度を制御する制御手段１
３が設けられている。以下にその具体的な制御方法につ
いて述べる。When the dehumidification is performed while the room is being heated during the reheating dry operation, the first condenser, which is a condenser, is used.
It is necessary to increase the condensation temperature in the heat exchanger 10 and perform sufficient heat exchange (heating). However, the evaporation temperature also increases, and the amount of dehumidification may decrease extremely.
Therefore, the indoor unit of the air conditioner 1 has a control unit 1 for controlling the temperature of the second heat exchanger 11 functioning as an evaporator.
3 are provided. The specific control method is described below.

【００２０】まず、図２に上記空調装置１の一実施の形
態を示す室内機の縦断面図を示す。図において、室内機
のケーシング１５には、その天面パネル１６のほぼ全面
に格子状の天面吸込口１７が形成され、前面パネル１８
のほぼ全面に格子状の前面吸込口１９が形成されてい
る。また、上記ケーシング１５内に配置された室内熱交
換器５は、背面側熱交換器１０（第１熱交換器）と前面
側熱交換器１１（第２熱交換器）とに分割され、これら
を逆Ｖ字状に組み合わせて構成されている。また逆Ｖ字
状の室内熱交換器５の内側には、室内ファンとしてクロ
スフローファン８が配設されている。そしてこのクロス
フローファン８の背後にスクロール部２０が形成され、
室内機のケーシング１５の前面側下部に開口する吹出口
２１になめらかに連設されている。この空調装置１にお
いては、前面側熱交換器１０において冷却・除湿した空
気と、背面側熱交換器１１において加熱した空気とを機
内において混合し、これを吹出口２１から吹出すことに
よって再熱ドライ運転が行えるようになっている。FIG. 2 is a longitudinal sectional view of an indoor unit showing an embodiment of the air conditioner 1 according to the present invention. In the drawing, a lattice-shaped top surface suction port 17 is formed on almost the entire surface of a top panel 16 of a casing 15 of an indoor unit.
A lattice-shaped front suction port 19 is formed on almost the entire surface of the substrate. The indoor heat exchanger 5 arranged in the casing 15 is divided into a rear heat exchanger 10 (first heat exchanger) and a front heat exchanger 11 (second heat exchanger). Are combined in an inverted V-shape. A cross flow fan 8 is arranged inside the inverted V-shaped indoor heat exchanger 5 as an indoor fan. A scroll portion 20 is formed behind the cross flow fan 8,
It is smoothly connected to the air outlet 21 which opens at the lower part on the front side of the casing 15 of the indoor unit. In the air conditioner 1, the air cooled and dehumidified in the front heat exchanger 10 and the air heated in the rear heat exchanger 11 are mixed in the machine, and the air is blown out from the air outlet 21 to reheat the air. Dry operation can be performed.

【００２１】また上記空調装置１の室内機には、上記制
御手段１３として、前面吸込口１９から供給される風量
を制御することが可能な風量制御手段が設けられてい
る。すなわちこの実施形態の場合、上記風量制御手段
は、前面吸込口１９を開閉することが可能なシャッター
２２と、上記シャッター２２を前面パネル１８の内側に
沿って移動させるモータ付ギア２３と、上記シャッター
２２を巻取る巻取り用器具２５とから構成されている。
さらに詳しく説明すると、上記ケーシング１５内の前面
パネル１８側の上方部には、棒状の巻取り用器具２５
が、その長手方向が上記ケーシング１５の長手方向と略
平行になるように配置されている。上記巻取り用器具２
５には、略長方形のシャッター２２の上端部が取付けら
れており、上記巻取り用器具２５に上記シャッター２２
を巻取ることができるように構成されている。さらに、
上記巻取り用器具２５より下方側の位置には、中心にモ
ータの回転軸２４を備えたギア２３が配置されており、
上記ギア２３と前面パネル１８との間にシャッター２２
が位置するように配置されている。また上記シャッター
２２には、その内側の面、すなわち上記ギア２３と向か
い合う方向にある面に、ギア２３と同じピッチの凹凸が
形成されており、上記シャッター２２に形成された凹凸
とギア２３とを噛み合わせることによって、ギア２３の
回転を上記シャッター２２に伝えることができるように
構成されている。そして上記構成により、前面パネル１
８の内側に沿って上記シャッター２２を上下方向にスラ
イドさせることにより、前面吸込口１９の開閉を行うこ
とができ、前面吸込口１９から供給される風量の制御を
行うことが可能となる。The indoor unit of the air conditioner 1 is provided with, as the control means 13, an air flow control means capable of controlling the air flow supplied from the front suction port 19. That is, in the case of this embodiment, the air volume control means includes a shutter 22 that can open and close the front suction port 19, a gear 23 with a motor that moves the shutter 22 along the inside of the front panel 18, And a winding device 25 for winding the 22.
More specifically, a rod-shaped winding device 25 is provided in the upper portion of the casing 15 on the front panel 18 side.
However, they are arranged such that their longitudinal direction is substantially parallel to the longitudinal direction of the casing 15. The above winding device 2
5 is provided with an upper end of a substantially rectangular shutter 22, and the shutter 22 is attached to the winding device 25.
Is wound up. further,
At a position below the winding device 25, a gear 23 having a motor rotation shaft 24 at the center is arranged.
A shutter 22 is provided between the gear 23 and the front panel 18.
Are arranged to be located. The shutter 22 has an inner surface, that is, a surface facing in the direction facing the gear 23, having irregularities having the same pitch as the gear 23, and the irregularities formed on the shutter 22 and the gear 23 are connected to each other. The gear 22 is configured to be able to transmit the rotation of the gear 23 to the shutter 22 by meshing. With the above configuration, the front panel 1
The front suction port 19 can be opened and closed by sliding the shutter 22 in the vertical direction along the inside of 8, and the amount of air supplied from the front suction port 19 can be controlled.

【００２２】次に、上記空調装置１の室内機の斜視図を
図４に示す。図に示すように、上記室内機本体１４の側
面下方部にはスリット２９が設けられており、その奥に
室内温度を測定する温度センサ２７と、室内湿度を測定
する湿度センサ２８とが設けられている。上記各センサ
２７、２８は、室内の温度と湿度とから露点温度を求め
るために設けられたもので、この露点温度から上記風量
制御手段を用いた前面側熱交換器１１の温度制御を行う
か否かの判断を行っている。このとき、上記各センサ２
７、２８は室内機内部に設けられているが、各センサ２
７、２８の前に設けられたスリット２９から室内空気の
出入りが行われるため、室内の湿度と温度とを正確に測
定することができ、これより、正確な露点温度が求めら
れる。Next, a perspective view of the indoor unit of the air conditioner 1 is shown in FIG. As shown in the figure, a slit 29 is provided at the lower side of the side surface of the indoor unit main body 14, and a temperature sensor 27 for measuring the indoor temperature and a humidity sensor 28 for measuring the indoor humidity are provided behind the slit 29. ing. Each of the sensors 27 and 28 is provided to determine the dew point temperature from the indoor temperature and humidity. Whether the temperature control of the front-side heat exchanger 11 using the air volume control means is performed based on the dew point temperature is performed. It is determined whether or not. At this time, each of the sensors 2
7 and 28 are provided inside the indoor unit.
Since indoor air enters and exits from the slits 29 provided before the gates 7 and 28, the indoor humidity and temperature can be accurately measured, and an accurate dew point temperature can be obtained.

【００２３】以上に述べた上記各センサ２７、２８と風
量制御手段を用いて前面吸込口１９の風量制御を行い、
室内を暖房ぎみにしながら除湿を行う際の制御方法につ
いて述べる。図５は上記風量制御手段を用いた制御動作
を説明するためのフローチャートである。The above-mentioned sensors 27 and 28 and the air volume control means are used to control the air volume of the front suction port 19,
A control method for performing dehumidification while heating the room is described. FIG. 5 is a flowchart for explaining a control operation using the air volume control means.

【００２４】まず、再熱ドライ運転中において、ステッ
プＳ１では、蒸発器として機能している前面側熱交換器
１１の温度が、各センサ２７、２８によって測定された
室内温度と湿度とから求めた露点温度より低いか否かに
ついての判断を行う。このとき、前面側熱交換器１１の
温度の方が高いか、あるいは等しい場合は、除湿能力が
不足する可能性があるということであるから、ステップ
Ｓ２に移行して、風量制御手段であるシャッター２２を
用いた風量分配制御が開始され、前面吸込口１９の開度
を狭くする。この後、ステップＳ３に進み、上記開度で
の運転状態が安定するまでこの状態を維持し（約１０分
間）、そして上記一定時間が経過した後、再びステップ
Ｓ１に戻って風量分配制御を行うか否かの判断を行う。
一方ステップＳ１において、露点温度の方が高ければ、
充分な除湿能力があるということであるから、上記シャ
ッター２２を用いた風量分配制御は行わず、現状態のま
ま維持する（ステップＳ４）。そして一定時間が経過し
た後、再びステップＳ１に戻る。First, during the reheating dry operation, in step S1, the temperature of the front-side heat exchanger 11 functioning as an evaporator was obtained from the room temperature and humidity measured by the sensors 27 and 28. A determination is made as to whether the temperature is lower than the dew point temperature. At this time, if the temperature of the front-side heat exchanger 11 is higher or equal, it means that the dehumidifying capacity may be insufficient. The air volume distribution control using 22 is started, and the opening of the front suction port 19 is narrowed. Thereafter, the process proceeds to step S3, and this state is maintained (about 10 minutes) until the operation state at the opening is stabilized (after about 10 minutes). Is determined.
On the other hand, in step S1, if the dew point temperature is higher,
Since there is sufficient dehumidification capability, the air volume distribution control using the shutter 22 is not performed, and the current state is maintained (step S4). Then, after a predetermined time has elapsed, the process returns to step S1 again.

【００２５】上記方法によれば、まず始めに各熱交換器
１０、１１への通過風量の比率が基本的に一定となるよ
うに、通常の再熱ドライ運転が開始される。このとき、
始めから風量制御を行わないのは、始めから前面側熱交
換器１１への風量を少なくすることによって、全体の運
転能力が低下してしまうのを防ぐためである。また本実
施形態によれば、室内温度と湿度とから求めた露点温度
より蒸発器である前面側熱交換器１１の温度の方が高い
か、あるいは等しい場合、自動的にシャッター２２によ
って前面吸込口１９の開度が狭められ、吸込風量が減少
するように調整されている。これによって前面側熱交換
器１１での熱交換が制限され、前面側熱交換器１１の温
度を下げることができ、この結果、除湿量を高めること
ができる。また、上記前面吸込口１９のシャッター２２
による開度調節は、連続的に行うことが可能であり、室
内を暖房ぎみにしながら再熱ドライ運転が実行されるま
で、繰り返し上記風量分配制御が行われる。また上記運
転が実行された場合でも、常にその状態が継続されるよ
うに、一定時間ごとに上記判断及び制御を行うよう構成
されている。以上のことにより、室内を暖房ぎみとする
ために凝縮器として機能する背面側熱交換器１０の凝縮
温度を上昇させても、風量制御手段によって、蒸発器と
して機能する前面側熱交換器１１の温度を低下させた
り、あるいは温度上昇を抑制することができるため、除
湿量を減少させることなく確実に再熱ドライ運転を実行
することができる。この結果、ユーザの望む室内環境を
実現でき、快適性が向上する。なおこのように前面側熱
交換器１１の温度を制御すれば、通常の再熱ドライ運転
時においても確実な除湿効果が得られるという利点があ
る。According to the above method, first, a normal reheating dry operation is started so that the ratio of the amount of air passing through each of the heat exchangers 10 and 11 is basically constant. At this time,
The reason why the air volume control is not performed from the beginning is to prevent the overall operation ability from being reduced by reducing the air volume to the front-side heat exchanger 11 from the beginning. Further, according to the present embodiment, when the temperature of the front-side heat exchanger 11 which is an evaporator is higher than or equal to the dew point temperature obtained from the room temperature and the humidity, the shutter 22 is automatically turned on by the shutter 22. The opening degree of the opening 19 is narrowed, and the suction air volume is adjusted so as to decrease. As a result, heat exchange in the front heat exchanger 11 is limited, and the temperature of the front heat exchanger 11 can be reduced, and as a result, the amount of dehumidification can be increased. Further, the shutter 22 of the front suction port 19 is provided.
Can be continuously adjusted, and the air volume distribution control is repeatedly performed until the reheat dry operation is performed while the room is being heated. Further, the configuration is such that the determination and the control are performed at regular intervals so that the state is always maintained even when the operation is performed. As described above, even if the condensing temperature of the rear-side heat exchanger 10 functioning as a condenser is increased in order to heat the room, even if the condensing temperature of the rear-side heat exchanger 10 is increased by the air volume control means, Since the temperature can be lowered or the rise in temperature can be suppressed, the reheat dry operation can be executed reliably without reducing the amount of dehumidification. As a result, the indoor environment desired by the user can be realized, and the comfort is improved. Controlling the temperature of the front-side heat exchanger 11 in this manner has an advantage that a reliable dehumidifying effect can be obtained even during a normal reheating dry operation.

【００２６】以上にこの発明の具体的な実施の形態につ
いて説明したが、この発明は上記実施の形態に限定され
るものではなく、この発明の範囲内で種々変更して実施
することが可能である。まず上記実施形態において、風
量制御手段による風量制御を行うか否かを判断する際、
蒸発器である前面側熱交換器１１の温度と露点温度とを
比較することによって判断したが、前面側熱交換器１１
の温度が、室内湿度５０％以下とするために必要な蒸発
温度であるか否かを比較することによって判断してもよ
い。この場合に必要とする蒸発温度は、センサ等を用い
て求めることも可能であるが、使用実態等を考慮して事
前に特定温度を設定しておいてもよい。Although the specific embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and various modifications can be made within the scope of the present invention. is there. First, in the above embodiment, when determining whether to perform the air volume control by the air volume control unit,
It was determined by comparing the temperature of the front-side heat exchanger 11 as an evaporator with the dew point temperature.
May be determined by comparing whether or not the temperature is the evaporation temperature necessary to make the room humidity 50% or less. The evaporating temperature required in this case can be obtained by using a sensor or the like, but a specific temperature may be set in advance in consideration of the actual use conditions and the like.

【００２７】また上記実施形態では、風量制御手段にシ
ャッター２２を用いて、前面吸込口１９から供給される
風量を制御したが、図３に示すように、上記室内機にお
いて、前面吸込口１９を外側から覆うことが可能な前面
蓋３０を設けることによって、吸込風量を制御すること
も可能である。すなわち上記前面蓋３０は、略長方形の
板の上下方向をわずかに湾曲させた形を有しており、そ
の凹部が内側を向くように配置されると共に、その下端
部が前面吸込口１９下方部のケーシング１５に回動可能
に取付けられている。また、上記前面蓋３０が取付けら
れた取付部３１の中心には、モータの回転軸３２が設け
られており、モータを駆動することによって、上記前面
蓋３０が取付部３１の回転軸３２を中心として内外に回
動するように構成されている。従って、上記前面蓋３０
の回動によって前面吸込口１９の開度を調節し、吸込風
量を制御することができる。In the above embodiment, the air volume supplied from the front suction port 19 is controlled by using the shutter 22 as the air flow control means. However, as shown in FIG. By providing the front cover 30 that can be covered from the outside, it is also possible to control the amount of suction air. That is, the front cover 30 has a shape in which the upper and lower sides of a substantially rectangular plate are slightly curved, and the concave portion thereof is arranged to face inward, and the lower end portion thereof is located below the front suction port 19. Is rotatably attached to the casing 15. A motor rotation shaft 32 is provided at the center of the mounting portion 31 to which the front cover 30 is mounted. By driving the motor, the front cover 30 is centered on the rotation shaft 32 of the mounting portion 31. It is configured to rotate inward and outward. Therefore, the front cover 30
The opening degree of the front suction port 19 can be adjusted by the rotation of, and the amount of suction air can be controlled.

【００２８】さらに上記方法によれば、蒸発器として機
能する前面側熱交換器１１を通過する風量を制御するこ
と、すなわち前面吸込口１９からの吸込風量を少なくす
ることによって、上記前面側熱交換器１１の温度を下
げ、除湿量を高めたが、前面側熱交換器１１に流入する
冷媒の圧力を制御することによって、前面側熱交換器１
１の蒸発温度を低下し、除湿量を高めることも可能であ
る。たとえば、圧力制御手段として上記前面側熱交換器
１１の冷媒経路の入口側に設けた減圧機構１２を利用
し、上記減圧機構１２の開度を狭くし減圧量を大きくす
ることによって、前面側熱交換器１１での蒸発温度を下
げ、除湿量を高めることもできる。このように構成すれ
ば、特別な機構を付加することなく実施可能であるの
で、構成付加によるコストアップを抑制できる。なお上
記実施形態では、室内温度センサと湿度センサを室内機
本体１４に設けたが、室内の温度と湿度を測定すること
ができればどこに設けてもよい。Further, according to the above method, by controlling the amount of air passing through the front-side heat exchanger 11 functioning as an evaporator, that is, by reducing the amount of air sucked from the front-side suction port 19, the above-mentioned front-side heat exchange is performed. Although the temperature of the heat exchanger 11 was lowered and the amount of dehumidification was increased, the pressure of the refrigerant flowing into the front heat exchanger 11 was controlled so that the front heat exchanger 1
It is also possible to lower the evaporation temperature of 1 and to increase the dehumidification amount. For example, by using a pressure reducing mechanism 12 provided on the inlet side of the refrigerant path of the front side heat exchanger 11 as the pressure control means, and narrowing the opening of the pressure reducing mechanism 12 to increase the pressure reduction amount, the front side heat The evaporation temperature in the exchanger 11 can be lowered to increase the dehumidification amount. With this configuration, the present invention can be implemented without adding a special mechanism, so that an increase in cost due to the additional configuration can be suppressed. In the above embodiment, the indoor temperature sensor and the humidity sensor are provided in the indoor unit main body 14, but may be provided anywhere as long as the indoor temperature and humidity can be measured.

【００２９】[0029]

【発明の効果】以上のように請求項１の空調装置によれ
ば、室内を暖房ぎみにしながら再熱ドライ運転を行うよ
うな場合において、制御手段を用いて第２熱交換器の温
度を制御するため、除湿量を減少させることなく確実に
再熱ドライ運転を実行することができる。この結果、ユ
ーザが求める室内環境を実現でき、快適性が向上する。
なおこのように第２熱交換器の温度を制御すれば、通常
の再熱ドライ運転時においても、確実な除湿効果を得ら
れるという利点がある。As described above, according to the air conditioner of the first aspect, the temperature of the second heat exchanger is controlled by using the control means in the case where the reheat dry operation is performed while the room is being heated. Therefore, the reheat dry operation can be reliably performed without reducing the amount of dehumidification. As a result, the indoor environment desired by the user can be realized, and the comfort is improved.
Controlling the temperature of the second heat exchanger in this way has the advantage that a reliable dehumidifying effect can be obtained even during a normal reheating dry operation.

【００３０】また請求項２の空調装置では、精度のよい
除湿制御が行え、この結果、ユーザが求める室内環境に
応じた再熱ドライ運転を一段と確実に行うことが可能と
なる。In the air conditioner according to the second aspect, accurate dehumidification control can be performed, and as a result, the reheat dry operation according to the indoor environment required by the user can be more reliably performed.

【００３１】さらに請求項３の空調装置では、簡素な構
成でもって確実に除湿量を高めることができる。Further, in the air conditioner of the third aspect, the amount of dehumidification can be reliably increased with a simple configuration.

【００３２】上記請求項４の空調装置では、簡素な構成
でもって確実に除湿量を高めることができる。In the air conditioner of the fourth aspect, the amount of dehumidification can be reliably increased with a simple configuration.

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

【図１】本発明の一実施の形態である空調装置の構成を
示す冷媒回路図である。FIG. 1 is a refrigerant circuit diagram illustrating a configuration of an air conditioner according to an embodiment of the present invention.

【図２】上記空調装置の一実施の形態を示す室内機の縦
断面図である。FIG. 2 is a longitudinal sectional view of an indoor unit showing one embodiment of the air conditioner.

【図３】上記空調装置の他の実施形態を示す室内機の縦
断面図である。FIG. 3 is a longitudinal sectional view of an indoor unit showing another embodiment of the air conditioner.

【図４】上記空調装置の室内機の斜視図である。FIG. 4 is a perspective view of an indoor unit of the air conditioner.

【図５】上記空調装置の制御動作を説明するためのフロ
ーチャートである。FIG. 5 is a flowchart illustrating a control operation of the air conditioner.

【符号の説明】[Explanation of symbols]

１ 空調装置 ５ 室内熱交換器 １０ 第１熱交換器（背面側熱交換器） １１ 第２熱交換器（前面側熱交換器） １２ 減圧機構 １３ 制御手段 １８ 前面パネル １９ 前面吸込口 ２２ シャッター ２３ ギア ２５ 巻取り用器具 ２７ 温度センサ ２８ 湿度センサ ３０ 前面蓋 ３１ 取付部 DESCRIPTION OF SYMBOLS 1 Air conditioner 5 Indoor heat exchanger 10 1st heat exchanger (back side heat exchanger) 11 2nd heat exchanger (front side heat exchanger) 12 Decompression mechanism 13 Control means 18 Front panel 19 Front inlet 22 Shutter 23 Gear 25 Winding device 27 Temperature sensor 28 Humidity sensor 30 Front cover 31 Mounting part

Claims (4)

【特許請求の範囲】[Claims] 【請求項１】 直列に接続された第１熱交換器（１０）
と第２熱交換器（１１）とから成る室内熱交換器（５）
と、上記各熱交換器（１０）（１１）の間に介設された
減圧機構（１２）とを有する空調装置であって、上記第
１熱交換器（１０）を凝縮器として機能させる一方、第
２熱交換器（１１）を蒸発器として機能させて、室内空
気を冷却して除湿した後に再び加熱して室内に戻す再熱
ドライ運転が可能な空調装置において、上記再熱ドライ
運転時に、蒸発器として機能する第２熱交換器（１１）
の温度を制御する制御手段（１３）を設けたことを特徴
とする空調装置。1. A first heat exchanger (10) connected in series
Indoor heat exchanger (5) comprising a heat exchanger and a second heat exchanger (11)
And a pressure reducing mechanism (12) interposed between the heat exchangers (10) and (11), wherein the first heat exchanger (10) functions as a condenser. In the air conditioner in which the second heat exchanger (11) functions as an evaporator to cool and dehumidify the indoor air, then heat it again and return it to the room, , A second heat exchanger functioning as an evaporator (11)
An air conditioner comprising a control means (13) for controlling the temperature of the air conditioner. 【請求項２】 室内温度センサ（２７）と、湿度センサ
（２８）とを設け、上記各センサ（２７）（２８）によ
って測定された温度と湿度とから露点温度を求めると共
に、上記露点温度から第２熱交換器（１１）の温度制御
を行うことを特徴とする請求項１の空調装置。2. An indoor temperature sensor (27) and a humidity sensor (28) are provided to determine a dew point temperature from the temperature and humidity measured by each of the sensors (27) and (28). The air conditioner according to claim 1, wherein the temperature of the second heat exchanger (11) is controlled. 【請求項３】 上記制御手段（１３）は、第２熱交換器
（１１）への風量を制御する風量制御手段であることを
特徴とする請求項１の空調装置。3. An air conditioner according to claim 1, wherein said control means (13) is an air volume control means for controlling an air volume to said second heat exchanger (11). 【請求項４】 上記制御手段（１３）は、上記減圧機構
（１２）を開度可変に構成して成る圧力制御手段である
ことを特徴とする請求項１の空調装置。4. An air conditioner according to claim 1, wherein said control means (13) is a pressure control means comprising a variable opening of said pressure reducing mechanism (12).
JP30854499A 1999-10-29 1999-10-29 Air conditioner Pending JP2001124434A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
JP30854499A JP2001124434A (en) 1999-10-29 1999-10-29 Air conditioner
KR10-2002-7005192A KR100491718B1 (en) 1999-10-29 2000-10-23 Air conditioner
AT00969980T ATE423949T1 (en) 1999-10-29 2000-10-23 AIR CONDITIONER
DE60041649T DE60041649D1 (en) 1999-10-29 2000-10-23 AIR CONDITIONING
AU79536/00A AU7953600A (en) 1999-10-29 2000-10-23 Air conditioner
EP00969980A EP1227286B1 (en) 1999-10-29 2000-10-23 Air conditioner
CNB008149356A CN1196902C (en) 1999-10-29 2000-10-23 Air conditioner
ES00969980T ES2321685T3 (en) 1999-10-29 2000-10-23 CLIMATE CONTROL
PCT/JP2000/007369 WO2001033146A1 (en) 1999-10-29 2000-10-23 Air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP30854499A JP2001124434A (en) 1999-10-29 1999-10-29 Air conditioner

Publications (1)

Publication Number Publication Date
JP2001124434A true JP2001124434A (en) 2001-05-11

Family

ID=17982316

Family Applications (1)

Application Number Title Priority Date Filing Date
JP30854499A Pending JP2001124434A (en) 1999-10-29 1999-10-29 Air conditioner

Country Status (9)

Country Link
EP (1) EP1227286B1 (en)
JP (1) JP2001124434A (en)
KR (1) KR100491718B1 (en)
CN (1) CN1196902C (en)
AT (1) ATE423949T1 (en)
AU (1) AU7953600A (en)
DE (1) DE60041649D1 (en)
ES (1) ES2321685T3 (en)
WO (1) WO2001033146A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008014605A (en) * 2006-07-10 2008-01-24 Matsushita Electric Ind Co Ltd Air conditioner

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002130863A (en) * 2000-10-19 2002-05-09 Chikayoshi Sato Dehumidifying method
KR100911789B1 (en) 2003-01-15 2009-08-12 엘지전자 주식회사 Air conditioner for dehumidification
EP1739366B1 (en) * 2004-03-31 2017-07-05 Daikin Industries, Ltd. Air conditioning system
KR100710057B1 (en) * 2006-02-27 2007-04-20 주식회사 대우일렉트로닉스 Cooling system for air-conditioner
JP4923794B2 (en) * 2006-07-06 2012-04-25 ダイキン工業株式会社 Air conditioner
KR101260418B1 (en) 2012-07-30 2013-05-07 정종인 Dryer and cold storage system using heat pump and method for operating the system
JP2018025344A (en) * 2016-08-09 2018-02-15 パナソニックＩｐマネジメント株式会社 Air conditioner
JP2018025342A (en) * 2016-08-09 2018-02-15 パナソニックＩｐマネジメント株式会社 Air conditioner
DE102017109552A1 (en) * 2017-05-04 2018-11-08 Weiss-Doppelbodensysteme GmbH Air conditioner for double floor systems
CN112797657B (en) * 2019-10-28 2024-06-21 广东美的制冷设备有限公司 Air conditioner and control method thereof
CN115789791B (en) * 2022-10-28 2024-11-08 珠海格力电器股份有限公司 Air conditioning system and control method

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2658691B2 (en) * 1991-01-29 1997-09-30 三菱電機株式会社 Dehumidifier
JPH0518630A (en) * 1991-07-10 1993-01-26 Toshiba Corp Air conditioner
JP2945512B2 (en) * 1991-07-19 1999-09-06 株式会社日立製作所 Air conditioner
US5341650A (en) * 1992-03-13 1994-08-30 Kabushiki Kaisha Toshiba Air conditioning apparatus having a plurality of inlets for taking in indoor air at a plurality of portions of main body thereof
JP3190139B2 (en) * 1992-10-13 2001-07-23 東芝キヤリア株式会社 Air conditioner
JP3205098B2 (en) * 1992-12-22 2001-09-04 富士通システムコンストラクション株式会社 Air conditioner
JP3404968B2 (en) * 1995-03-16 2003-05-12 株式会社日立製作所 Air conditioner
US5678417A (en) * 1995-06-28 1997-10-21 Kabushiki Kaisha Toshiba Air conditioning apparatus having dehumidifying operation function
JP3410859B2 (en) * 1995-06-28 2003-05-26 東芝キヤリア株式会社 Air conditioner
JPH11248288A (en) * 1998-03-04 1999-09-14 Sanyo Electric Co Ltd Air conditioner

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008014605A (en) * 2006-07-10 2008-01-24 Matsushita Electric Ind Co Ltd Air conditioner

Also Published As

Publication number Publication date
KR100491718B1 (en) 2005-05-25
CN1384910A (en) 2002-12-11
ES2321685T3 (en) 2009-06-10
DE60041649D1 (en) 2009-04-09
WO2001033146A1 (en) 2001-05-10
EP1227286A4 (en) 2003-05-07
ATE423949T1 (en) 2009-03-15
KR20020070973A (en) 2002-09-11
EP1227286B1 (en) 2009-02-25
AU7953600A (en) 2001-05-14
EP1227286A1 (en) 2002-07-31
CN1196902C (en) 2005-04-13

Similar Documents

Publication Publication Date Title
CN108507138B (en) Air conditioner and control method thereof
US7987680B2 (en) Air conditioner
JPH04143541A (en) Air conditioner
EP1705433A1 (en) Air conditioner
JP2001124434A (en) Air conditioner
JP2000158933A (en) Air conditioner for vehicle
JP2004131033A (en) Air-conditioner
WO2005010443A1 (en) Multiple room-type air conditioner and method of controlling the same
JP4325119B2 (en) Air conditioner
KR20180078833A (en) Air conditioner and method for controlling the same
JP4039100B2 (en) Air conditioner
JPH08178393A (en) Air conditioning apparatus
JP2004239609A (en) Air conditioner
JP2651328B2 (en) Method and apparatus for controlling hot gas bypass circuit of refrigeration circuit
JP2000025446A (en) Air conditioner
CN115654570A (en) Fresh air conditioner, control method thereof and air conditioner
JPH06143996A (en) Vehicle air conditioner
JP2009109134A (en) Ventilation device
KR101362664B1 (en) Air conditioning apparatus
JP3297105B2 (en) Air conditioner
JPH05248690A (en) Air conditioner
JP3991202B2 (en) Air conditioner
JP3522076B2 (en) Air conditioner
KR20110085396A (en) Outdoor unit of air conditioner
JPH062920A (en) Controller for air conditioner

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20060830

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20090929

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20100706