JPH046374A - Mixed cooling and heating type refrigerating cycle device - Google Patents
Mixed cooling and heating type refrigerating cycle deviceInfo
- Publication number
- JPH046374A JPH046374A JP10791590A JP10791590A JPH046374A JP H046374 A JPH046374 A JP H046374A JP 10791590 A JP10791590 A JP 10791590A JP 10791590 A JP10791590 A JP 10791590A JP H046374 A JPH046374 A JP H046374A
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- heat exchanger
- pressure gas
- outdoor
- compressor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000001816 cooling Methods 0.000 title claims abstract description 14
- 238000010438 heat treatment Methods 0.000 title claims abstract description 14
- 238000001704 evaporation Methods 0.000 claims abstract description 31
- 239000003507 refrigerant Substances 0.000 claims abstract description 22
- 230000008020 evaporation Effects 0.000 claims description 25
- 230000005494 condensation Effects 0.000 claims description 21
- 238000009833 condensation Methods 0.000 claims description 21
- 239000007788 liquid Substances 0.000 claims description 14
- 238000005057 refrigeration Methods 0.000 claims description 9
- 230000005540 biological transmission Effects 0.000 abstract description 4
- 238000000034 method Methods 0.000 abstract 1
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 238000004378 air conditioning Methods 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000001052 transient effect Effects 0.000 description 3
- 238000009825 accumulation Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
Landscapes
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は冷暖混在形冷凍サイクル装置に関するもので
あり、特に圧縮機能力と室外熱交換器の送風機の速度の
制御に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a mixed cooling/heating refrigeration cycle apparatus, and particularly to control of the compression function and the speed of the blower of an outdoor heat exchanger.
第３図は例えば特開平１−２４７９６７号公報に示され
た従来の多室型冷暖房装置を示す構成図であり、図にお
いて、（１）は室外ユニ９ ＋−、ｆ３］は圧縮機、（
４ａ） （４ｂ）は室外機熱交換器、（２ａｌ 〜（
２ｃ）は室内ユニット、（１８４）〜（１８ｃ）は室内
熱交換器、（２１）は冷媒吐出管、（２２）は冷媒吸入
管、（１６ａ） （１６ｂ） （１７ｉ） （１７ｂ）
は切換弁、（１１）は高圧ガス管、（１３）は低圧ガス
管、（１４）は液管、（１６ａ）〜（１６ｃ） （１７
ａ）〜（１７ｃ）は切換弁、（１５ａ） 〜（１５ｅ）
、（２３ａ） （２３ｂｌは冷媒減圧器である。FIG. 3 is a configuration diagram showing a conventional multi-room air conditioning system disclosed in, for example, Japanese Patent Application Laid-Open No. 1-247967. In the figure, (1) is an outdoor unit 9 +-, f3] is a compressor,
4a) (4b) is an outdoor unit heat exchanger, (2al ~ (
2c) is an indoor unit, (184) to (18c) are indoor heat exchangers, (21) is a refrigerant discharge pipe, (22) is a refrigerant suction pipe, (16a) (16b) (17i) (17b)
is a switching valve, (11) is a high pressure gas pipe, (13) is a low pressure gas pipe, (14) is a liquid pipe, (16a) to (16c) (17
a) to (17c) are switching valves, (15a) to (15e)
, (23a) (23bl is a refrigerant pressure reducer.
次に動作について説明する。室内ユニッＩ−（２ａ）と
（２ｂ）が暖房運転のモードで室内ユニット（２Ｃ）が
冷房運転のモードになった壜台を想定する。圧縮機（３
２）の能力は負荷の多い暖房モードの室内ユニッ１−（
２ａ）と（２ｂ）に合わせて決定し、室外ユニット（１
）の熱交換器（４ａ） （４ｂ）の容量は室内ユニット
（２＆）（２ｂ）の暖房負荷合計値から室内ユニット（
２ｃ）の冷房負荷合計値を差し引いた量を室外熱交換器
（４ａ）のみがまかなうことになりしかも蒸発器として
機能させることになる。以上のことより、高圧ガス管（
１１）につながる切換弁（１６ａ） 、 （１６ｂ）
を開とし、低圧ガス管（１３）とつながる切換弁（１７
ａ） 、 （１７ｂ）は閉とする。液管（１４）とつな
がる冷媒減圧器（１５ａ）（１５ｂ）は全開としＰｒｌ
管（１４）からの冷媒が、膨張弁として機能する冷媒減
圧器（１５ｃ） 、 （２３ａ）を通り、蒸発器として
機能する熱交換器（１８ｃｌと（４ａ）で蒸発ガス化す
る。その冷媒は切換弁（１７ｃ） （２５ａｌを開とす
ることによって低圧ガス管（１３）を通って吸込管（２
２）に流入する。ここで切換弁（２４ａ） （２４ｂ）
（２５ｂ）は閉となっている。Next, the operation will be explained. Assume a bottle stand in which indoor units I-(2a) and (2b) are in heating operation mode and indoor unit (2C) is in cooling operation mode. Compressor (3
The capacity of 2) is the indoor unit 1-(
2a) and (2b), and install the outdoor unit (1
) The capacity of the heat exchanger (4a) (4b) of the indoor unit (2&) (2b) is calculated from the total heating load of the indoor unit (2&) (2b)
Only the outdoor heat exchanger (4a) will cover the amount after subtracting the total cooling load in 2c), and will also function as an evaporator. From the above, high pressure gas pipe (
Switching valves (16a) and (16b) connected to 11)
the switching valve (17) connected to the low pressure gas pipe (13).
a) and (17b) are closed. The refrigerant pressure reducers (15a) (15b) connected to the liquid pipe (14) are fully open and Prl
The refrigerant from the pipe (14) passes through the refrigerant pressure reducers (15c) and (23a), which function as expansion valves, and is evaporated and gasified in the heat exchanger (18cl) and (4a), which function as evaporators.The refrigerant is By opening the switching valve (17c) (25al), the suction pipe (2) passes through the low pressure gas pipe (13).
2). Here, the switching valve (24a) (24b)
(25b) is closed.
従来の多室型冷暖房装置は、以上のように構成されてい
るので、圧縮機の能力と室外熱交換器の容量を決定する
ために、室内ユニットの情報を必要とし、室内−室外間
の情報伝送のために制御系が複雑になりイ＝頼性が低下
するという問題点があった。Conventional multi-room air conditioning systems are configured as described above, so in order to determine the capacity of the compressor and the capacity of the outdoor heat exchanger, information on the indoor unit is required, and information between indoor and outdoor units is required. There was a problem in that the control system became complicated due to the transmission, reducing reliability.
この発明は上記のような問題点を解消するためなされた
もので、室内−室外機間の情報伝送が不必要で常に暖房
用高圧圧力と冷房用低圧圧力が一定になるように制御で
きろ冷暖混在形マルチ冷凍サイクルを得ることを目的と
する。This invention was made to solve the above-mentioned problems, and it is possible to control the high pressure for heating and the low pressure for cooling to always be constant without the need for information transmission between the indoor and outdoor units. The purpose is to obtain a mixed type multi-refrigeration cycle.
この発明に係る冷暖混在形マルチ冷凍サイクルは、冷媒
蒸発温度ＥＴと凝縮温度ＣＴを検出する温度セッサを設
け、その２つの検出温度とあらかじめ設定された設定蒸
発温度ＥＴｏおよび設定凝縮温度ＣＴｏとの２つの偏差
ΔＥＴ、ΔＣＴに応じて、圧縮機能力と室外熱交換器の
運転モード及び送風機の回転数を制御するようにしたも
のである。The cooling/heating mixed type multi-refrigeration cycle according to the present invention is provided with a temperature sensor that detects a refrigerant evaporation temperature ET and a condensation temperature CT, and a temperature sensor that detects a refrigerant evaporation temperature ET and a condensation temperature CT. The compression function, the operation mode of the outdoor heat exchanger, and the rotation speed of the blower are controlled according to the two deviations ΔET and ΔCT.
また、冷媒蒸発温度ＥＴ、凝縮温度ＣＴからその予測値
を求め、これに基づいて室外機を制御するようにしたも
のである。Further, a predicted value is obtained from the refrigerant evaporation temperature ET and condensation temperature CT, and the outdoor unit is controlled based on this.
この発明においては、蒸発温度偏差ΔＥＴと凝縮温度偏
差△ＣＴとから、圧縮機能力変更量ΔＱｃｏａｐと室外
熱交換器能力変更量ΔＡＫｅを次式から求め、
−（Ａ、Ｂ、Ｃ，Ｄは定数）
これにより圧縮機、室外熱交換器能力が制御される。In this invention, the compression function power change amount ΔQcoap and the outdoor heat exchanger capacity change amount ΔAKe are calculated from the following equations from the evaporation temperature deviation ΔET and the condensation temperature deviation ΔCT, where −(A, B, C, and D are constants) ) This controls the compressor and outdoor heat exchanger capacity.
また過去の蒸発温度ＥＴと凝縮温度ＣＴからそれらの予
測値が求められ、それら予測値と各設定値との偏差から
△Ｑｃｏｍｐ、ΔＡＫｅが求められ、これに基づいて圧
縮機、室外熱交換器が制御される。In addition, predicted values are obtained from the past evaporation temperature ET and condensation temperature CT, and △Qcomp and ΔAKe are obtained from the deviations between these predicted values and each setting value, and based on this, the compressor and outdoor heat exchanger are controlled.
以下、乙の発明の一実施例を図について説明する。第１
図において（１）は室外ユニット、（２）は室内ユニッ
ト、（３１は能力可変の圧縮機、（４）は室外熱交換器
、（４ｆ）は室外熱交換器用送風機、（５）は蒸発温度
検知器、（６）は凝縮温度検知器、（７）は制訂器、（
８）は圧縮機能力可変手段、（９）は室外送風機回転数
可変手段、（１０）は高低圧間熱交換アキュームレータ
、（１１）は高圧ガス配管、（１２）は高圧液配管、（
１３）は低圧ガス配管、（１４）は高圧液配管（１２）
のうち、高低圧熱交換アキュームし−りθ０）でサブク
ールした高圧サブクーノＬ管、（１８） （１９１（２
０）は各室内熱交換器、（１５ａｌ （１５ｂ） （１
５ｃ）は各室内熱交換器（１８） （１９１（２０）と
高圧液配管（１２）との間に連結された電子膨張弁、（
１６ａ） （１６ｂ） （１６ｃ）は各熱交換器（１８
１（１９１（２０）と高圧ガス配管（１１）との間に連
結された電磁開閉弁、（１７ａｌ 、 （１７ｂ） 、
（１７ｃ）は各熱交換器と低圧ガス配管（１３）との
間に連結された電磁開閉弁である。Hereinafter, one embodiment of the invention of B will be described with reference to the drawings. 1st
In the figure, (1) is the outdoor unit, (2) is the indoor unit, (31 is the variable capacity compressor, (4) is the outdoor heat exchanger, (4f) is the outdoor heat exchanger blower, and (5) is the evaporation temperature. Detector, (6) is a condensing temperature detector, (7) is a regulator, (
8) is a compression function force variable means, (9) is an outdoor blower rotation speed variable means, (10) is a high-low pressure heat exchange accumulator, (11) is a high-pressure gas pipe, (12) is a high-pressure liquid pipe, (
13) is a low pressure gas pipe, (14) is a high pressure liquid pipe (12)
Among them, high-pressure sub-cooled L tube, (18) (191 (2
0) is each indoor heat exchanger, (15al (15b) (1
5c) is an electronic expansion valve connected between each indoor heat exchanger (18) (191 (20) and the high pressure liquid pipe (12),
16a) (16b) (16c) each heat exchanger (18
1 (191 (20) and the electromagnetic on-off valve connected between the high pressure gas pipe (11), (17al, (17b),
(17c) is an electromagnetic on-off valve connected between each heat exchanger and the low pressure gas pipe (13).
なお、（１５ｄ）は電子膨張弁、（１６ｄ）、 （１７
ｄｌは電磁開閉弁である。In addition, (15d) is an electronic expansion valve, (16d), (17
dl is an electromagnetic on-off valve.
上記のように構成された冷凍サイクルにおいて、室内熱
交換器（１８） （１９）が暖房運転で室内熱交換器（
２０）が冷房運転の場合について詳述する。In the refrigeration cycle configured as described above, the indoor heat exchangers (18) and (19) are operated during heating operation.
The case where 20) is in cooling operation will be explained in detail.
圧縮機（８）を出た高圧ガス冷媒は、高圧ガス配管（１
１）を通り、電磁開閉弁（１６ａｌと（１６ｂｌより室
内熱交換器（１８）と（１９）とて各々凝縮液化し、全
開とされた電子膨張弁（１５ａ）と（１５ｂ）より高圧
液配管（１２）に流入する。高圧液冷媒は高圧液配管（
１２）より、電子膨張弁（１５ｃ）で減圧膨張されて室
内熱交換器（２０）に流入し、蒸発ガス化し電磁開閉弁
（１７ｃ）を経て低圧ガス配管（１３）に流入室外ユニ
ット（１）に運ばれアキュームし・−夕００）を経由し
て再び圧縮機（３）に帰り循環路が形成される。The high pressure gas refrigerant leaving the compressor (8) is transferred to the high pressure gas pipe (1
1), the electromagnetic on-off valves (16al and (16bl) are condensed and liquefied in the indoor heat exchangers (18) and (19), respectively, and the electronic expansion valves (15a) and (15b) which are fully open are connected to high-pressure liquid pipes. (12).The high pressure liquid refrigerant flows into the high pressure liquid pipe (
12), the gas is expanded under reduced pressure by the electronic expansion valve (15c), flows into the indoor heat exchanger (20), evaporates into gas, passes through the electromagnetic shut-off valve (17c), and flows into the low-pressure gas pipe (13) from the outdoor unit (1). It is carried to the compressor (3), where it is accumulated, and returned to the compressor (3) again to form a circulation path.
上記のように冷房負荷１台に対し暖房負荷２台の時には
、設定された目標蒸発温度ＥＴｏと目標凝縮温度ＣＴｏ
に対し蒸発温度ＥＴも凝縮温度ＣＴも低い状態となる。As mentioned above, when there is one cooling load and two heating loads, the set target evaporation temperature ETo and target condensation temperature CTo
In contrast, both the evaporation temperature ET and the condensation temperature CT are low.
この偏差△ＥＴ＝ＥＴｏ−ＥＴ、ΔＣＴ ＝ ＣＴ ｏ
−ＣＴに基づき、次式により圧縮機能力変更ｉ△Ｑ
ｅｏｍｐと室外熱交換器の熱交換能力変更量ΔＡＫｅと
を求める。This deviation △ET=ETo-ET, ΔCT = CT o
- Based on CT, compression function power change i△Q by the following formula
eomp and the heat exchange capacity change amount ΔAKe of the outdoor heat exchanger are determined.
本式の基本は、圧ｍ機能力を△Ｑｃｏｍｐだけアップす
ると凝縮温度がａだけ増加し、蒸発温度が−ｂだけ減少
することと、熱交換器を蒸発器として△ＡＫｅ能カアツ
カアップ凝縮温度がＣだけ上昇し、蒸発温度もｄだけ上
昇することにある。っまり 、
△ＣＴ＝ ａ△Ｑ ｃｏｍｐ＋ ｃ△ＡＫｅ△ＥＴ＝−
ｂムＱ ｃｏｍｐ＋ ｄ△ＡＫｅが成立する。The basics of this formula are that when the pressure m function is increased by △Qcomp, the condensing temperature increases by a, and the evaporation temperature decreases by -b. , and the evaporation temperature also rises by d. Completely, △CT= a△Q comp+ c△AKe△ET=-
bmuQcomp+dΔAKe holds true.
よって
本式の逆行列をとれば
ＴとＥＴｏ、ＣＴｏとの偏差として求めろかわりに、Ｅ
Ｔ、ＣＴよりその予測値を求め、その予測値とＥＴｏ、
ＣＴｏとの偏差とし、これに基づいて△Ｑ ｃｏｍｐ、
△ＡＫｅを求めろようにしてもよい。Therefore, if we take the inverse matrix of this equation, we can find it as the deviation between T, ETo, and CTo.Instead, E
The predicted value is obtained from T and CT, and the predicted value and ETo,
Based on the deviation from CTo, △Q comp,
It is also possible to calculate ΔAKe.
すなわち、現在および過去の蒸発温度、凝縮ンＨ度の過
渡データから蒸発温度予測値ＥＴＡと凝縮温度予測値Ｃ
Ｔ＾を算出する。That is, the predicted evaporation temperature value ETA and the predicted condensation temperature value C are calculated from the current and past transient data of the evaporation temperature and the condensation temperature.
Calculate T^.
となる。第２図にこのような制御の制御ブロック線図を
示す。becomes. FIG. 2 shows a control block diagram of such control.
このように求められたΔＱ ｃｏｍｐ、ΔＡＫｅに基づ
き例えば圧縮機（３）の回転数や、室外熱交換器用送風
機（４［）のファン回転数を制御すれば、常に暖房用高
圧圧力と冷房用低圧圧力が一定となる定常運転状態を室
外−室内間の情報伝送を複雑にすることなく実現できる
。If, for example, the rotation speed of the compressor (3) or the fan rotation speed of the outdoor heat exchanger blower (4) is controlled based on ΔQ comp and ΔAKe obtained in this way, the high pressure for heating and the low pressure for cooling can always be controlled. A steady operating state in which the pressure is constant can be achieved without complicating information transmission between the outdoors and indoors.
また、上記のようにムＥＴ ΔＣＴをＥＴ、にこで
Ｅ Ｔ ｒ 、 Ｅ Ｔ ｚ 、Ｅ Ｔ ３は蒸発温度
過渡データ
ＣＴ工、ＣＴ２．ＣＴ３は凝縮温度過渡データ
これらの予測値ＥＴａ、ＣＴａと各設定目標値との偏差
ΔＥＴ、△ＣＴとを求めろ。In addition, as mentioned above, ET ΔCT is ET, Niko
E T r , E T z , E T 3 are evaporation temperature transient data CT engineering, CT2. CT3 is condensing temperature transient data. Find deviations ΔET and ΔCT between these predicted values ETa and CTa and each set target value.
△Ｅ Ｔ ＝ Ｅ Ｔ ｏ Ｅ ＴＡ −ΔＣＴ＝Ｃ
Ｔｏ−ＣＴ＾
これらの偏差から同様に次式により圧ｍｍ能力変更量△
Ｑ ｃｏｍｐと室外熱交換器の熱交換能力変更旦ΔＡＫ
ｅとを求めろ。△E T = E T o E T A −ΔCT=C
To-CT^ From these deviations, the pressure mm capacity change amount △ can be calculated using the following formula.
Change in heat exchange capacity of Q comp and outdoor heat exchanger ΔAK
Find e.
そしてこれらΔＱ ｃｏｍｐ、ΔＡＫｅに基づいて圧縮
機（３）、室外熱交換器（４）の熱交換能力を制御すれ
ば、安定した運転が実現されるものである。Stable operation can be achieved by controlling the heat exchange capabilities of the compressor (3) and outdoor heat exchanger (4) based on these ΔQ comp and ΔAKe.
以上のように、この発明によれば、高圧ガス配管と高圧
液配管と低圧ガス配管の３配管を有する冷暖同時運転可
能な冷凍サイクルにおいて、冷媒蒸発温度と凝縮温度を
検出し、その温度あるいはそれから求められる予測温度
とあらかしめ設定した目標蒸発温度、凝縮温度との偏差
に基づいて、圧縮機能力を室外熱交換器の熱交換能力を
可変としたので制御情報の伝送が容易になす＜ｇ顆性が
増すという効果がある。As described above, according to the present invention, in a refrigeration cycle capable of simultaneous cooling and heating operations that has three pipes: a high-pressure gas pipe, a high-pressure liquid pipe, and a low-pressure gas pipe, the refrigerant evaporation temperature and condensation temperature are detected, and the refrigerant evaporation temperature and condensation temperature are Based on the deviation between the predicted temperature required and the preset target evaporation temperature and condensation temperature, the compression function power and the heat exchange capacity of the outdoor heat exchanger are made variable, making it easy to transmit control information. It has the effect of increasing sex.
第１図はこの発明の一実施例による冷凍サイクル装置の
構成図、第２図は開園ブロック線図、第３図（よ従来の
多室型冷暖房装置の構成図を示す。
図において（１）は室外ユニッＩ−、（２＋は室内ユニ
ッ１− 、（３１は圧縮機、（４）は室外熱交換器、（
５］ ｆ６１は温度検知器、（７）は制御器、（８）は
圧縮機能力制卸手段、（９）は室外送風開園手段、α０
）は高低圧熱交換アキュームし、−タ、（１］）は高圧
ガス配管、（１２）は高圧液配管、（］３）は低圧ガス
配管である。
なお、各図中同一符号は同一または相当部分を示す。Fig. 1 is a block diagram of a refrigeration cycle device according to an embodiment of the present invention, Fig. 2 is an opening block diagram, and Fig. 3 is a block diagram of a conventional multi-room air conditioning system. is the outdoor unit I-, (2+ is the indoor unit 1-, (31 is the compressor, (4) is the outdoor heat exchanger, (
5] f61 is a temperature sensor, (7) is a controller, (8) is a compression function force control means, (9) is an outdoor ventilation opening means, α0
) is a high-low pressure heat exchange accumulation, -ta, (1) is a high-pressure gas pipe, (12) is a high-pressure liquid pipe, and (]3 is a low-pressure gas pipe. Note that the same reference numerals in each figure indicate the same or corresponding parts.
Claims (2)
換器とを有し、室外機−室内機間に高圧ガス配管と高圧
液配管と低圧ガス配管の三連絡配管を有し、複数の室内
熱交換器には各々に前記高圧ガス配管と低圧ガス配管と
の流路のどちらか一方を選択可能とする電磁開閉弁を有
し、更に上記室内熱交換器の他端から電子膨張弁を介し
て上記高圧液配管に連結した冷暖混在形マルチ冷凍サイ
クルにおいて、冷媒の蒸発温度と凝縮温度とを検出する
手段と、その検出された蒸発温度および凝縮温度と設定
蒸発温度および設定凝縮温度との偏差を演算する手段と
、この蒸発温度および凝縮温度の偏差に基づいて上記圧
縮機の能力と上記室外送風機の回転数を制御する制御手
段とを備えたことを特徴とする冷暖混在形冷凍サイクル
装置。(1) The outdoor unit has a variable capacity compressor, a blower, and an outdoor heat exchanger, and has three connecting pipes between the outdoor unit and the indoor unit: a high-pressure gas pipe, a high-pressure liquid pipe, and a low-pressure gas pipe, and multiple Each of the indoor heat exchangers has an electromagnetic on-off valve that allows selection of either the high-pressure gas piping or the low-pressure gas piping, and an electronic expansion valve from the other end of the indoor heat exchanger. In the mixed cooling/heating multi-refrigeration cycle connected to the high-pressure liquid piping via a means for detecting the evaporation temperature and condensation temperature of the refrigerant, and the detected evaporation temperature and condensation temperature and the set evaporation temperature and set condensation temperature. and control means for controlling the capacity of the compressor and the rotational speed of the outdoor blower based on the deviation between the evaporation temperature and the condensation temperature. Device.
換器とを有し、室外機−室内機間に高圧ガス配管と高圧
液配管と低圧ガス配管の三連絡配管を有し、複数の室内
熱交換器には各々に前記高圧ガス配管と低圧ガス配管と
の流路のどちらか一方を選択可能とする電磁開閉弁を有
し、更に上記室内熱交換器の他端から電子膨張弁を介し
て上記高圧液配管に連結した冷暖混在形マルチ冷凍サイ
クルにおいて、冷媒の蒸発温度と凝縮温度とを検出する
手段と、その検出された蒸発温度、凝縮温度からその予
測値を演算する手段と、この予測された蒸発温度、凝縮
温度と設定蒸発温度、設定凝縮温度との偏差を演算する
手段と、この蒸発温度および凝縮温度の偏差に基づいて
上記圧縮機の能力と上記室外送風機の回転数を制御する
制御手段とを備えたことを特徴とする冷暖混在形冷凍サ
イクル装置。(2) The outdoor unit has a variable capacity compressor, a blower, and an outdoor heat exchanger, and has three connecting pipes between the outdoor unit and the indoor unit: a high-pressure gas pipe, a high-pressure liquid pipe, and a low-pressure gas pipe, and multiple Each of the indoor heat exchangers has an electromagnetic opening/closing valve that allows selection of either the high-pressure gas piping or the low-pressure gas piping, and an electronic expansion valve from the other end of the indoor heat exchanger. means for detecting the evaporation temperature and condensation temperature of the refrigerant, and means for calculating the predicted value from the detected evaporation temperature and condensation temperature in the cooling/heating mixed multi-refrigeration cycle connected to the high-pressure liquid pipe through the , a means for calculating the deviation between the predicted evaporation temperature and condensation temperature and the set evaporation temperature and the set condensation temperature, and the capacity of the compressor and the rotation speed of the outdoor blower based on the deviation of the evaporation temperature and the condensation temperature. A mixed cooling/heating refrigeration cycle device comprising: a control means for controlling.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10791590A JPH046374A (en) | 1990-04-23 | 1990-04-23 | Mixed cooling and heating type refrigerating cycle device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10791590A JPH046374A (en) | 1990-04-23 | 1990-04-23 | Mixed cooling and heating type refrigerating cycle device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH046374A true JPH046374A (en) | 1992-01-10 |
Family
ID=14471280
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10791590A Pending JPH046374A (en) | 1990-04-23 | 1990-04-23 | Mixed cooling and heating type refrigerating cycle device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH046374A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013102953A1 (en) | 2012-01-05 | 2013-07-11 | 三菱電機株式会社 | Air-conditioning device |
-
1990
- 1990-04-23 JP JP10791590A patent/JPH046374A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013102953A1 (en) | 2012-01-05 | 2013-07-11 | 三菱電機株式会社 | Air-conditioning device |
| US9719691B2 (en) | 2012-01-05 | 2017-08-01 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
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