JPH01222137A - Air conditioning device - Google Patents
Air conditioning deviceInfo
- Publication number
- JPH01222137A JPH01222137A JP63047853A JP4785388A JPH01222137A JP H01222137 A JPH01222137 A JP H01222137A JP 63047853 A JP63047853 A JP 63047853A JP 4785388 A JP4785388 A JP 4785388A JP H01222137 A JPH01222137 A JP H01222137A
- Authority
- JP
- Japan
- Prior art keywords
- humidity
- temperature
- difference
- expansion valve
- electronic expansion
- 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
Links
- 238000004378 air conditioning Methods 0.000 title claims description 12
- 238000001816 cooling Methods 0.000 claims description 29
- 238000010438 heat treatment Methods 0.000 claims description 24
- 238000005057 refrigeration Methods 0.000 claims description 9
- 230000007423 decrease Effects 0.000 claims description 7
- 239000003507 refrigerant Substances 0.000 claims description 7
- 238000003303 reheating Methods 0.000 claims description 6
- 230000003247 decreasing effect Effects 0.000 claims description 4
- 230000002441 reversible effect Effects 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 7
- 238000005070 sampling Methods 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 101150068029 RH11 gene Proteins 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 230000003044 adaptive effect Effects 0.000 description 1
- 230000001174 ascending effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 238000007791 dehumidification Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
Landscapes
- Air Conditioning Control Device (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は電算機室用など全年間を通じて恒温・恒温を保
持させるのに適した空気調和装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an air conditioner suitable for maintaining a constant temperature throughout the year, such as in a computer room.
(従来の技術)
この種の恒温・恒温装置としては例えば実開昭59−7
9744号公報によって開示されたものがあって電算機
室等の空気調和用に多用されているが、これは上限値の
オン作動点と下限値のオフ作動点との間に2℃前後のデ
ィファレンシャルを有する温度調節器と、上限値のオン
作動点と下限値のオフ作動点との間に10%相対湿度前
後のディファレンシャルを有する湿度調節器との両信号
のうち、いずれか一方のオン作動点で発信する信号によ
って冷凍装置の圧縮機を運転し、各オフ作動点で発信す
る信号が共に出されて圧縮機を停止させ、温度及び湿度
を所定領域内に維持しようとするものである。(Prior art) As this type of constant temperature/constant temperature device, for example,
There is a system disclosed in Japanese Patent No. 9744, which is widely used for air conditioning in computer rooms, etc., but this is a differential with a temperature of around 2°C between the upper limit ON operating point and the lower limit OFF operating point. and a humidity controller that has a differential of around 10% relative humidity between the upper limit ON operation point and the lower limit OFF operation point. The compressor of the refrigeration system is operated by the signal transmitted at each off operating point, and the signals transmitted at each OFF operating point are issued together to stop the compressor and maintain the temperature and humidity within a predetermined range.
(発明が解決しようとする課題)
上述の従来装置はオン・オフ方式によってステップ状に
温・湿度を制御するものであるから、空調対象域にはど
うしも前記ディファレンシャルと同じか若しくは若干幅
が広い温度、湿度の変化域が存することは避けられなく
、従って温・湿度制御が粗くなるのが問題であった。(Problems to be Solved by the Invention) Since the above-mentioned conventional device controls temperature and humidity in steps using an on-off method, the range to be air-conditioned necessarily has a width that is the same as or slightly wider than that of the differential. It is inevitable that there will be a range of changes in temperature and humidity, and therefore the problem is that temperature and humidity control becomes rough.
なお、ディファレンシャルを可及的に差が小さくなるよ
うにすることは理論的に可能であるが、実際には、圧m
機の発停頻度が大となって機器寿命、ランニゲコストに
悪影響を与えるばかりでなく、ハンチング現象を起こす
ことが考えられるので実用的な方策とは云い難いもので
ある。Although it is theoretically possible to make the difference in the differential as small as possible, in reality, the pressure m
It is difficult to say that this is a practical measure because the frequency of starting and stopping the aircraft increases, which not only has a negative effect on equipment life and running costs, but also causes a hunting phenomenon.
このような問題点に対処して本発明は成されたものであ
って、弁開度の制御が容易かつ確実な構造の電子膨張弁
を従来多用されている感温膨張弁に替えて用いると共に
、この電子膨張弁を対象域の室温度及び室湿度によって
開度制御することにより圧縮機の発停を回避した連続安
定運転を単純構造の冷凍回路により可能ならしめると同
時に高制御精度の下で温度及び湿度の安定をはからしめ
たものであって、最少必y限度の機器構成による経済性
に富み、かつ、コンパクトを可能とする実用装置の実現
を果たさせることを目的とする。The present invention has been made to address these problems, and it uses an electronic expansion valve with a structure that allows easy and reliable valve opening control in place of the temperature-sensitive expansion valve that has been widely used in the past. By controlling the opening of this electronic expansion valve according to the room temperature and humidity of the target area, continuous stable operation that avoids the start and stop of the compressor is made possible with a simple refrigeration circuit, and at the same time, with high control accuracy. The object of the present invention is to realize a practical device that is stable in temperature and humidity, has a minimum equipment configuration, is economical, and is compact.
(課題を解決するための手段)
そこで本発明は添付図面を参照して明らかなように、圧
縮機(1)、室外側に設けた凝縮器(2)、第1電子膨
張弁(3)、室内側に設けた蒸発器(4)により冷凍サ
イクルを形成し、前記蒸発器(4)に対し空気流通方向
の下手側に再熱器(5)を配置して該再熱器(5)と第
2電子膨張弁(6)とを直列に接続した冷媒回路を、凝
縮器(2)と第1電子膨張弁(3)との直列接続になる
冷媒回路に並列接続せしめる一方、前記蒸発器(4)の
吸込空気温度を検知する室温検知器(9)と、蒸発器(
4)の吸込空気湿度を検知する湿度検知器0〔と、室温
検知器(9)による室温が設定温度に比し高く、かつ、
所定温度差を超える値であると、第1電子膨張弁(3)
をそのときの温度差(ΔT)に比例した開度に制御する
第1温度制御手段Q5)と、前記温度差(ΔT)が所定
温度差以内のときに、湿度検知器αωによる室湿度が設
定湿度に対して所定湿度差を超える値であると、室湿度
の方が高いときは第2電子膨張弁(6)をそのときの湿
度差(ΔRH11)に比例した開度に開かせ、逆に低い
ときは第2電子膨張弁(6)をそのときの湿度差(ΔR
H)I)に比例した開度に閉じさせる再熱量制御手段a
1と、前記湿度差(ΔRHH)が所定湿度差以内のとき
に、前記温度差(6丁)が所定湿度差を超える値である
と、室温が設定温度よりも高い場合は該温度差(ΔT)
に比例した開度に第2電子膨張弁(6)を閉じさせ、逆
に低い場合は該温度差(ΔT)に比例した開度に第2電
子膨張弁(6)を開かせる第2温度制御手段(2)とを
設けたことを特徴とする。(Means for Solving the Problems) Therefore, as is clear with reference to the accompanying drawings, the present invention provides a compressor (1), a condenser (2) provided on the outdoor side, a first electronic expansion valve (3), A refrigerating cycle is formed by an evaporator (4) provided on the indoor side, and a reheater (5) is arranged on the downstream side of the evaporator (4) in the air flow direction. A refrigerant circuit in which the second electronic expansion valve (6) is connected in series is connected in parallel to a refrigerant circuit in which the condenser (2) and the first electronic expansion valve (3) are connected in series, while the evaporator ( 4), a room temperature detector (9) that detects the intake air temperature, and an evaporator (
4) The room temperature measured by the humidity detector 0 [that detects the suction air humidity] and the room temperature detector (9) is higher than the set temperature, and
If the value exceeds the predetermined temperature difference, the first electronic expansion valve (3)
a first temperature control means Q5) that controls the opening to an opening proportional to the temperature difference (ΔT) at that time; and when the temperature difference (ΔT) is within a predetermined temperature difference, the room humidity is set by the humidity detector αω. If the value exceeds a predetermined humidity difference with respect to humidity, when the room humidity is higher, the second electronic expansion valve (6) is opened to an opening proportional to the humidity difference (ΔRH11) at that time, and vice versa. When the humidity is low, the second electronic expansion valve (6) is
H) Reheat amount control means a for closing to an opening proportional to I)
1, and when the humidity difference (ΔRHH) is within a predetermined humidity difference, and the temperature difference (6 dens) exceeds the predetermined humidity difference, if the room temperature is higher than the set temperature, the temperature difference (ΔT )
A second temperature control that closes the second electronic expansion valve (6) to an opening proportional to the temperature difference (ΔT), and, conversely, opens the second electronic expansion valve (6) to an opening proportional to the temperature difference (ΔT) when the temperature is low. The present invention is characterized by comprising means (2).
また、本発明は室温と設定温度との前記温度差(ΔT)
が前記所定温度差よりも大きい値の高設定温度差を超え
る場合に第2電子膨張弁(6)を閉じさせる再熱制限手
段α瞬を付設してなることが望ましい。Further, the present invention provides the temperature difference (ΔT) between the room temperature and the set temperature.
It is preferable that reheat limiting means α instantaneous is provided for closing the second electronic expansion valve (6) when the temperature difference exceeds a high set temperature difference which is larger than the predetermined temperature difference.
さらに、冷凍サイクルを冷・暖房が可能な可逆冷凍サイ
クルに形成すると共に、前記第1温度制御手段αつ及び
前記第2温度制御手段Q6)を冷房、暖房の何れにも対
応し得る構成となし、また、空調負荷が大で前記温度差
(ΔT)が前記所定温度差よりも大きい値の高設定温度
差を超える場合に、四路切換弁(7)を空調負荷条件に
応じた冷房側又は暖房側に切り換える冷暖房制御手段α
匂を設けることが好ましい。Furthermore, the refrigeration cycle is formed into a reversible refrigeration cycle capable of cooling and heating, and the first temperature control means α and the second temperature control means Q6) are configured to be capable of handling both cooling and heating. In addition, when the air conditioning load is large and the temperature difference (ΔT) exceeds a high set temperature difference that is larger than the predetermined temperature difference, the four-way switching valve (7) is switched to the cooling side or to the cooling side according to the air conditioning load condition. Air conditioning control means α that switches to the heating side
It is preferable to provide a scent.
一方、加湿器(11)を再熱器(5)に対し空気流通方
向の下手側に配設する一方、前記再熱量制御手段aηに
より第2電子膨張弁(6)が全閉制御されていて、かつ
、室湿度が前記設定湿度よりも低い場合に前記加湿器α
υを加湿運転させる加湿制御手段amを付設したことを
好ましい構成とする。On the other hand, the humidifier (11) is disposed on the downstream side of the reheater (5) in the air flow direction, and the second electronic expansion valve (6) is fully closed controlled by the reheat amount control means aη. , and when the room humidity is lower than the set humidity, the humidifier α
A preferable configuration is that a humidification control means am for operating υ in humidification is provided.
本発明はまた、圧縮機(11が空調負荷に対応して周波
数制御されるインバータ駆動方式の容量可変圧縮機であ
り、一方、前記湿度差(ΔRH)が所定湿度差以内であ
って、室湿度の方が低く、かつ湿度増加傾向のときはイ
ンバータ@の出力周波数を下げ、逆に湿度減少傾向のと
きは出力周波数を上げ、また、室温度の方が高く、かつ
湿度増加傾向のときは出力周波数を上げ、逆に湿度減少
傾向のときは出力周波数を下げ、さらに、湿度差(ΔR
HH)が所定湿度差を超えているときはこの湿度差(Δ
RH11)に対応して室湿度の方が高いときはインバー
タQ2)の出力周波数を上げ、逆に低いときは出力周波
数を下げる調湿制御手段(21)を付設したことを好ま
しい構成とするものである。The present invention also provides an inverter-driven variable capacity compressor in which the compressor (11) is frequency-controlled in accordance with the air conditioning load, and on the other hand, the humidity difference (ΔRH) is within a predetermined humidity difference, and the room humidity is lower and the humidity is increasing, the output frequency of the inverter @ is lowered; conversely, when the humidity is decreasing, the output frequency is increased, and when the room temperature is higher and the humidity is increasing, the output frequency is increased. Increase the frequency, and conversely lower the output frequency when the humidity is decreasing, and further increase the humidity difference (ΔR
When the humidity difference (HH) exceeds the predetermined humidity difference, this humidity difference (Δ
A preferred configuration includes a humidity control means (21) that increases the output frequency of the inverter Q2) when the room humidity is high, and lowers the output frequency when the room humidity is low, in response to RH11). be.
(作用)
本発明は室内の温度、湿度を検知して、室内側熱交換器
(4)の冷却文は加熱能力及び再熱器(5)の再熱能力
を直接的に制御するようにしており、しかもこの制御が
2個の電子膨張弁(3)、 f6)によって無段階な連
続的に行われるので制御精度を高くすると同時に高応答
制御が可能である。(Function) The present invention detects indoor temperature and humidity, and directly controls the cooling capacity of the indoor heat exchanger (4) and the reheating capacity of the reheater (5). Furthermore, since this control is performed steplessly and continuously by the two electronic expansion valves (3) and f6), it is possible to increase control precision and at the same time perform high response control.
(実施例)
第1図は本発明の実施例に係る装置回路図であって、圧
縮機(1)、四路切換弁(7)、冷房時の凝縮器となる
室外側熱交換器(2)、第1電子膨張弁(3)冷房時の
蒸発器となる室内側熱交換器(4)、アキュムレータ(
8)によって公知の可逆冷凍サイクルを形成しており、
四路切換弁(7)の切換操作で請求項3の発明に係る冷
房と暖房の運転が可能であって、普通には専ら冷房運転
が年間の殆どを通じて行われる使用態様となっている。(Embodiment) Fig. 1 is a circuit diagram of an apparatus according to an embodiment of the present invention, which includes a compressor (1), a four-way switching valve (7), an outdoor heat exchanger (2) which serves as a condenser during cooling. ), first electronic expansion valve (3), indoor heat exchanger (4) which serves as an evaporator during cooling, and accumulator (
8) forms a known reversible refrigeration cycle,
Cooling and heating operations according to the invention of claim 3 can be performed by switching the four-way switching valve (7), and normally the cooling operation is exclusively carried out most of the year.
そして、圧縮機(1)、四路切換弁(7)、凝縮器(2
)、アキュムレータ(8)を要素として室外機を構成し
、第1電子膨張弁(3)、蒸発器(4)を要素として室
内機を構成しており、室内機においては、蒸発器(4)
の空気流入口部に吸込空気温度を検知して室温信号を発
信する室温検知器(9)の感温部としてのサーミスタが
配置され、同じく空気流入口部に吸込空気湿度を検知し
て室温度信号を発信する湿度検知器α0)の感湿素子が
配置され、さらに蒸発器(4)の出口配管及び入口配管
には過熱度検知器の感温部としての第1サーミスタQ3
)及び第2サーミスタQ4)が添着されている。Then, a compressor (1), a four-way switching valve (7), a condenser (2
), an accumulator (8) constitutes an outdoor unit, and a first electronic expansion valve (3) and an evaporator (4) constitute an indoor unit.
A thermistor as a temperature-sensing part of a room temperature detector (9) that detects the temperature of the suction air and sends a room temperature signal is placed at the air inlet, and also detects the humidity of the suction air and detects the room temperature. A humidity sensing element of a humidity detector α0) that transmits a signal is arranged, and a first thermistor Q3 as a temperature sensing part of a superheat detector is arranged in the outlet piping and inlet piping of the evaporator (4).
) and a second thermistor Q4) are attached.
図示装置はさらに再熱回路が前記冷凍サイクルに付設さ
れており、この再熱回路は蒸発器(4)に対し空気流通
方向の下手側に配置される再熱2m (5)と流入口を
再熱器(5)側とした第2電子膨張弁(6)とを直列に
接続した回路構成であって、この再熱回路は、凝縮器(
2)と第1電子膨張弁(3)との直列接続になる冷媒回
路に対し並列接続せしめることによって成立する。The illustrated device further includes a reheat circuit attached to the refrigeration cycle, and this reheat circuit connects a reheat 2m (5) located downstream of the evaporator (4) in the air flow direction and an inlet. The circuit has a circuit configuration in which the second electronic expansion valve (6), which is connected to the heating device (5), is connected in series, and this reheating circuit is connected to the condenser (5).
2) and the first electronic expansion valve (3) are connected in parallel to the refrigerant circuit which is connected in series.
第1電子膨張弁(3)と第2電子膨張弁(6)とは弁軸
に対しパルスモータ出力軸を連結させてなる電気駆動形
の膨張弁であって、極性を変えたパルス出力をパルスモ
ータに与えるとパルス数に比例した開度で開き側又は絞
り側に弁が制御されるようになっており、第1電子膨張
弁(3)は前記過熱度検知器の発信信号によって作動す
る制御回路(図示せず)と、後述する第1温度制御手段
αつとからのパルス出力で弁開度調節が成され、また、
第2電子膨張弁(6)は再熱量制御手段0ηと、再熱制
限手段0榎と、第2温度制御手段Q61と、冷暖房制御
手段α匂とからのパルス出力で弁開度調節が成されるよ
うになっている。The first electronic expansion valve (3) and the second electronic expansion valve (6) are electrically driven expansion valves in which a pulse motor output shaft is connected to the valve shaft, and the pulse output with changed polarity is pulsed. When applied to the motor, the valve is controlled to the opening side or the throttle side with an opening degree proportional to the number of pulses, and the first electronic expansion valve (3) is controlled to be activated by the signal transmitted from the superheat degree detector. The valve opening degree is adjusted by a pulse output from a circuit (not shown) and a first temperature control means α, which will be described later.
The second electronic expansion valve (6) has its valve opening adjusted by pulse outputs from the reheat amount control means 0η, the reheat limiting means 0, the second temperature control means Q61, and the air conditioning control means α. It has become so.
一方、圧縮機(11はインバータ亜により回転制御され
るモータに連結させていて、このインバータ(転)は空
調負荷に応じて出力周波数が制御される公知の制御方式
に加えて、請求項5に係る構成の調湿制御手段(21)
からのパルス出力で周波数制御が成される。On the other hand, the compressor (11) is connected to a motor whose rotation is controlled by an inverter, and in addition to the known control method in which the output frequency of the inverter is controlled according to the air conditioning load, Humidity control means (21) having such a configuration
Frequency control is achieved by the pulse output from.
さらに、上記装置は室内機における再熱器(5)に近接
して該再熱器(5)よりも風下側に加湿器ODを配設し
ており、この加湿器αυは、請求項4の構成である加湿
制御手段(2のからの出力で加湿運転が成される。Further, in the above device, a humidifier OD is disposed in the vicinity of the reheater (5) in the indoor unit and on the leeward side of the reheater (5), and the humidifier αυ according to claim 4 is The humidifying operation is performed by the output from the humidifying control means (2).
上記空気調和装置の制御系を第2図乃至第4図を併せ参
照して次に説明すると、
◎ 第1温度制御手段aω、
室温検知器(9)からの室温信号と室温設定器からの設
定温度信号とを入力信号として受けて第1電子膨張弁(
3)に出力を与えるものであって、室温から設定温度を
減じた温度差(ΔT)が±1℃の範囲内、すなわち、−
1’C≦ΔT≦1℃であるかどうかを判断して(ステッ
プ([1) ) 、その範囲内であれば第1電子膨張弁
(3)の開度を現状に保持する。The control system of the above air conditioner will be explained below with reference to FIGS. 2 to 4. ◎ First temperature control means aω, room temperature signal from room temperature detector (9) and setting from room temperature setting device The first electronic expansion valve (
3), and the temperature difference (ΔT) obtained by subtracting the set temperature from the room temperature is within the range of ±1°C, that is, -
It is determined whether 1'C≦ΔT≦1°C (step ([1)), and if it is within that range, the opening degree of the first electronic expansion valve (3) is maintained at the current state.
一方、冷房時において温度差(ΔT)がへT>1℃すな
わち設定温度に比して高く、差が1℃を超えているとき
と、暖房時においてΔT<−1’C1すなわち、設定温
度に比して低く差が1℃を超えているときとでは、この
温度差の絶対値に応じて第1電子膨張弁(3)の開閉を
リニア能力制御方式によって行わせる(ステップ(ハ)
)。但し、蒸発器(4)出口が湿りになったときと蒸発
温度が低いときは能力制御は行わず保護制御を行わせる
。On the other hand, when the temperature difference (ΔT) during cooling is T>1°C, that is, higher than the set temperature, and the difference exceeds 1°C, and when during heating, ΔT<−1'C1, that is, higher than the set temperature. When the temperature difference exceeds 1°C, the first electronic expansion valve (3) is opened and closed according to the absolute value of this temperature difference using a linear capacity control method (step (c)).
). However, when the outlet of the evaporator (4) becomes wet or when the evaporation temperature is low, the capacity control is not performed and the protection control is performed.
具体的な制御例を挙げると、その吸込空気温度において
湿りにならない限度の開度に相当する最大値と能力制御
範囲から決定される開度に相当する最小値を基準として
、前記温度差(ΔT)に対し上昇直線特性の目標開度線
図を求めて、サンプリング時間(30秒)毎に上記目標
開度を演算し下記動作を行う。To give a specific control example, the temperature difference (ΔT ), the target opening degree diagram of the ascending linear characteristic is obtained, and the target opening degree is calculated at every sampling time (30 seconds), and the following operation is performed.
i)目標開度〈現在開度(閉じる方向)の場合、蒸発器
(4)入口温度T、(′−蒸発温度)と凍結開始温度の
差に比例したパルス数だけ第1電子膨張弁(3)を閉じ
させる。i) If the target opening is the current opening (closed direction), the first electronic expansion valve (3 ) close.
ii )目標開度〉現在開度(開く方向)の場合、蒸発
器(4)の出口過熱度と設定過熱度例えば5℃との差に
比例したパルス数だけ前記膨張弁(3)を開ける。ii) Target opening degree> In the case of the current opening degree (opening direction), the expansion valve (3) is opened by the number of pulses proportional to the difference between the exit superheat degree of the evaporator (4) and the set superheat degree, for example, 5°C.
なお、現在開度が目標開度に対し±10パルスの範囲内
になればその開度を保持する。Note that if the current opening is within the range of ±10 pulses with respect to the target opening, that opening is maintained.
iii )低温保護、
入口温度T、が設定温度を下まわれば、目標開度と現在
開度との大小関係にかかわらず、入口温度T、と設定温
度との差に比例したパルス数だけ膨張弁(3)を開いて
蒸発温度を上昇させる。iii) Low-temperature protection: If the inlet temperature T is below the set temperature, the expansion valve is activated by the number of pulses proportional to the difference between the inlet temperature T and the set temperature, regardless of the magnitude relationship between the target opening and the current opening. Open (3) to increase the evaporation temperature.
■)湿り保護、
前記過熱度が設定過熱度(5℃)を下まわれば、目標開
度と現在開度との大小関係にかかわりなく、過熱度と5
℃の差に比例したパルス数だけ膨張弁(3)を閉じ過熱
度を上昇させる。■) Moisture protection: If the superheat degree falls below the set superheat degree (5℃), regardless of the magnitude relationship between the target opening degree and the current opening degree, the superheat degree
The expansion valve (3) is closed by the number of pulses proportional to the difference in degrees Celsius to increase the degree of superheat.
◎ 再熱量制御手段αη、
前記温度差(ΔT)に対応する温度差信号と湿度検知器
α場からの室温度信号及び設定湿度信号とを入力信号と
して受けて第2電子膨張弁(6)に出力を与えるもので
あって、温度差(ΔT)が所定温度差以内、すなわち、
−1℃≦ΔT 51T:のときに、室湿度から設定湿度
を滅じた湿度差(ΔRH11)が所定湿度差の範囲内例
えば±10%の範囲内(−10≦ΔRHH≦10)であ
るかを判断して(ステップ(へ))、その範囲内であれ
ば第2電子膨張弁(6)の開度を現状に保持する(ステ
ップ(ト))。◎ A reheat amount control means αη receives a temperature difference signal corresponding to the temperature difference (ΔT), a room temperature signal from the humidity detector α field, and a set humidity signal as input signals, and sends them to the second electronic expansion valve (6). It provides an output, and the temperature difference (ΔT) is within a predetermined temperature difference, that is,
-1℃≦∆T 51T: Is the humidity difference (∆RH11) obtained by subtracting the set humidity from the room humidity within the predetermined humidity difference range, for example, within the range of ±10% (-10≦∆RHH≦10)? is determined (Step (G)), and if it is within that range, the opening degree of the second electronic expansion valve (6) is maintained at the current level (Step (G)).
一方、湿度差(ΔRH11)が前記範囲外にあって室湿
度の方が高い(ΔRH1+>10%)ときは、除湿が必
要な運転状態であるから、第2電子膨張弁(6)を湿度
差(ΔRHH)に比例したパルス数だけ開くことによっ
て再熱器(5)に流れる冷媒量を増やし再熱能力を増加
せしめる(ステップ(+7)’ ) 。On the other hand, when the humidity difference (ΔRH11) is outside the above range and the room humidity is higher (ΔRH1+>10%), the operation state requires dehumidification, so the second electronic expansion valve (6) is By opening the number of pulses proportional to (ΔRHH), the amount of refrigerant flowing to the reheater (5) is increased, and the reheating capacity is increased (step (+7)').
これとは逆に室湿度の方が低い(ΔRH11> 10%
)のときは、加湿が必要な運転状態であるから、第2電
子膨張弁(+9)を湿度差(ΔRHH)に比例したパル
ス数だけ閉じることによって再熱能力を減少せしめる(
ステップ(す))。On the contrary, room humidity is lower (ΔRH11>10%
), the operating state requires humidification, so the reheating capacity is reduced by closing the second electronic expansion valve (+9) by the number of pulses proportional to the humidity difference (ΔRHH).
Step (su)).
◎ 第2温度制御手段αe、
前記湿度差(ΔRHH)が所定湿度差以内、すなわち、
−10%≦ΔRHH≦10%であって、温度差(ΔT)
が所定温度差を超える場合に作動するものであって、温
度差(ΔT)に対応する温度差信号と湿度差(ΔRHH
)に対応する湿度差信号を受けて第2電子膨張弁(6)
に出力を与える。◎ Second temperature control means αe, the humidity difference (ΔRHH) is within a predetermined humidity difference, that is,
−10%≦ΔRHH≦10%, temperature difference (ΔT)
is activated when the temperature difference exceeds a predetermined temperature difference, and the temperature difference signal corresponding to the temperature difference (ΔT) and the humidity difference (ΔRHH
) in response to a humidity difference signal corresponding to the second electronic expansion valve (6).
gives the output.
すなわち、室温の方が冷房時は高くて1℃く6162℃
であり、また、暖房時は低くて一り℃≦へTく一1℃で
あると、湿度差(ΔRH)による第2電子膨張弁(6)
への開閉指令に優先させて温度差(ΔT)に比例したパ
ルス数だけ膨張弁(6)を閉じさせて室内側熱交換器(
4)の能力を増大させる(ステップ(ワ)′) 。In other words, room temperature is 1°C higher when air conditioned, 6162°C.
In addition, during heating, when the temperature is low and T<1°C, the second electronic expansion valve (6) due to the humidity difference (ΔRH)
The indoor heat exchanger (
4) Increase the ability (step (wa)').
逆に室温の方が冷房時は低くて一り℃≦ΔT〈−1’C
であり、また、暖房時は高くて1’c<6162℃であ
ると、膨張弁(6)を温度差(ΔT)に比例したパルス
数だけ開かせて、前記熱交換器(4)の能力を減少させ
る(ステップ(ワ))。On the other hand, room temperature is lower during cooling and is much lower ℃≦ΔT〈-1'C
In addition, during heating, if the temperature is 1'c<6162°C at the highest, the expansion valve (6) is opened by the number of pulses proportional to the temperature difference (ΔT) to increase the capacity of the heat exchanger (4). decrease (step (wa)).
◎ 再熱制限手段側、
請求項3の構成に係るものであって、前記温度差(ΔT
)に対応する温度差信号を受けて第2電子膨張弁(6)
に出力を与えるよう形成している。◎ Reheat limiting means side, according to the structure of claim 3, wherein the temperature difference (ΔT
) in response to a temperature difference signal corresponding to the second electronic expansion valve (6).
It is configured to give an output to.
温度差(ΔT)が所定温度差(−1℃≦ΔT≦1℃)を
超えて高設定温度差以上になり、例えば冷房時でΔT>
2℃、暖房時でΔTく一2°Cとなるとすれば、強制的
に第2電子膨張弁(6)を全閉させ(ステップ(り))
、室内側熱交換器(4)を最大能力で運転するようにす
るものである。The temperature difference (ΔT) exceeds the predetermined temperature difference (-1°C≦ΔT≦1°C) and becomes equal to or higher than the high set temperature difference, for example, when ΔT>
If the temperature is 2°C and ΔT is 2°C during heating, the second electronic expansion valve (6) is forcibly closed (step (ri)).
, the indoor heat exchanger (4) is operated at maximum capacity.
■ 冷暖房制御手段a匂、
請求項2の構成に係るものであって、温度差(ΔT)に
対応する温度差信号を受けて四路切換弁(7)に切換指
令を与えるよう形成している。■ Heating and cooling control means (a), which is according to the structure of claim 2, and is configured to give a switching command to the four-way switching valve (7) in response to a temperature difference signal corresponding to the temperature difference (ΔT). .
すなわち、前記温度差(ΔT)が前記設定温度差以上に
なって室温度の方が高い(ΔT>2℃)ときは、四路切
換弁(7)を冷房側に、室温度の方が低い(ΔT<−2
℃)ときは逆に暖房側に切り換えるようにするものであ
る(ステップ(ネ))。That is, when the temperature difference (ΔT) exceeds the set temperature difference and the room temperature is higher (ΔT>2°C), the four-way switching valve (7) is set to the cooling side and the room temperature is lower. (ΔT<-2
℃), the device switches to the heating side (step (ne)).
この制御手段α佛を設けたことによって、急激な負荷変
動があったりした場合に冷房と暖房との間の自動切換え
が成される。By providing this control means α, automatic switching between cooling and heating can be achieved in the event of sudden load changes.
■ 加湿制御手段(21゜
請求項4に係る構成であって、湿度検知器Qωの湿度信
号と設定湿度信号とを受けて加湿器aυに発停出力を与
えるよう形成している。(2) Humidification control means (21°) This is a configuration according to claim 4, and is configured to receive the humidity signal from the humidity detector Qω and the set humidity signal and give an on/off output to the humidifier aυ.
第2電子膨張弁(6)が再熱量制御手段aηによって全
閉に制御されている(ステップ(り))ことを条件とし
て室温度が設定湿度よりも低い(ΔR11<−10%)
場合に加湿器αDに対して加湿運転指令を発信するよう
になっている。The room temperature is lower than the set humidity (ΔR11<-10%) on the condition that the second electronic expansion valve (6) is fully closed (step (ri)) by the reheat amount control means aη.
In this case, a humidification operation command is sent to the humidifier αD.
この制御手段12鴎を設けたことによって、乾燥気味の
状態においても、給温を行って恒温状態を維持し得る。By providing this control means 12, it is possible to maintain a constant temperature state by supplying heat even in a slightly dry state.
◎ 調湿制御手段(21)、
請求項5に係る構成であって、湿度検知器α0の湿度信
号と設定湿度信号とを受けて圧縮機(1)駆動モータの
電源装置であるインバータ(ロ)に対して周波数変換出
力を与えるよう形成している。◎ Humidity control means (21), which has the configuration according to claim 5, and receives the humidity signal from the humidity detector α0 and the set humidity signal and connects the inverter (b) which is a power supply device for the drive motor of the compressor (1). It is formed so as to give a frequency conversion output to.
インバータ顛駆動方式の圧縮機(1)の場合は、周知の
ことであるが、その能力制御は30〜120 Hzの範
囲内において、前記温度差(ΔT)を基準としてこの温
度差(ΔT)が基準値よりも大きいときは、サンプリン
グ毎に2〜3 Hzの周波数増加出力を発し、基準値に
合致したときは現周波数の状態を保持する出力を発し、
基準値よりも小さいときは反対に2〜3 Hzの周波数
減少出力を発し温度に対する能力制御を行っている(ス
テップ(イ)。As is well known in the case of an inverter-driven compressor (1), its capacity control is based on the temperature difference (ΔT) within the range of 30 to 120 Hz. When the frequency is greater than the reference value, a frequency increase output of 2 to 3 Hz is generated for each sampling, and when the reference value is met, an output that maintains the current frequency state is generated.
When it is smaller than the reference value, on the other hand, a frequency reduction output of 2 to 3 Hz is generated to control the temperature (step (a)).
本発明はかかる能力制御に加えて、湿度変化に応動し圧
縮機(1)能力を増減しようとするものであって、前記
湿度差(ΔRHH)が所定湿度差以内、すなわち、−1
0%≦ΔRHH≦10%であるかどうかによって夫々に
適応した能力制御を行わせ、所定湿度再内の場合には、
サンプリング前の湿度差(ΔRHH1)と現サンプリン
グ時の温度差(ΔRH)I! )との差をとり、その差
が成る値例えば設定湿度に対して5%以上になると周波
数を1ステツプ変更せしめるが、具体例を示すと下記の
通りであり、ステップ(ソ)に示される。In addition to such capacity control, the present invention attempts to increase or decrease the capacity of the compressor (1) in response to changes in humidity, and the humidity difference (ΔRHH) is within a predetermined humidity difference, that is, -1
Depending on whether 0%≦∆RHH≦10%, adaptive capacity control is performed, and if the humidity is within the predetermined humidity,
Humidity difference before sampling (ΔRHH1) and temperature difference at current sampling (ΔRH) I! ), and if the difference becomes 5% or more relative to the set humidity, the frequency is changed by one step.A specific example is as follows, and is shown in step (S).
i)ΔRH,,ΔRHt<Oの場合(室温度の方が低い
場合)、
向)では出力周波数を1ステ、プ下げ、傾向)では1ス
テップ上げる。i) If ΔRH,, ΔRHt<O (when the room temperature is lower), lower the output frequency by 1 step in direction), increase it by 1 step in direction).
ii )ΔRHH+、ΔRHI1.>0の場合(室温度
の方が高い場合)、
数を1ステップ上げ、
ツブ下げる。ii) ΔRHH+, ΔRHI1. If >0 (room temperature is higher), increase the number by one step and decrease it by one step.
in)ΔRH111>0.ΔRH1h<O又はΔRHH
+<0゜ΔRH1(!>Oの場合、
室温度が設定湿度に対し高い方から低い方に、又その逆
に変動する場合であるから、現在の周波数を保持させる
。in)ΔRH111>0. ΔRH1h<O or ΔRHH
If +<0°ΔRH1(!>O), the current frequency is held because the room temperature fluctuates from higher to lower than the set humidity or vice versa.
一方、湿度差(ΔRHH)が所定湿度差を超えている場
合にはステップ(ツ)に移行せしめて、湿度差(ΔRH
)が基準値よりも大きいときはサンプリング毎に1ステ
ツプの周波数増加出力を発し、合致するときは現周波数
を保持する出力を発し、小さいときは反対に周波数減少
出力を発せしめて能力制御を行わせる。On the other hand, if the humidity difference (ΔRHH) exceeds the predetermined humidity difference, the process proceeds to step (T), and the humidity difference (ΔRHH)
) is larger than the reference value, output increases the frequency by 1 step per sampling, when they match, output maintains the current frequency, and when it is smaller, output decreases the frequency to control the capacity. .
以上各手段毎に分脱したが、それ等の制御の態様につい
ては、第3図に冷房運転状態及び暖房運転状態が併記し
て示され、さらに第4図には調湿制御手段(21)によ
って圧縮機(1)の能力が湿度変化に応じ制御される場
合の冷房運転状態が示される。Although the above has been explained separately for each means, the mode of control thereof is shown in FIG. 3 along with the cooling operation state and heating operation state, and furthermore, in FIG. 4, the humidity control means (21) shows the cooling operation state when the capacity of the compressor (1) is controlled according to changes in humidity.
それ等各運転はフローから明らかなように、第5図の空
気線図上で斜線領域に室内の温湿度が保持されるよう制
御する場合には、温湿度が高いときは冷房(冷却)、温
湿度が低いときは暖房(加熱)を優先し、すなわち、第
1電子膨張弁(3)の開度を大きく第2電子膨張弁(6
)の開度を全閉もしくは最小にさせて、温度が設定領域
内に到達した時点で第2電子膨張弁(6)の開度制御に
よる湿度コントロールを行わせ、冷(暖)房優先方式を
採用し第3図及び第4図に示す運転制御を成している。As is clear from the flow of each of these operations, when controlling the indoor temperature and humidity to be maintained in the shaded area on the air diagram in Figure 5, when the temperature and humidity are high, air conditioning (cooling), When the temperature and humidity are low, priority is given to heating, that is, the opening degree of the first electronic expansion valve (3) is increased and the opening degree of the second electronic expansion valve (6) is increased.
) is fully closed or minimized, and when the temperature reaches the set range, humidity control is performed by controlling the opening of the second electronic expansion valve (6), and the cooling (heating) priority system is activated. The operation control shown in FIGS. 3 and 4 is implemented.
かくして再熱機能を併有させて室温及び室温度を一定に
保持する安定運転が可能である。In this way, it is possible to perform stable operation in which the room temperature and room temperature are kept constant by having a reheating function.
(発明の効果)
第1電子膨張弁(3)を第1温度制御手段α鴫によって
弁開度制御することにより室内側熱交換器(4)の熱交
換能力を空調負荷に対応し無段階的に調節でき、また、
再熱量制御手段anにより第2電子膨張弁(6)を弁開
度制御して再熱器(5)の能力を室湿度に応じ増減調節
できるので、室内の温度、湿度を変動幅が少ない状態に
維持し得て、温湿度制御精度を飛躍的に向上させること
ができる。(Effect of the invention) By controlling the valve opening degree of the first electronic expansion valve (3) by the first temperature control means α, the heat exchange capacity of the indoor heat exchanger (4) can be adjusted steplessly in response to the air conditioning load. It can be adjusted to
The capacity of the reheater (5) can be adjusted to increase or decrease according to the room humidity by controlling the opening degree of the second electronic expansion valve (6) by the reheat amount control means an, so that the room temperature and humidity can be kept in a state where the range of fluctuation is small. temperature and humidity control accuracy can be dramatically improved.
さらに室湿度が保持されているときに温度変動があった
場合には再熱器(5)の能力を第2温度制御手段αeに
よって増減制御するようにしているので、湿度の変動を
抑えて温度制御を確実に行い得る。Furthermore, if there is a temperature fluctuation while the room humidity is maintained, the capacity of the reheater (5) is controlled to increase or decrease by the second temperature control means αe, so that the temperature can be increased while suppressing the humidity fluctuation. Control can be performed reliably.
かくして室温及び室湿度を全年間を通じて一定に保持す
ることができる。In this way, room temperature and room humidity can be kept constant throughout the year.
また、請求項2においては、冷凍サイクルに可逆方式採
用して冷暖切換え可能となすと共に、冷房運転時に大巾
な室温低下があり、あるいは暖房運転時に大巾な室温上
昇があったときには、冷暖房制御手段α唾によって自動
的に暖房あるいは冷房に切り換え得る構成としたことに
より、温度制御中を一層拡大でき、温度変動が激しい環
境にも十分対応し得る。In addition, in claim 2, a reversible system is adopted in the refrigeration cycle to enable switching between cooling and heating, and when there is a large drop in room temperature during cooling operation or a large rise in room temperature during heating operation, heating and cooling control is performed. By configuring the system to be able to automatically switch to heating or cooling using the means α, the temperature control period can be further expanded and the system can be fully adapted to environments with severe temperature fluctuations.
さらに請求項3においては、室温が設定温度に対し著し
い温度差を有するような場合は、再熱器(5)の機能を
再熱制限手段α瞬で抑制させるようにしているので、室
内側熱交換器(4)を負荷に対し最大能力で運転させて
温度の安定保持が確実に成される。Furthermore, in claim 3, when the room temperature has a significant temperature difference with respect to the set temperature, the function of the reheater (5) is suppressed by the reheat limiting means α instantaneous, so that the indoor heat The exchanger (4) is operated at maximum capacity for the load to ensure stable temperature maintenance.
また、請求項4においては、加湿器aDを付設して、加
湿制御手段C21によって室湿度が一定保持できない低
湿度時に加湿器a0を作動させるようにしているので、
乾き過ぎの好ましくない環境を生ぜしめることがなく高
信転性が維持される。Further, in claim 4, a humidifier aD is attached, and the humidifier a0 is operated by the humidification control means C21 when the room humidity cannot be maintained at a constant level at low humidity.
High reliability is maintained without creating an unfavorable environment that is too dry.
さらにまた、請求項5においては、室湿度の変動に対し
て熱交換器側での能力制御だけでなく、圧縮機の能力制
御を調湿制御手段(21)で行わせることにより、より
きめ細かい湿度制御が可能である。Furthermore, in claim 5, the humidity control means (21) performs not only the capacity control on the heat exchanger side but also the capacity control of the compressor in response to fluctuations in room humidity. Control is possible.
第1図は本発明の実施例に係る装置回路図、第2図は同
じ(制御系のブロック示回路図、第3図及び第4図は本
発明装置例の運転制御を示す各フロー線図、第5図は温
湿制御の態様を説明するための空気線図である。
(1)・・・圧縮機、
(2)・・・室外側′熱交換器(凝縮器)、(3)・・
・第1電子膨張弁、
(4)・・・室内側熱交換器(蒸発器)、(5)・・・
再熱器、 (6)・・・第2電子膨張弁、(7)・・・
四路切換弁、 (9)・・・室温検知器、(II・・・
湿度検知器、 Ql)・・・加湿器、(2)・・・イン
バータ、
QSI・・・第1温度制御手段、
(II・・・第2温度制御手段、
αη・・・再熱量制御手段、
Ql・・・再熱制限手段、
Ql・・・冷暖房制御手段、
am・・・加湿制御手段、
(21)・・・調湿制御手段。
第 2図
1113 間
第4図
慎 ら 間
10℃ 1719 Z:j−憑庚(0C)Fig. 1 is a circuit diagram of a device according to an embodiment of the present invention, Fig. 2 is the same (block diagram of the control system), and Figs. 3 and 4 are flow diagrams showing operation control of an example of the device of the present invention. , Fig. 5 is an air diagram for explaining the mode of temperature and humidity control. (1)...Compressor, (2)...Outdoor heat exchanger (condenser), (3)...・・・
・First electronic expansion valve, (4)... Indoor heat exchanger (evaporator), (5)...
Reheater, (6)...Second electronic expansion valve, (7)...
Four-way switching valve, (9)...Room temperature detector, (II...
Humidity detector, Ql)... Humidifier, (2)... Inverter, QSI... First temperature control means, (II... Second temperature control means, αη... Reheat amount control means, Ql... Reheat limiting means, Ql... Cooling/heating control means, am... Humidification control means, (21)... Humidity control means. Z:j-possessed (0C)
Claims (5)
電子膨張弁(3)、室内側に設けた蒸発器(4)により
冷凍サイクルを形成し、前記蒸発器(4)に対し空気流
通方向の下手側に再熱器(5)を配置して該再熱器(5
)と第2電子膨張弁(6)とを直列に接続した冷媒回路
を、凝縮器(2)と第1電子膨張弁(3)との直列接続
になる冷媒回路に並列接続せしめる一方、前記蒸発器(
4)の吸込空気温度を検知する室温検知器(9)と、蒸
発器(4)の吸込空気湿度を検知する湿度検知器(10
)と、室温検知器(9)による室温が設定温度に比し高
く、かつ、所定温度差を超える値であると、第1電子膨
張弁(3)をそのときの温度差(ΔT)に比例した開度
に制御する第1温度制御手段a,と、前記温度差(ΔT
)が所定温度差以内のときに、湿度検知器(10)によ
る室湿度が設定湿度に対して所定湿度差を超える値であ
ると、室湿度の方が高いときは第2電子膨張弁(6)を
そのときの湿度差(ΔRH)に比例した開度に開かせ、
逆に低いときは第2電子膨張弁(6)をそのときの湿度
差(ΔRH)に比例した開度に閉じさせる再熱量制御手
段(17)と、前記湿度差(ΔRH)が所定湿度差以内
のときに、前記温度差(ΔT)が所定湿度差を超える値
であると、室温が設定温度よりも高い場合は該温度差(
ΔT)に比例した開度に第2電子膨張弁(6)を閉じさ
せ、逆に低い場合は該温度差(ΔT)に比例した開度に
第2電子膨張弁(6)を開かせる第2温度制御手段(1
6)とを設けたことを特徴とする空気調和装置。1. Compressor (1), condenser (2) installed on the outdoor side, first
An electronic expansion valve (3) and an evaporator (4) provided on the indoor side form a refrigeration cycle, and a reheater (5) is arranged on the downstream side of the evaporator (4) in the air flow direction. Reheater (5
) and the second electronic expansion valve (6) are connected in parallel to the refrigerant circuit connected in series with the condenser (2) and the first electronic expansion valve (3). vessel(
4), a room temperature detector (9) that detects the suction air temperature, and a humidity detector (10) that detects the suction air humidity of the evaporator (4).
), and if the room temperature detected by the room temperature detector (9) is higher than the set temperature and exceeds a predetermined temperature difference, the first electronic expansion valve (3) is activated in proportion to the temperature difference (ΔT) at that time. the first temperature control means a, which controls the opening degree to the temperature difference (ΔT
) is within a predetermined temperature difference, if the room humidity measured by the humidity detector (10) exceeds the predetermined humidity difference with respect to the set humidity, if the room humidity is higher, the second electronic expansion valve (6 ) to an opening proportional to the humidity difference (ΔRH) at that time,
Conversely, when the humidity is low, the second electronic expansion valve (6) is closed to an opening proportional to the humidity difference (ΔRH) at that time; When the temperature difference (ΔT) exceeds the predetermined humidity difference, if the room temperature is higher than the set temperature, the temperature difference (ΔT) exceeds the predetermined humidity difference.
The second electronic expansion valve (6) is closed to an opening proportional to the temperature difference (ΔT), and conversely, when the temperature difference is low, the second electronic expansion valve (6) is opened to an opening proportional to the temperature difference (ΔT). Temperature control means (1
6) An air conditioner characterized by comprising:
冷房時凝縮器となる室外側熱交換器(2)、第1電子膨
張弁(3)、室内側に設けた冷房時蒸発器となる室内側
熱交換器(4)により可逆冷凍サイクルを形成し、前記
室内側熱交換器(4)に対し空気流通方向の下手側に再
熱器(5)を配置して、該再熱器(5)と第2電子膨張
弁(6)とを直列に接続した冷媒回路を、室外側熱交換
器(2)と第1電子膨張弁(3)との直列接続になる冷
媒回路に並列接続せしめる一方、室内側熱交換器(4)
の吸込空気温度を検知する室温検知器(9)と、同じく
吸込空気湿度を検知する湿度検知器(10)と、室温検
知器(9)による室温が設定温度に比し冷房時は高く、
暖房時は低くて、かつ、所定温度差を超える値であると
、第1電子膨張弁(3)をそのときの温度差(ΔT)に
比例した開度に制御する第1温度制御手段(15)と、
前記温度差(ΔT)が所定温度差以内のときに、湿度検
知器(10)による室湿度が設定湿度に対して所定湿度
差を超える値であると、室湿度の方が高いときは第2電
子膨張弁(6)をそのときの湿度差(ΔRH)に比例し
た開度に開かせ、逆に低いときは第2電子膨張弁(6)
をそのときの湿度差(ΔRH)に比例した開度に閉じさ
せる再熱量制御手段(17)と、前記湿度差(ΔRH)
が所定湿度差以内のときに、前記温度差(ΔT)が所定
温度差を超える値であると、室温が設定温度よりも高い
場合は該温度差(ΔT)に比例した開度に第2電子膨張
弁(6)を冷房時は閉じ、暖房時は開かせ、逆に低い場
合は該温度差(ΔT)に比例した開度に第2電子膨張弁
(6)を冷房時は開き、暖房時は閉じさせる第2温度制
御手段(16)と、前記温度差(ΔT)が前記所定温度
差よりも大きい値の高設定温度差を超える場合に、四路
切換弁(7)を室温度の方が高いときは冷房側に、逆に
低いときは暖房側に切り換える冷暖房制御手(19)を
設けてなることを特徴とする空気調和装置。2. Compressor (1), four-way switching valve (7), outdoor heat exchanger (2) that serves as a condenser for cooling provided on the outdoor side, first electronic expansion valve (3), provided on the indoor side for cooling A reversible refrigeration cycle is formed by an indoor heat exchanger (4) serving as an evaporator, and a reheater (5) is disposed on the downstream side in the air flow direction with respect to the indoor heat exchanger (4). A refrigerant circuit in which a reheater (5) and a second electronic expansion valve (6) are connected in series is a refrigerant circuit in which an outdoor heat exchanger (2) and a first electronic expansion valve (3) are connected in series. while the indoor heat exchanger (4)
The room temperature detected by the room temperature detector (9) which detects the temperature of the intake air, the humidity detector (10) which also detects the humidity of the intake air, and the room temperature detector (9) is higher than the set temperature during cooling.
During heating, if the temperature is low and exceeds a predetermined temperature difference, the first temperature control means (15) controls the first electronic expansion valve (3) to an opening proportional to the temperature difference (ΔT) at that time. )and,
When the temperature difference (ΔT) is within a predetermined temperature difference, if the room humidity measured by the humidity detector (10) exceeds the predetermined humidity difference with respect to the set humidity, if the room humidity is higher, the second The electronic expansion valve (6) is opened to an opening proportional to the humidity difference (ΔRH) at that time, and when the humidity is low, the second electronic expansion valve (6) is opened.
reheating amount control means (17) for closing the opening to an opening proportional to the humidity difference (ΔRH) at that time, and the humidity difference (ΔRH)
is within a predetermined humidity difference, and if the temperature difference (ΔT) exceeds the predetermined temperature difference, if the room temperature is higher than the set temperature, a second electron is applied to the opening proportional to the temperature difference (ΔT). The expansion valve (6) is closed during cooling and opened during heating; conversely, when the temperature is low, the second electronic expansion valve (6) is opened to an opening proportional to the temperature difference (ΔT) during cooling, and opened during heating. a second temperature control means (16) that closes the four-way switching valve (7) when the temperature difference (ΔT) exceeds a high set temperature difference that is larger than the predetermined temperature difference; This air conditioner is characterized by being provided with an air conditioning control hand (19) that switches to the cooling side when the temperature is high and to the heating side when the temperature is low.
温度差よりも大きい値の高設定温度差を超える場合に第
2電子膨張弁(6)を閉じさせる再熱制限手段(18)
を付設してなる請求項1又は2記載の空気調和装置。3. reheat limiting means (18) for closing the second electronic expansion valve (6) when the temperature difference (ΔT) between the room temperature and the set temperature exceeds a high set temperature difference that is larger than the predetermined temperature difference;
The air conditioner according to claim 1 or 2, further comprising: an air conditioner.
の下手側に配設する一方、前記再熱量制御手段(17)
により第2電子膨張弁(6)が全閉制御されていて、か
つ、室湿度が前記設定湿度よりも低い場合に前記加湿器
(11)を加湿運転させる加湿制御手段(20)を付設
してなる請求項1乃至3の何れかに記載の空気調和装置
。4. The humidifier (11) is disposed on the downstream side of the reheater (5) in the air flow direction, while the reheat amount control means (17)
a humidification control means (20) for operating the humidifier (11) when the second electronic expansion valve (6) is fully closed and the room humidity is lower than the set humidity; The air conditioner according to any one of claims 1 to 3.
るインバータ駆動方式の容量可変圧縮機であり、一方、
前記湿度差(ΔRH)が所定湿度差以内であって、室湿
度の方が低く、かつ湿度増加傾向のときはインバータ(
12)の出力周波数を下げ、逆に湿度減少傾向のときは
出力周波数を上げ、また、室湿度の方が高く、かつ湿度
増加傾向のときは出力周波数を上げ、逆に湿度減少傾向
のときは出力周波数を下げ、さらに、湿度差(ΔRH)
が所定湿度差を超えているときはこの湿度差(ΔRH)
に対応して室湿度の方が高いときはインバータ(12)
の出力周波数を上げ、逆に低いときは出力周波数を下げ
る調湿制御手段(21)を付設してなる請求項1乃至4
の何れかに記載の空気調和装置。5. The compressor (1) is an inverter-driven variable capacity compressor whose frequency is controlled according to the air conditioning load;
When the humidity difference (ΔRH) is within a predetermined humidity difference, the room humidity is lower, and the humidity is increasing, the inverter (
12) Decrease the output frequency, and conversely increase the output frequency when the humidity is decreasing, and increase the output frequency when the room humidity is higher and the humidity is increasing, and conversely when the humidity is decreasing. Lower the output frequency and further reduce the humidity difference (ΔRH)
exceeds the specified humidity difference, this humidity difference (ΔRH)
When the room humidity is higher, the inverter (12)
Claims 1 to 4 further comprising a humidity control means (21) for increasing the output frequency of the humidity control device and lowering the output frequency when the output frequency is low.
The air conditioner according to any of the above.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63047853A JPH0668410B2 (en) | 1988-02-29 | 1988-02-29 | Air conditioner |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63047853A JPH0668410B2 (en) | 1988-02-29 | 1988-02-29 | Air conditioner |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH01222137A true JPH01222137A (en) | 1989-09-05 |
JPH0668410B2 JPH0668410B2 (en) | 1994-08-31 |
Family
ID=12786928
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63047853A Expired - Lifetime JPH0668410B2 (en) | 1988-02-29 | 1988-02-29 | Air conditioner |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0668410B2 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0682122A (en) * | 1992-09-07 | 1994-03-22 | Daikin Ind Ltd | Refrigerating apparatus |
JP2011133136A (en) * | 2009-12-22 | 2011-07-07 | Daikin Industries Ltd | Air conditioning device, and method of determining failure of humidity sensor in the same |
JP2012017889A (en) * | 2010-07-07 | 2012-01-26 | Daikin Industries Ltd | Air conditioner |
JP2012172929A (en) * | 2011-02-22 | 2012-09-10 | Ryosuke Okada | Data center and operation method thereof |
WO2018221652A1 (en) | 2017-05-31 | 2018-12-06 | ダイキン工業株式会社 | Air conditioning apparatus |
CN110691950B (en) * | 2017-05-31 | 2021-08-27 | 大金工业株式会社 | Air conditioner |
CN114251802A (en) * | 2020-09-21 | 2022-03-29 | 广东美的制冷设备有限公司 | Dehumidification control method, air conditioner and readable storage medium |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101290780B1 (en) * | 2012-02-23 | 2013-07-29 | 서울대학교산학협력단 | Heating and cooling system |
-
1988
- 1988-02-29 JP JP63047853A patent/JPH0668410B2/en not_active Expired - Lifetime
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0682122A (en) * | 1992-09-07 | 1994-03-22 | Daikin Ind Ltd | Refrigerating apparatus |
JP2011133136A (en) * | 2009-12-22 | 2011-07-07 | Daikin Industries Ltd | Air conditioning device, and method of determining failure of humidity sensor in the same |
JP2012017889A (en) * | 2010-07-07 | 2012-01-26 | Daikin Industries Ltd | Air conditioner |
JP2012172929A (en) * | 2011-02-22 | 2012-09-10 | Ryosuke Okada | Data center and operation method thereof |
WO2018221652A1 (en) | 2017-05-31 | 2018-12-06 | ダイキン工業株式会社 | Air conditioning apparatus |
CN110691950B (en) * | 2017-05-31 | 2021-08-27 | 大金工业株式会社 | Air conditioner |
CN114251802A (en) * | 2020-09-21 | 2022-03-29 | 广东美的制冷设备有限公司 | Dehumidification control method, air conditioner and readable storage medium |
CN114251802B (en) * | 2020-09-21 | 2023-09-26 | 广东美的制冷设备有限公司 | Dehumidification control method, air conditioner and readable storage medium |
Also Published As
Publication number | Publication date |
---|---|
JPH0668410B2 (en) | 1994-08-31 |
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