JPH01318861A - Two-room cooler-heater - Google Patents
Two-room cooler-heaterInfo
- Publication number
- JPH01318861A JPH01318861A JP15100188A JP15100188A JPH01318861A JP H01318861 A JPH01318861 A JP H01318861A JP 15100188 A JP15100188 A JP 15100188A JP 15100188 A JP15100188 A JP 15100188A JP H01318861 A JPH01318861 A JP H01318861A
- Authority
- JP
- Japan
- Prior art keywords
- room
- load
- compressor
- expansion valve
- indoor
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 33
- 238000010438 heat treatment Methods 0.000 claims abstract description 20
- 238000004378 air conditioning Methods 0.000 claims description 11
- 238000001704 evaporation Methods 0.000 claims 1
- 238000001816 cooling Methods 0.000 abstract description 18
- 238000005057 refrigeration Methods 0.000 abstract description 5
- 238000010586 diagram Methods 0.000 description 19
- 239000007788 liquid Substances 0.000 description 3
- 239000007787 solid Substances 0.000 description 2
- 206010028980 Neoplasm Diseases 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
Landscapes
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Control Of Temperature (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、インバータ圧縮機により駆動される冷凍サイ
クル中に電動膨張弁を有し、該電動膨張弁によって冷媒
流量制御が行われる冷暖房装置に係り、特に１台の室外
機に２台の室内機が接続されたものに関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an air-conditioning and heating system that has an electric expansion valve in a refrigeration cycle driven by an inverter compressor, and in which refrigerant flow rate is controlled by the electric expansion valve. In particular, the present invention relates to one in which two indoor units are connected to one outdoor unit.
（従来の技術）
従来、２台の室内機を有する多室型冷暖房装置は、それ
ぞれの室内機に対応する膨張弁を有し、該膨張弁制御は
、それぞれ室内機の熱交換器と対応して得られる冷媒過
熱度に基づいて行われていた。第７図は、従来の二室冷
暖房装置の全体構成の概略を示す図である。同図におい
て、点線矢印は冷房運転時の冷媒の流れを、実線矢印は
暖房運転時の冷媒の流れを示す。つまり、冷房の場合、
圧縮機１で圧縮された冷媒蒸気は、四方弁２を介して室
外熱交換器３にて凝縮液化し、レシーバ−タンク４に貯
えられる。この後、冷媒液はそれぞれの室内機Ａ、Ｂに
対応する電動膨張弁６ａ、６ｂにて減圧され、室内熱交
換器７，８において、低圧蒸気となり、再び四方弁２を
介して圧縮機Ｉに戻る。この時、電動膨張弁６ａ、６ｂ
の開閉度の制？３１１ｇ、ｈ（第８図参照）は、各電動
膨張弁６ａ、５ｂの出口バイブに取付けられた温度セン
サ１６ａ、Ｌ６ｂから得られる温度（ＴＡ）、（ＴＢ）
と圧縮機１の吸込パイプに取付けられた温度センサ９か
ら得られる温度（ＴＳ）との差（ＴＳ−ＴＡ）、（ＴＳ
−ＴＢ）が一定となるようにそれぞれ行われる。また、
暖房の場合には、冷媒の流れは冷房の場合の逆方向とな
り、圧縮された冷媒蒸気は室内側熱交換器７，８にて凝
縮した後レシーバ−タンク４を経て暖房用膨張弁５にて
減圧され、室外熱交換器３にて低圧蒸気となり再び圧縮
機１に戻る。この時、暖房用膨張弁５の開閉度の制御ｉ
（第８図参照）は、その出口バイブに取付けられた温
度センサ１７から得られる温度（ＴＣ）と圧縮機１の吸
込パイプに取付けられた温度センサ９から得られる温度
（ＴＳ）との差（ＴＳ−ＴＣ）が一定となるように行わ
れる。(Prior Art) Conventionally, a multi-room air conditioning system having two indoor units has an expansion valve corresponding to each indoor unit, and the expansion valve control corresponds to the heat exchanger of each indoor unit. This was done based on the degree of superheating of the refrigerant obtained. FIG. 7 is a diagram schematically showing the overall configuration of a conventional two-room air conditioning system. In the figure, dotted arrows indicate the flow of refrigerant during cooling operation, and solid arrows indicate the flow of refrigerant during heating operation. In other words, in the case of cooling,
Refrigerant vapor compressed by the compressor 1 is condensed and liquefied in an outdoor heat exchanger 3 via a four-way valve 2 and stored in a receiver tank 4. Thereafter, the refrigerant liquid is depressurized by the electric expansion valves 6a and 6b corresponding to the indoor units A and B, becomes low-pressure steam in the indoor heat exchangers 7 and 8, and is again passed through the four-way valve 2 to the compressor I. Return to At this time, the electric expansion valves 6a, 6b
Is there a restriction on the degree of opening and closing? 311g and h (see Fig. 8) are temperatures (TA) and (TB) obtained from temperature sensors 16a and L6b attached to the outlet vibes of each electric expansion valve 6a and 5b.
and the temperature (TS) obtained from the temperature sensor 9 attached to the suction pipe of the compressor 1 (TS - TA), (TS
-TB) are respectively performed so that they are constant. Also,
In the case of heating, the flow of the refrigerant is in the opposite direction to that in the case of cooling, and the compressed refrigerant vapor is condensed in the indoor heat exchangers 7 and 8, then passes through the receiver tank 4, and then flows in the expansion valve 5 for heating. It is depressurized and becomes low-pressure steam in the outdoor heat exchanger 3 and returns to the compressor 1 again. At this time, control i of the opening/closing degree of the heating expansion valve 5
(See Figure 8) is the difference between the temperature (TC) obtained from the temperature sensor 17 attached to the outlet vibrator and the temperature (TS) obtained from the temperature sensor 9 attached to the suction pipe of the compressor 1 ( TS-TC) is held constant.
このように、従来サイクルでは、暖房用膨張弁５及び電
動膨張弁６ａ、６ｂはその出口冷媒と圧縮機吸込冷媒と
の温度差が一定となるように開閉制御され、冷凍サイク
ルの安定のみに使用される。In this way, in the conventional cycle, the heating expansion valve 5 and the electric expansion valves 6a and 6b are controlled to open and close so that the temperature difference between the outlet refrigerant and the compressor suction refrigerant is constant, and are used only to stabilize the refrigeration cycle. be done.
従って、各室内機Ａ、Ｂの負荷がそれぞれ変動してもそ
の合計負荷が一定であれば各室内熱交換器７．８に流れ
る冷媒流量もほとんど変わらず、冷暖房能力もほぼ一定
である。なお、室内設定温度（ＴＲａ）、（ＴＲｂ）と
室温（Ｔ Ｉ ａ）、 （Ｔ Ｉ ｂ）との差から得ら
れる負荷量（ＴＲａ −Ｔ Ｉ ａ）、 （ＴＲｂ−Ｔ
Ｉｂ）は、第８図に示すごとく圧縮機周波数ｆ、すなわ
ち圧縮機１の出力を決定することのみに使用される。Therefore, even if the loads of the indoor units A and B vary, if the total load is constant, the flow rate of refrigerant flowing into each indoor heat exchanger 7.8 will hardly change, and the heating and cooling capacity will also remain almost constant. In addition, the load amount (TRa - T I a), (TRb - T
Ib) is used only to determine the compressor frequency f, ie the output of the compressor 1, as shown in FIG.
（発明が解決しようとする課題）
しかし、この従来の膨張弁制御方法では、圧縮機の出力
の決定と、冷凍サイクルの安定とが独立して行われてい
るため、二室同時運転の場合、各室内機の負荷の合計が
一定であれば、一方の室内機の負荷が小さく他方の室内
機の負荷が大きい場合でも各室内熱交換器への冷媒流量
はほとんど等しく分配されるため、能力もほぼ等しくな
る。(Problems to be Solved by the Invention) However, in this conventional expansion valve control method, the determination of the output of the compressor and the stabilization of the refrigeration cycle are performed independently, so in the case of simultaneous operation of two chambers, If the total load of each indoor unit is constant, even if one indoor unit has a small load and the other indoor unit has a large load, the refrigerant flow rate to each indoor heat exchanger will be distributed almost equally, and the capacity will also increase. almost equal.
本発明は、かかる実情に鑑みてなされたもので、二室同
時運転の場合、各室内機の負荷は、圧縮機周波数を決定
するのに使用されるだけでなく膨張弁の開閉制御にも使
用され、各室内熱交換器への冷媒流量を制御して各室内
機の負荷に見合った冷暖房能力を発生する膨張弁制御が
可能な冷暖房装置を提供することを目的とする。The present invention was made in view of the above circumstances, and in the case of simultaneous operation of two rooms, the load of each indoor unit is used not only to determine the compressor frequency but also to control the opening and closing of the expansion valve. It is an object of the present invention to provide a heating and cooling device capable of controlling an expansion valve to generate heating and cooling capacity commensurate with the load of each indoor unit by controlling the flow rate of refrigerant to each indoor heat exchanger.
（課題を解決するための手段）
本発明の二室冷暖房装置は、１台の室外機に２台の室内
機が各々電動膨張弁を介して接続され、圧縮機により圧
縮された冷媒を各室内熱交換器もしくは室外熱交換器で
凝縮させ、さらに上記冷媒を各電動膨張弁で膨張、減圧
させた後、上記室外熱交換器もしくは各室内熱交換器で
蒸発させて各室内の暖房もしくは冷房を行うようにした
冷暖房装置において、上記電動膨張弁の開閉度は、各室
内機に設置された室温設定器の設定温度と実際の室内温
度との差から得られる各室内機の負荷の比により決定さ
れるものである。(Means for Solving the Problems) In the two-room air conditioning system of the present invention, two indoor units are connected to one outdoor unit through electric expansion valves, and refrigerant compressed by a compressor is delivered to each room. The refrigerant is condensed in a heat exchanger or an outdoor heat exchanger, further expanded and depressurized by each electric expansion valve, and then evaporated in the outdoor heat exchanger or each indoor heat exchanger to heat or cool each room. In the air conditioning system, the degree of opening and closing of the electric expansion valve is determined by the ratio of the load on each indoor unit obtained from the difference between the set temperature of the room temperature setting device installed in each indoor unit and the actual indoor temperature. It is something that will be done.
（作用）
第１図に点線矢印で示すように、２台の室内機Ａ、Ｂを
同時に冷房運転する場合、圧縮機１で圧縮された冷媒蒸
気は、四方弁２を介して室外熱交換器３にて凝縮液化す
る。こうして得られた冷媒液は、２台のレシーバ−タン
ク４ａ、４ｂに貯えられる。この後、冷媒液は、それぞ
れの室内機Ａ。(Function) As shown by the dotted arrows in FIG. Condensate and liquefy in step 3. The refrigerant liquid thus obtained is stored in two receiver tanks 4a and 4b. After this, the refrigerant liquid is distributed to each indoor unit A.
Ｂに対応する電動膨張弁６ａ、６ｂにて減圧し、室内熱
交換器７．８において低圧蒸気となり、再び四方弁２を
介して圧縮機１に戻る。It is depressurized by the electric expansion valves 6a and 6b corresponding to B, becomes low-pressure steam in the indoor heat exchanger 7.8, and returns to the compressor 1 via the four-way valve 2 again.
この際、第２図に示すように、マイコン制御部１３の圧
縮機周波数制御部１４には、室内機Ａの設定温度（Ｔ
Ｉ ａ ）とその室内の実測室温（ＴＲａ）、室内機Ｂ
の設定温度（Ｔｌｂ）とその室内の実測室温（ＴＲｂ）
とが入力される。一方、膨張弁開閉制御部１５には、電
動膨張弁６ａ、６ｂの出口バイブに取付けた温度センサ
１６ａ、１６ｂから得られる温度（ＴＡ）、（ＴＢ）と
圧縮機１の吸込パイプに取付けた温度センサ９から得ら
れる温度（ＴＳ）とが入力される。このうち、圧縮機周
波数制御部１４では、室内機Ａの室内負荷（ＴＲａ−Ｔ
ｌａ）と室内機Ｂの室内負荷（ＴＲｂ−Ｔｌｂ）とによ
って圧縮機１の出力を制御するとともに、各室内負荷（
ＴＲａ −Ｔ Ｉ ａ）、 （ＴＲｂ−Ｔｌｂ）を各室
内負荷係数ａ、ｂに変換して膨張弁開閉制御部１５に出
力する。一方、膨張弁開閉制御部１５では、各電動膨張
弁６ａ、６ｂの出口温度（ＴＡ）、（ＴＢ）の平均値（
ＴＡ＋ＴＢ）／２と圧縮機１の吸込温度（ＴＳ）との差
から得られる過熱度が一定となるように冷凍バランスを
保ちつつ、各室内負荷係数ａ、ｂの負荷比に応じて各電
動膨張弁６ａ、６ｂの開閉度を制御し、これによって冷
房運転が行われる。次に、暖房運転の場合、第１図に実
線矢印で示すように、冷媒蒸気の流れは、冷房運転の場
合と逆方向になり、室内熱交換器７．８で凝縮液化し、
室外熱交換器３で低圧蒸気となる。その他各部の働きは
、上記冷房運転の場合と制御特性が異なる以外は同様で
ある。At this time, as shown in FIG.
I a ), the actual measured room temperature in the room (TRa), and indoor unit B
The set temperature (Tlb) and the actual measured room temperature (TRb)
is input. On the other hand, the expansion valve opening/closing control unit 15 stores the temperatures (TA) and (TB) obtained from temperature sensors 16a and 16b attached to the outlet vibrators of the electric expansion valves 6a and 6b, and the temperature attached to the suction pipe of the compressor 1. The temperature (TS) obtained from the sensor 9 is input. Of these, the compressor frequency control section 14 controls the indoor load (TRa-T) of the indoor unit A.
The output of the compressor 1 is controlled by the indoor load (TRb-Tlb) of the indoor unit B and the indoor load (
TRa - T I a), (TRb - Tlb) are converted into respective indoor load coefficients a and b and output to the expansion valve opening/closing control section 15. On the other hand, in the expansion valve opening/closing control section 15, the average value (
While maintaining the refrigeration balance so that the degree of superheat obtained from the difference between TA+TB)/2 and the suction temperature (TS) of compressor 1 is constant, each electric expansion is performed according to the load ratio of each indoor load coefficient a and b. The degree of opening and closing of the valves 6a and 6b is controlled, thereby performing cooling operation. Next, in the case of heating operation, as shown by the solid arrow in Fig. 1, the flow of refrigerant vapor is in the opposite direction to that in cooling operation, and is condensed and liquefied in the indoor heat exchanger 7.8.
It becomes low pressure steam in the outdoor heat exchanger 3. The functions of the other parts are the same as in the case of the cooling operation described above except for the control characteristics.
（実施例） 以下、本発明の一実施例を図面を参照して説明する。(Example) Hereinafter, one embodiment of the present invention will be described with reference to the drawings.
第１図は、二基冷暖房装置の全体構成の概略を示す回路
図である。FIG. 1 is a circuit diagram schematically showing the overall configuration of a two-unit air conditioning system.
同図において点線矢印で示すように、冷房運転の場合、
圧縮機ｌにより圧縮された冷媒蒸気は、四方弁２を介し
て室外熱交換器３にて凝縮液化し、レシーバ−タンク４
ａ、４ｂに導かれる。その後、冷媒は、それぞれ電動膨
張弁６ａ、６ｂにて減圧され、各室内機Ａ、Ｂの室内熱
交換器７，８にて蒸発し、分岐管１８にて合流した後、
再び四方弁２を介して圧縮機ｌに戻る。As shown by the dotted arrow in the figure, in the case of cooling operation,
The refrigerant vapor compressed by the compressor 1 is condensed and liquefied in the outdoor heat exchanger 3 via the four-way valve 2, and then transferred to the receiver tank 4.
a, lead to 4b. Thereafter, the refrigerant is depressurized by the electric expansion valves 6a and 6b, evaporated in the indoor heat exchangers 7 and 8 of each indoor unit A and B, and then merged in the branch pipe 18.
It returns to the compressor l via the four-way valve 2 again.
この際、圧縮機１の周波数及び電動膨張弁６ａ。At this time, the frequency of the compressor 1 and the electric expansion valve 6a.
６ｂの開閉度は、次のようにして決定される。The opening/closing degree of 6b is determined as follows.
すなわち、第１図及び第２図に示すように、マイコン制
御部１３の圧縮機周波数制御部１４に、各室温設定器１
２ａ、１２ｂでの設定温度（Ｔｌａ）、（Ｔ Ｉ ｂ）
と、各室内温度センサＩｌａ、１１ｂから得られる実測
室温（ＴＲａ）、（ＴＲｂ）とが入力され、膨張弁開閉
制御部１５に、各膨張弁６ａ、６ｂの出口バイブに取付
けられた温度センサ１６ａ、１６ｂから得られる温度（
ＴＡ）、（ＴＢ）と、圧縮機１の吸込パイプに取付けら
れた温度センサ９から得られる温度（ＴＳ）とが入力さ
れる。That is, as shown in FIGS. 1 and 2, each room temperature setting device 1 is connected to the compressor frequency control section 14 of the microcomputer control section 13.
Set temperature at 2a and 12b (Tla), (T I b)
and the actual measured room temperature (TRa), (TRb) obtained from each indoor temperature sensor Ila, 11b are input, and the temperature sensor 16a attached to the outlet vibrator of each expansion valve 6a, 6b is inputted to the expansion valve opening/closing control section 15. , 16b (
TA), (TB), and the temperature (TS) obtained from the temperature sensor 9 attached to the suction pipe of the compressor 1 are input.
このうち、圧縮機周波数Ｍ ａ１１部１４では、表１に
示されるような関係に基づいて、各室温設定器１２ａ、
１２ｂでの設定温度と各室内の実測室温との差（ＴＲａ
−Ｔｌ ａ）、（ＴＲｂ−Ｔｌ ｂ）を各室内の負荷と
してとらえ、その範囲を負荷係数ａ、ｂに置換える。そ
して、表２に示すように、各負荷係数の合計から圧縮機
ｌの周波数ｆを決定する。Among these, in the compressor frequency M a11 section 14, based on the relationship shown in Table 1, each room temperature setting device 12a,
The difference between the set temperature at 12b and the actual room temperature in each room (TRa
-Tl a) and (TRb-Tl b) are taken as the loads in each room, and their ranges are replaced by load coefficients a and b. Then, as shown in Table 2, the frequency f of the compressor l is determined from the sum of each load coefficient.
（以下余白）
表 １
表 ２
［
一方、膨張弁開閉制御部１５では、圧縮機周波数制御部
１４で得られた各室内機Ａ、Ｂの負荷係数ａ、ｂの信号
を受け、各電動膨張弁６ａ、６ｂの開閉度ｃ、ｄの割合
を決定する。この各電動膨張弁６ａ、６ｂの開閉度ｃ、
ｄの割合を決定するに当たっては、第３図に示すように
、各膨張弁６ａ、６ｂの出口温度（ＴＡ）、（ＴＢ）の
平均温度（ＴＡ＋ＴＢ）／２と圧縮機１の吸込温度（Ｔ
Ｓ）との差から得られる過熱度を一定値に保つ冷媒流量
の理想特性図を予め求めておく。そして、この理想特性
図に基づいて上記負荷係数ａ、ｂと膨張弁開閉度ｃ、ｄ
との関係を求め、この関係に基づいて決定した第４図に
示す制御特性図によって決定する。なお、第４図は第３
図に示す理想特性図に基づいて作成した制御特性図であ
る。(Margin below) Table 1 Table 2 [On the other hand, the expansion valve opening/closing control unit 15 receives the signals of the load coefficients a and b of each indoor unit A and B obtained by the compressor frequency control unit 14, and controls each electric expansion valve. Determine the ratio of opening/closing degrees c and d of 6a and 6b. The opening/closing degree c of each electric expansion valve 6a, 6b,
In determining the ratio of d, as shown in FIG.
An ideal characteristic diagram of the refrigerant flow rate that maintains the degree of superheating obtained from the difference with S) at a constant value is determined in advance. Then, based on this ideal characteristic diagram, the load coefficients a, b and the expansion valve opening/closing degrees c, d are
This is determined based on the control characteristic diagram shown in FIG. 4, which is determined based on this relationship. In addition, Figure 4 is the third
It is a control characteristic diagram created based on the ideal characteristic diagram shown in the figure.
次に、暖房運転の場合、第１図に実線矢印で示すように
、圧縮機１により圧縮された冷媒蒸気は、四方弁２を介
して分岐管１日で分岐した後、各室内機Ａ、Ｂの室内熱
交換器７，８にて凝縮液化し、レシーバ−タンク４ａ、
４ｂに導かれる。その後、冷媒は、それぞれの電動膨張
弁６ａ、６ｂにて減圧され、室外熱交換器３にて蒸発し
、再び四方弁２を介して圧縮機１に戻る。Next, in the case of heating operation, as shown by the solid line arrow in FIG. Condensed and liquefied in the indoor heat exchangers 7 and 8 of B, the receiver tank 4a,
Guided by 4b. Thereafter, the refrigerant is depressurized by the electric expansion valves 6a and 6b, evaporated in the outdoor heat exchanger 3, and returned to the compressor 1 via the four-way valve 2 again.
この際、圧縮機１の周波数及び電動膨張弁６ａ。At this time, the frequency of the compressor 1 and the electric expansion valve 6a.
６ｂの開閉度は冷房運転時と同様にして決定される。The opening/closing degree of 6b is determined in the same manner as during cooling operation.
ただし、冷媒の流れが逆方向であるため、冷媒流量の理
想特性図は第５図に示すような特性図になる。そのため
、制御特性図も第６図に示すような特性図になる。However, since the flow of the refrigerant is in the opposite direction, the ideal characteristic diagram of the refrigerant flow rate is as shown in FIG. Therefore, the control characteristic diagram also becomes a characteristic diagram as shown in FIG.
次に、上記実施例と同一特性の二基冷暖房装置に基づい
て電動膨張弁６ａ、６ｂの開閉度ｃ、 ｄを決定する
具体例を示す。Next, a specific example will be shown in which the opening/closing degrees c and d of the electric expansion valves 6a and 6b are determined based on a two-unit air conditioning system having the same characteristics as those of the above embodiment.
〔第１具体例〕
冷房時において、室内機Ａの負荷（ＴＲａ−ＴＩａ）が
７±０．５ｄｅｇであり、室内機Ｂの負荷（ＴＲｂ−Ｔ
Ｉ ｂ）が３±０．５ｄｅｇである場合、それぞれの
負荷係数ａ、ｂは表１より室内機Ａが９、室内機Ｂが５
となる。また、この時の圧縮機周波数ｆは、負荷係数ａ
、ｂの合計が１４なので表２より８０七と決定される。[First specific example] During cooling, the load on indoor unit A (TRa-TIa) is 7±0.5 deg, and the load on indoor unit B (TRb-T
When Ib) is 3±0.5deg, the respective load coefficients a and b are 9 for indoor unit A and 5 for indoor unit B from Table 1.
becomes. Also, the compressor frequency f at this time is the load coefficient a
, b is 14, so from Table 2 it is determined to be 807.
そして、第４図から室内機Ａの膨張弁開閉度Ｃの係数は
１３、室内機Ｂの膨張弁開閉度ｄの係数は６と決定され
、冷媒流量の分配が行われる。Then, from FIG. 4, the coefficient of the expansion valve opening/closing degree C of indoor unit A is determined to be 13, and the coefficient of the expansion valve opening/closing degree d of indoor unit B is determined to be 6, and the refrigerant flow rate is distributed.
〔第２具体例］
暖房時において、室内機Ａの負荷（ＴＲａ−ＴＩａ）が
７±０．５ｄｅｇであり、室内機Ｂの負荷（ＴＲｂ−Ｔ
ｌｂ）が３±０．５ｄｅｇである場合、それぞれの負荷
係数は表１より室内機Ａが９、室内機Ｂが５となる。ま
た、この時の圧縮機周波数は、負荷係数の合計が１４な
ので表２より５ｏｌ（ｚと決定される。そして、第６図
から室内機Ａの膨張弁開閉度ｆの係数は１２、室内機Ｂ
の膨張弁開閉度ｄの係数は５と決定され、冷媒流量の分
配が行われる。[Second specific example] During heating, the load on indoor unit A (TRa-TIa) is 7±0.5deg, and the load on indoor unit B (TRb-T
lb) is 3±0.5deg, the respective load coefficients are 9 for indoor unit A and 5 for indoor unit B from Table 1. In addition, the compressor frequency at this time is determined as 5ol(z) from Table 2 since the total load coefficient is 14.And from Fig. 6, the coefficient of the expansion valve opening/closing degree f of indoor unit A is 12, B
The coefficient of the expansion valve opening/closing degree d is determined to be 5, and the refrigerant flow rate is distributed.
（発明の効果）
以上述べたように、本発明によれば、各室の室内機の負
荷に応じた電動膨張弁の開閉度を決定することにより、
二基同時運転において、より細かな能力可変が可能とな
り、各室の快適性が向上する。また、室内配管及び室外
配管の抵抗の変化などにより、各室内機の冷暖房能力が
アンバランスになっても、室内機の負荷に見合った冷媒
流量が得られるため、安定した冷暖房能力が確保される
。(Effects of the Invention) As described above, according to the present invention, by determining the opening/closing degree of the electric expansion valve according to the load of the indoor unit in each room,
Simultaneous operation of two units allows for finer adjustment of capacity, improving comfort in each room. In addition, even if the heating and cooling capacity of each indoor unit becomes unbalanced due to changes in the resistance of indoor and outdoor piping, a refrigerant flow rate commensurate with the load of the indoor unit can be obtained, ensuring stable heating and cooling capacity. .
第１図ないし第６図は本発明の図面を示し、第１図は二
基冷暖房装置の全体構成の概略を示す図、第２図はマイ
コン制御部の概略ブロック図、第３図は冷房運転時の圧
縮機の周波数における各室内機への冷媒流量の理想値及
びそれに対応する各室の膨張弁開閉度の関係を示す曲線
図、第４図は冷房運転時の圧縮機の周波数における各室
内機の膨張弁開閉度及びそれに対応する負荷係数の関係
を示す曲線図、第５図は暖房運転時の圧縮機の周波数に
おける各室内機への冷媒流量の理想値及びそれに対応す
る各室の膨張弁開閉度の係数の関係を示す曲線図、第６
図は暖房運転時の圧縮機の周波数における各室内機の膨
張弁開閉度の係数及びそれに対応する負荷係数の関係を
示す曲線図である。
第７図は従来の二基冷暖房装置の全体構成の概略を示す
図、第８図は従来のマイコン制御部の概略ブロック図で
ある。
１・・・圧縮機
３・・・室外熱交換器
４ａ、４ｂ・・・レシーバ−タンク
５・・・暖房用膨張弁
６・・・電動膨張弁
７．８・・・室内熱交換器
９・・・圧縮機吸込バイブ表面温度センサ１１ａ、ｌｌ
ｂ・・・室内温度センサ
１２ａ、１２ｂ・・・室内温度設定器
１３・・・マイコン制御部
１４・・・圧縮機周波数制御部
１５・・・膨張弁開閉制御部
１６ａ、１６ｂ・・・膨張弁出ロバイブ表面温度センサ
第２図
！ｌ￥ ０
電
＋＋１ｌｌｌｌ
Ｌ瘍体ゴトぜ℃ヱ ♀ ♀ （ＯｕＤ 臂
Ｎ ０第７図
第８図Figures 1 to 6 show drawings of the present invention, Figure 1 is a diagram showing the outline of the overall configuration of the two-unit air conditioning system, Figure 2 is a schematic block diagram of the microcomputer control section, and Figure 3 is the cooling operation. Figure 4 is a curve diagram showing the relationship between the ideal value of the refrigerant flow rate to each indoor unit at the frequency of the compressor and the corresponding opening/closing degree of the expansion valve in each room at the frequency of the compressor during cooling operation. A curve diagram showing the relationship between the opening/closing degree of the expansion valve of the machine and the corresponding load coefficient. Figure 5 shows the ideal value of the refrigerant flow rate to each indoor unit and the corresponding expansion of each room at the frequency of the compressor during heating operation. Curve diagram showing the relationship between coefficients of valve opening/closing degree, No. 6
The figure is a curve diagram showing the relationship between the expansion valve opening/closing coefficient of each indoor unit and the corresponding load coefficient at the frequency of the compressor during heating operation. FIG. 7 is a diagram schematically showing the overall configuration of a conventional two-unit air-conditioning system, and FIG. 8 is a schematic block diagram of a conventional microcomputer control section. 1...Compressor 3...Outdoor heat exchanger 4a, 4b...Receiver tank 5...Heating expansion valve 6...Electric expansion valve 7.8...Indoor heat exchanger 9. ...Compressor suction vibe surface temperature sensor 11a, ll
b... Indoor temperature sensor 12a, 12b... Indoor temperature setter 13... Microcomputer control section 14... Compressor frequency control section 15... Expansion valve opening/closing control section 16a, 16b... Expansion valve Diagram 2 of the external vibe surface temperature sensor! l￥ 0 Den++1lllll L tumor body stiff ℃ヱ ♀ ♀ (OuD armpit
N 0 Figure 7 Figure 8
Claims (1)
して接続され、圧縮機により圧縮された冷媒を各室内熱
交換器もしくは室外熱交換器で凝縮させ、さらに上記冷
媒を各電動膨張弁で膨張、減圧させた後、上記室外熱交
換器もしくは各室内熱交換器で蒸発させて各室内の暖房
もしくは冷房を行うようにした冷暖房装置において、上
記電動膨張弁の開閉度は、各室内機に設置された室温設
定器の設定温度と実際の室内温度との差から得られる各
室内機の負荷の比により決定されることを特徴とする二
室冷暖房装置。1) Two indoor units are connected to one outdoor unit through electric expansion valves, and the refrigerant compressed by the compressor is condensed in each indoor heat exchanger or outdoor heat exchanger, and the refrigerant is further In an air-conditioning system that heats or cools each room by expanding and reducing pressure with each electric expansion valve and then evaporating it with the outdoor heat exchanger or each indoor heat exchanger, the opening/closing degree of the electric expansion valve is A two-room air conditioning/heating system characterized in that the load ratio of each indoor unit is determined based on the difference between the set temperature of a room temperature setting device installed in each indoor unit and the actual indoor temperature.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15100188A JPH01318861A (en) | 1988-06-17 | 1988-06-17 | Two-room cooler-heater |
| US07/367,141 US4926653A (en) | 1988-06-17 | 1989-06-16 | Multi-room type air-conditioning equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15100188A JPH01318861A (en) | 1988-06-17 | 1988-06-17 | Two-room cooler-heater |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH01318861A true JPH01318861A (en) | 1989-12-25 |
Family
ID=15509119
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15100188A Pending JPH01318861A (en) | 1988-06-17 | 1988-06-17 | Two-room cooler-heater |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01318861A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000241002A (en) * | 1999-02-19 | 2000-09-08 | Daikin Ind Ltd | Multiple air conditioner |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6124937A (en) * | 1984-07-16 | 1986-02-03 | Mitsubishi Electric Corp | Control of multiple room air-conditioning system |
-
1988
- 1988-06-17 JP JP15100188A patent/JPH01318861A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6124937A (en) * | 1984-07-16 | 1986-02-03 | Mitsubishi Electric Corp | Control of multiple room air-conditioning system |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000241002A (en) * | 1999-02-19 | 2000-09-08 | Daikin Ind Ltd | Multiple air conditioner |
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