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JP4803237B2 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
JP4803237B2
JP4803237B2 JP2008276087A JP2008276087A JP4803237B2 JP 4803237 B2 JP4803237 B2 JP 4803237B2 JP 2008276087 A JP2008276087 A JP 2008276087A JP 2008276087 A JP2008276087 A JP 2008276087A JP 4803237 B2 JP4803237 B2 JP 4803237B2
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refrigerant
degree
outdoor
heat exchanger
unit
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JP2009019875A (en
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聡 河野
昌弘 岡
和彦 谷
岡本　　敦
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Daikin Industries Ltd
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Daikin Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/025—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units
    • F25B2313/0253—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple outdoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/001—Charging refrigerant to a cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/003—Control issues for charging or collecting refrigerant to or from a cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/19—Refrigerant outlet condenser temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Description

本発明は、複数の熱源ユニットを備える空気調和装置に関する。   The present invention relates to an air conditioner including a plurality of heat source units.

従来より、熱源ユニットと、利用ユニットと、熱源ユニットと利用ユニットとを接続する連絡配管とを備える空気調和装置がある。このような空気調和装置では、予め熱源ユニットに所定量の冷媒を充填しておき、現地施工時に熱源ユニットと利用ユニットとを接続する連絡配管の長さに応じて冷媒を追加充填する方法が採用されている。しかし、現地における空気調和装置の設置状況によって、冷媒配管の長さが異なってくるため、適正な量の冷媒を冷媒回路へ充填することが困難な場合があった。   Conventionally, there is an air conditioner including a heat source unit, a utilization unit, and a connecting pipe that connects the heat source unit and the utilization unit. In such an air conditioner, a method is adopted in which a predetermined amount of refrigerant is filled in the heat source unit in advance, and additional refrigerant is charged according to the length of the connecting pipe connecting the heat source unit and the utilization unit at the time of on-site construction. Has been. However, since the length of the refrigerant pipe varies depending on the installation condition of the air conditioner in the field, it may be difficult to fill the refrigerant circuit with an appropriate amount of refrigerant.

そこで、冷媒回路への冷媒の追加充填時に、利用ユニットを冷房運転しつつ凝縮器として機能している熱源側熱交換器の出口における冷媒の過冷却度によって冷媒回路に充填されている冷媒量を判断し、その過冷却度が所定値に達するまで冷媒充填を継続するような運転が提案されている（例えば、特許文献１参照）。
特開２００６−２３０７２号公報 Therefore, at the time of additional charging of the refrigerant into the refrigerant circuit, the amount of refrigerant charged in the refrigerant circuit is determined by the degree of supercooling of the refrigerant at the outlet of the heat source side heat exchanger that functions as a condenser while cooling the use unit. An operation has been proposed in which the refrigerant charging is continued until the degree of supercooling reaches a predetermined value (see, for example, Patent Document 1).
JP 2006-23072 A

しかしながら、複数の熱源ユニットを備える空気調和装置において、冷媒回路に冷媒を充填する場合、各熱源ユニットの設置状況や温度状況等によって冷媒が偏流し、各熱源側熱交換器の出口における各過冷却度が偏ることがある。このため、熱源側熱交換器の出口における冷媒の過冷却度によって冷媒回路に充填されている冷媒量が判断されると、その判断の精度が低下するおそれがある。   However, in an air conditioner equipped with a plurality of heat source units, when the refrigerant is filled in the refrigerant circuit, the refrigerant drifts depending on the installation status, temperature status, etc. of each heat source unit, and each subcooling at the outlet of each heat source side heat exchanger The degree may be biased. For this reason, if the amount of the refrigerant | coolant with which a refrigerant circuit is filled is judged by the supercooling degree of the refrigerant | coolant in the exit of a heat source side heat exchanger, there exists a possibility that the precision of the judgment may fall.

本発明の課題は、複数の熱源ユニットを備える空気調和装置において、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上することにある。   The subject of this invention is improving the precision which judges the refrigerant | coolant amount with which the refrigerant circuit is filled when an refrigerant | coolant circuit is filled with a refrigerant | coolant in an air conditioning apparatus provided with a several heat-source unit.

第１発明に係る空気調和装置は、第１熱源ユニットと、第２熱源ユニットと、第１判定部と、第２判定部と、制御部とを備えている。第１熱源ユニットは、第１熱源側熱交換器と第１熱源側過冷却度調節手段とを含んでいる。第１熱源側熱交換器は少なくとも凝縮器として機能し、第１熱源側過冷却度調節手段は第１熱源側熱交換器の出口側における第１過冷却度を調節する。第２熱源ユニットは、第２熱源側熱交換器と第２熱源側過冷却度調節手段とを含んでいる。第２熱源側熱交換器は少なくとも凝縮器として機能し、第２熱源側過冷却度調節手段は第２熱源側熱交換器の出口側における第２過冷却度を調節する。第１判定部は、第１過冷却度を判定する。第２判定部は、第２過冷却度を判定する。制御部は、第１熱源側熱交換器と第２熱源側熱交換器とを有する冷媒回路に冷媒が充填されるときに、第１過冷却度と第２過冷却度との差が小さくなるように第１熱源側過冷却度調節手段および第２熱源側過冷却度調節手段を制御する。また、制御部は、第１過冷却度および第２過冷却度のいずれか一方に基づいて、冷媒回路内の冷媒量を判断する。第１熱源側過冷却度調節手段は、冷媒回路を流れる冷媒を圧縮する第１圧縮機である。また、第２熱源側過冷却度調節手段は、冷媒回路を流れる冷媒を圧縮する第２圧縮機である。さらに、制御部は、第１過冷却度が第２過冷却度よりも大きいときに、第２圧縮機の回転数が第１圧縮機の回転数よりも小さくなるように、第１圧縮機および第２圧縮機を制御する。また、制御部は、第１過冷却度が第２過冷却度よりも小さいときに、第１圧縮機の回転数が第２圧縮機の回転数よりも小さくなるように、第１圧縮機および第２圧縮機を制御する。   The air conditioning apparatus according to the first aspect of the present invention includes a first heat source unit, a second heat source unit, a first determination unit, a second determination unit, and a control unit. The first heat source unit includes a first heat source side heat exchanger and a first heat source side subcooling degree adjusting means. The first heat source side heat exchanger functions as at least a condenser, and the first heat source side subcooling degree adjusting means adjusts the first subcooling degree on the outlet side of the first heat source side heat exchanger. The second heat source unit includes a second heat source side heat exchanger and a second heat source side subcooling degree adjusting means. The second heat source side heat exchanger functions as at least a condenser, and the second heat source side subcooling degree adjusting means adjusts the second subcooling degree on the outlet side of the second heat source side heat exchanger. The first determination unit determines the first degree of supercooling. The second determination unit determines the second degree of supercooling. When the refrigerant is filled in the refrigerant circuit having the first heat source side heat exchanger and the second heat source side heat exchanger, the control unit reduces the difference between the first supercooling degree and the second supercooling degree. Thus, the first heat source side subcooling degree adjusting means and the second heat source side subcooling degree adjusting means are controlled. Further, the control unit determines the amount of refrigerant in the refrigerant circuit based on one of the first subcooling degree and the second subcooling degree. The first heat source side subcooling degree adjusting means is a first compressor that compresses the refrigerant flowing through the refrigerant circuit. The second heat source side supercooling degree adjusting means is a second compressor that compresses the refrigerant flowing through the refrigerant circuit. Further, the control unit includes the first compressor and the first compressor so that the rotation speed of the second compressor is smaller than the rotation speed of the first compressor when the first subcooling degree is larger than the second subcooling degree. Control the second compressor. In addition, the control unit includes the first compressor and the first compressor and the second compressor so that the rotational speed of the first compressor is smaller than the rotational speed of the second compressor when the first supercooling degree is smaller than the second supercooling degree. Control the second compressor.

第１発明に係る空気調和装置では、制御部は、第１過冷却度および第２過冷却度に基づいて、第１圧縮機および第２圧縮機の回転数を調節する。例えば、第１過冷却度が第２過冷却度よりも大きい場合、過冷却度の小さい第２圧縮機の回転数を第１圧縮機の回転数よりも小さくすることで、第１熱源側熱交換器を流れる冷媒量と第２熱源側熱交換器を流れる冷媒の流量との差を小さくすることができる。このため、第１熱源側熱交換器および第２熱源側熱交換器において冷媒の偏流を発生させ難くすることができる。   In the air conditioning apparatus according to the first aspect, the control unit adjusts the rotation speeds of the first compressor and the second compressor based on the first subcooling degree and the second subcooling degree. For example, when the first supercooling degree is larger than the second supercooling degree, the first heat source side heat is obtained by making the rotation speed of the second compressor having a small supercooling degree smaller than the rotation speed of the first compressor. The difference between the amount of refrigerant flowing through the exchanger and the flow rate of refrigerant flowing through the second heat source side heat exchanger can be reduced. For this reason, it is possible to make it difficult to generate refrigerant drift in the first heat source side heat exchanger and the second heat source side heat exchanger.

これによって、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上させることができる。   Thereby, when the refrigerant is filled in the refrigerant circuit, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit.

また、この空気調和装置では、簡易な構成によって冷媒の偏流を発生させ難くすることができる。   Further, in this air conditioner, it is possible to make it difficult for refrigerant drift to occur with a simple configuration.

さらに、制御部は、第１過冷却度および第２過冷却度のいずれか一方に基づいて冷媒回路内の冷媒量を判断する。この空気調和装置では、制御部によって第１熱源側熱交換器と第２熱源側熱交換器とを流れる冷媒量の差が小さくなるように制御されているため、第１過冷却度と第２過冷却度との差は小さくなっている。したがって、配備されているどちらの熱源側熱交換器の出口における過冷却度からも冷媒回路に充填されている冷媒量を判断することができる。   Furthermore, the control unit determines the amount of refrigerant in the refrigerant circuit based on one of the first subcooling degree and the second subcooling degree. In this air conditioner, since the controller controls the difference in the amount of refrigerant flowing through the first heat source side heat exchanger and the second heat source side heat exchanger, the first supercooling degree and the second The difference from the degree of supercooling is small. Therefore, the amount of refrigerant filled in the refrigerant circuit can be determined from the degree of supercooling at the outlet of either of the heat source side heat exchangers provided.

なお、ここでいう、第１過冷却度と第２過冷却度との差が小さくなるというのは、第１過冷却度と第２過冷却度との差が所定の値以下になった場合でも、第１過冷却度および第２過冷却度とが一致した場合でもよい。   Note that the difference between the first and second subcooling degrees here is small when the difference between the first and second subcooling degrees is below a predetermined value. However, the case where the 1st supercooling degree and the 2nd supercooling degree correspond may be sufficient.

第２発明に係る空気調和装置は、第１熱源ユニットと、第２熱源ユニットと、第１判定部と、第２判定部と、制御部とを備えている。第１熱源ユニットは、第１熱源側熱交換器と第１熱源側過冷却度調節手段とを含んでいる。第１熱源側熱交換器は少なくとも凝縮器として機能し、第１熱源側過冷却度調節手段は第１熱源側熱交換器の出口側における第１過冷却度を調節する。第２熱源ユニットは、第２熱源側熱交換器と第２熱源側過冷却度調節手段とを含んでいる。第２熱源側熱交換器は少なくとも凝縮器として機能し、第２熱源側過冷却度調節手段は第２熱源側熱交換器の出口側における第２過冷却度を調節する。第１判定部は、第１過冷却度を判定する。第２判定部は、第２過冷却度を判定する。制御部は、第１熱源側熱交換器と第２熱源側熱交換器とを有する冷媒回路に冷媒が充填されるときに、第１過冷却度と第２過冷却度との差が小さくなるように第１熱源側過冷却度調節手段および第２熱源側過冷却度調節手段を制御する。また、制御部は、第１過冷却度および第２過冷却度のいずれか一方に基づいて、冷媒回路内の冷媒量を判断する。第１熱源側過冷却度調節手段は、第１熱源側熱交換器に空気を送る第１熱源側ファンである。また、第２熱源側過冷却度調節手段は、第２熱源側熱交換器に空気を送る第２熱源側ファンである。さらに、制御部は、第１過冷却度が第２過冷却度よりも大きいときに、第２熱源側ファンの回転数が第１熱源側ファンの回転数よりも大きくなるように、第１熱源側ファンおよび第２熱源側ファンを制御する。また、制御部は、第１過冷却度が第２過冷却度よりも小さいときに、第１熱源側ファンの回転数が第２熱源側ファンの回転数よりも大きくなるように、第１熱源側ファンおよび第２熱源側ファンを制御する。   An air conditioner according to a second aspect of the present invention includes a first heat source unit, a second heat source unit, a first determination unit, a second determination unit, and a control unit. The first heat source unit includes a first heat source side heat exchanger and a first heat source side subcooling degree adjusting means. The first heat source side heat exchanger functions as at least a condenser, and the first heat source side subcooling degree adjusting means adjusts the first subcooling degree on the outlet side of the first heat source side heat exchanger. The second heat source unit includes a second heat source side heat exchanger and a second heat source side subcooling degree adjusting means. The second heat source side heat exchanger functions as at least a condenser, and the second heat source side subcooling degree adjusting means adjusts the second subcooling degree on the outlet side of the second heat source side heat exchanger. The first determination unit determines the first degree of supercooling. The second determination unit determines the second degree of supercooling. When the refrigerant is filled in the refrigerant circuit having the first heat source side heat exchanger and the second heat source side heat exchanger, the control unit reduces the difference between the first supercooling degree and the second supercooling degree. Thus, the first heat source side subcooling degree adjusting means and the second heat source side subcooling degree adjusting means are controlled. Further, the control unit determines the amount of refrigerant in the refrigerant circuit based on one of the first subcooling degree and the second subcooling degree. The first heat source side subcooling degree adjusting means is a first heat source side fan that sends air to the first heat source side heat exchanger. The second heat source side subcooling degree adjusting means is a second heat source side fan that sends air to the second heat source side heat exchanger. Further, the control unit may control the first heat source so that when the first subcooling degree is larger than the second subcooling degree, the rotational speed of the second heat source side fan is larger than the rotational speed of the first heat source side fan. The side fan and the second heat source side fan are controlled. In addition, the controller may control the first heat source so that when the first supercooling degree is smaller than the second supercooling degree, the rotational speed of the first heat source side fan is larger than the rotational speed of the second heat source side fan. The side fan and the second heat source side fan are controlled.

第２発明に係る空気調和装置では、制御部は、第１過冷却度および第２過冷却度に基づいて、第１熱源側ファンおよび第２熱源側ファンの回転数を調節する。例えば、第１過冷却度が第２過冷却度よりも大きい場合、第２熱源側ファンの回転数を第１熱源側ファンの回転数よりも大きくすることで、第１過冷却度と第２過冷却度との差を小さくすることができる。   In the air conditioner according to the second aspect of the present invention, the control unit adjusts the rotational speeds of the first heat source side fan and the second heat source side fan based on the first subcooling degree and the second subcooling degree. For example, when the first supercooling degree is larger than the second supercooling degree, the first supercooling degree and the second supercooling degree are increased by setting the rotational speed of the second heat source side fan higher than the rotational speed of the first heat source side fan. The difference from the degree of supercooling can be reduced.

これによって、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上させることができる。   Thereby, when the refrigerant is filled in the refrigerant circuit, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit.

また、制御部は、第１過冷却度および第２過冷却度のいずれか一方に基づいて冷媒回路内の冷媒量を判断する。この空気調和装置では、制御部によって第１熱源側熱交換器と第２熱源側熱交換器とを流れる冷媒量の差が小さくなるように制御されているため、第１過冷却度と第２過冷却度との差は小さくなっている。したがって、配備されているどちらの熱源側熱交換器の出口における過冷却度からも冷媒回路に充填されている冷媒量を判断することができる。   Further, the control unit determines the amount of refrigerant in the refrigerant circuit based on one of the first supercooling degree and the second supercooling degree. In this air conditioner, since the controller controls the difference in the amount of refrigerant flowing through the first heat source side heat exchanger and the second heat source side heat exchanger, the first supercooling degree and the second The difference from the degree of supercooling is small. Therefore, the amount of refrigerant filled in the refrigerant circuit can be determined from the degree of supercooling at the outlet of either of the heat source side heat exchangers provided.

なお、ここでいう、第１過冷却度と第２過冷却度との差が小さくなるというのは、第１過冷却度と第２過冷却度との差が所定の値以下になった場合でも、第１過冷却度および第２過冷却度とが一致した場合でもよい。   Note that the difference between the first and second subcooling degrees here is small when the difference between the first and second subcooling degrees is below a predetermined value. However, the case where the 1st supercooling degree and the 2nd supercooling degree correspond may be sufficient.

第１発明に係る空気調和装置では、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上させることができる。   In the air conditioner according to the first aspect of the present invention, when the refrigerant is charged into the refrigerant circuit, it is possible to improve the accuracy of determining the amount of refrigerant charged in the refrigerant circuit.

第２発明に係る空気調和装置では、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上させることができる。   In the air conditioning apparatus according to the second aspect of the present invention, when the refrigerant is charged into the refrigerant circuit, it is possible to improve the accuracy of determining the amount of refrigerant charged in the refrigerant circuit.

本発明の一実施形態に係る空気調和装置１００の概略の冷媒回路を図１に示す。空気調和装置１００は、蒸気圧縮式の冷凍サイクル運転を行うことによって、ビル等の屋内の冷暖房に使用される装置である。この空気調和装置１００は、主として、２台の室外ユニット１ａ，１ｂと、室外ユニット１ａ，１ｂに並列に接続された３台の室内ユニット２ａ，２ｂ，２ｃと、室外ユニット１ａ，１ｂと室内ユニット２ａ，２ｂ，２ｃとを接続する冷媒連絡配管とを備えている。また、冷媒連絡配管は液冷媒連絡配管１１およびガス冷媒連絡配管１２から構成される。具体的には、液冷媒連絡配管１１およびガス冷媒連絡配管１２は、室外ユニット１ａ，１ｂの有する室外側冷媒回路１４ａ，１４ｂと室内ユニット２ａ，２ｂ，２ｃの有する室内側冷媒回路１３ａ，１３ｂ，１３ｃとに接続されている。すなわち、この空気調和装置１００の冷媒回路１０は、室外側冷媒回路１４ａ，１４ｂと室内側冷媒回路１３ａ，１３ｂ，１３ｃと液冷媒連絡配管１１とガス冷媒連絡配管１２とが接続されることによって構成されている。また、冷媒回路１０において、凝縮器として機能する熱交換器から蒸発器として機能する熱交換器に向かって流れる冷媒が通る配管を液冷媒配管１５といい、蒸発器として機能する熱交換器から凝縮器として機能する熱交換器に向かって流れる冷媒が通る配管をガス冷媒配管１６という。以下、後述する冷媒回路１０に配備されている各種機器において、液冷媒配管１５に接続されている側を各種機器の液側と、ガス冷媒配管１６に接続されている側を各種機器のガス側という。   FIG. 1 shows a schematic refrigerant circuit of an air conditioner 100 according to an embodiment of the present invention. The air conditioner 100 is an apparatus used for indoor air conditioning such as a building by performing a vapor compression refrigeration cycle operation. This air conditioner 100 mainly includes two outdoor units 1a, 1b, three indoor units 2a, 2b, 2c connected in parallel to the outdoor units 1a, 1b, outdoor units 1a, 1b, and indoor units. 2a, 2b, and 2c are connected to the refrigerant communication pipe. The refrigerant communication pipe is composed of a liquid refrigerant communication pipe 11 and a gas refrigerant communication pipe 12. Specifically, the liquid refrigerant communication pipe 11 and the gas refrigerant communication pipe 12 include the outdoor refrigerant circuits 14a and 14b included in the outdoor units 1a and 1b and the indoor refrigerant circuits 13a and 13b included in the indoor units 2a, 2b, and 2c, 13c. That is, the refrigerant circuit 10 of the air conditioner 100 is configured by connecting the outdoor refrigerant circuits 14a and 14b, the indoor refrigerant circuits 13a, 13b, and 13c, the liquid refrigerant communication pipe 11, and the gas refrigerant communication pipe 12. Has been. In the refrigerant circuit 10, a pipe through which the refrigerant flowing from the heat exchanger functioning as a condenser toward the heat exchanger functioning as an evaporator is referred to as a liquid refrigerant pipe 15, and is condensed from the heat exchanger functioning as an evaporator. A pipe through which the refrigerant flowing toward the heat exchanger functioning as a vessel passes is referred to as a gas refrigerant pipe 16. Hereinafter, in various devices provided in the refrigerant circuit 10 to be described later, the side connected to the liquid refrigerant pipe 15 is the liquid side of the various devices, and the side connected to the gas refrigerant pipe 16 is the gas side of the various devices. That's it.

〔室内ユニット〕
第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃは、ビル等の屋内の天井に埋め込みや吊り下げ等により、又は、屋内の壁面に壁掛け等により設置されている。第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃは、液冷媒連絡配管１１およびガス冷媒連絡配管１２を介して第１室外ユニット１ａおよび第２室外ユニット１ｂに接続されており、冷媒回路１０の一部を構成している。 [Indoor unit]
The first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c are installed by being embedded or suspended in an indoor ceiling of a building or the like, or mounted on a wall surface of the indoor wall. The first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c are connected to the first outdoor unit 1a and the second outdoor unit 1b via the liquid refrigerant communication pipe 11 and the gas refrigerant communication pipe 12, respectively. A part of the refrigerant circuit 10 is configured.

次に、第１室内ユニット２ａの構成について説明する。なお、第１室内ユニット２ａと、第２室内ユニット２ｂおよび第３室内ユニット２ｃとは、同様の構成であるため、ここでは、第１室内ユニット２ａの構成のみ説明する。   Next, the configuration of the first indoor unit 2a will be described. Since the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c have the same configuration, only the configuration of the first indoor unit 2a will be described here.

第１室内ユニット２ａは、主として、第１室内膨張弁５ａと、第１室内熱交換器６ａと、第１室内熱交液側温度センサ２０ａと、第１室内熱交ガス側温度センサ２１ａと、第１室内熱交温度センサ２６ａとを備えている。なお、第１室内膨張弁５ａと第１室内熱交換器６ａとが冷媒配管によって接続されることで、冷媒回路１０の一部である第１室内側冷媒回路１３ａが構成されている。   The first indoor unit 2a mainly includes a first indoor expansion valve 5a, a first indoor heat exchanger 6a, a first indoor heat exchange liquid side temperature sensor 20a, a first indoor heat exchange gas side temperature sensor 21a, And a first indoor heat exchanger temperature sensor 26a. In addition, the 1st indoor side refrigerant circuit 13a which is a part of the refrigerant circuit 10 is comprised by connecting the 1st indoor expansion valve 5a and the 1st indoor heat exchanger 6a by refrigerant | coolant piping.

第１室内膨張弁５ａは、第１室内側冷媒回路１３ａ内を流れる冷媒の流量の調節等を行うために、第１室内熱交換器６ａの液側に接続された電動膨張弁である。   The first indoor expansion valve 5a is an electric expansion valve connected to the liquid side of the first indoor heat exchanger 6a in order to adjust the flow rate of the refrigerant flowing in the first indoor-side refrigerant circuit 13a.

第１室内熱交換器６ａは、伝熱管と多数のフィンとにより構成されたクロスフィン式のフィン・アンド・チューブ型熱交換器である。また、第１室内熱交換器６ａは、冷房運転時には冷媒の蒸発器として機能して室内の空気を冷却し、暖房運転時には冷媒の凝縮器として機能して室内の空気を加熱する。   The first indoor heat exchanger 6a is a cross-fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins. The first indoor heat exchanger 6a functions as a refrigerant evaporator during cooling operation to cool indoor air, and functions as a refrigerant condenser during heating operation to heat indoor air.

第１室内熱交液側温度センサ２０ａは、第１室内熱交換器６ａの液側に設けられており、液状態又は気液二相状態の冷媒の温度を検出する。第１室内熱交ガス側温度センサ２１ａは、第１室内熱交換器６ａのガス側に設けられており、ガス状態又は気液二相状態の冷媒の温度を検出する。第１室内熱交温度センサ２６ａは、第１室内熱交換器６ａに設けられており、第１室内熱交換器６ａ内を流れる冷媒の温度を検出する。また、本実施形態において、第１室内熱交液側温度センサ２０ａ、第１室内熱交ガス側温度センサ２１ａおよび第１室内熱交温度センサ２６ａは、サーミスタからなる。   The first indoor heat exchange liquid side temperature sensor 20a is provided on the liquid side of the first indoor heat exchanger 6a, and detects the temperature of the refrigerant in the liquid state or the gas-liquid two-phase state. The first indoor heat exchange gas side temperature sensor 21a is provided on the gas side of the first indoor heat exchanger 6a, and detects the temperature of the refrigerant in the gas state or the gas-liquid two-phase state. The first indoor heat exchange temperature sensor 26a is provided in the first indoor heat exchanger 6a and detects the temperature of the refrigerant flowing in the first indoor heat exchanger 6a. In the present embodiment, the first indoor heat exchange liquid side temperature sensor 20a, the first indoor heat exchange gas side temperature sensor 21a, and the first indoor heat exchange temperature sensor 26a are composed of thermistors.

また、第１室内ユニット２ａは、図２に示すように、第１室内ユニット２ａの各種機器および弁を制御する第１室内側制御部６７ａを備えている。第１室内側制御部６７ａは、第１室内側判定部６５ａと第１室内側開度調節部６１ａとを有している。第１室内側判定部６５ａは、第１室内熱交液側温度センサ２０ａ、第１室内熱交ガス側温度センサ２１ａおよび第１室内熱交温度センサ２６ａによって検知された冷媒の温度に基づいて、第１室内熱交換器６ａが、蒸発器として機能する場合は過熱度を、凝縮器として機能する場合は過冷却度を、それぞれ算出する。第１室内側開度調節部６１ａは、第１室内側判定部６５ａが算出した過熱度または過冷却度に基づいて、第１室内膨張弁５ａの開度を調節する。さらに、第１室内側制御部６７ａは、第１室内ユニット２ａの制御を行うために設けられたマイクロコンピュータやメモリ等を有しており、第１室内ユニット２ａを個別に操作するためのリモコン（図示せず）との間で制御信号等のやりとりを行ったり、第１室外ユニット１ａおよび第２室外ユニット１ｂとの間で制御信号等のやりとりを行ったりすることができる。   Moreover, the 1st indoor unit 2a is provided with the 1st indoor side control part 67a which controls the various apparatus and valve | bulb of the 1st indoor unit 2a, as shown in FIG. The 1st indoor side control part 67a has the 1st indoor side determination part 65a and the 1st indoor side opening degree adjustment part 61a. The first indoor side determination unit 65a is based on the temperature of the refrigerant detected by the first indoor heat exchange liquid side temperature sensor 20a, the first indoor heat exchange gas side temperature sensor 21a, and the first indoor heat exchange temperature sensor 26a. When the first indoor heat exchanger 6a functions as an evaporator, the degree of superheat is calculated, and when the first indoor heat exchanger 6a functions as a condenser, the degree of supercooling is calculated. The first indoor side opening degree adjustment unit 61a adjusts the opening degree of the first indoor expansion valve 5a based on the degree of superheat or the degree of supercooling calculated by the first room side determination unit 65a. Further, the first indoor side control unit 67a has a microcomputer, a memory, and the like provided for controlling the first indoor unit 2a, and a remote controller for individually operating the first indoor unit 2a ( A control signal and the like can be exchanged with a first outdoor unit 1a and a second outdoor unit 1b.

〔室外ユニット〕
第１室外ユニット１ａおよび第２室外ユニット１ｂは、ビル等の屋上等に設置されており、液冷媒連絡配管１１およびガス冷媒連絡配管１２を介して第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃに接続されている。 [Outdoor unit]
The first outdoor unit 1a and the second outdoor unit 1b are installed on the rooftop of a building or the like, and the first indoor unit 2a, the second indoor unit 2b, and the like through the liquid refrigerant communication pipe 11 and the gas refrigerant communication pipe 12 It is connected to the third indoor unit 2c.

次に、第１室外ユニット１ａの構成について説明する。なお、第１室外ユニット１ａと第２室外ユニット１ｂとは、同様の構成であるため、ここでは、第１室外ユニット１ａの構成のみ説明する。   Next, the configuration of the first outdoor unit 1a will be described. In addition, since the 1st outdoor unit 1a and the 2nd outdoor unit 1b are the same structures, only the structure of the 1st outdoor unit 1a is demonstrated here.

第１室外ユニット１ａは、主として、第１圧縮機８ａと、第１四路切換弁７ａと、第１室外熱交換器４ａと、第１室外膨張弁３ａと、第１室外ファン９ａと、第１液側閉鎖弁２４ａと、第１ガス側閉鎖弁２５ａと、第１室外熱交温度センサ２２ａと、第１室外熱交液側温度センサ２３ａとを備えている。また、第１室外ユニット１ａでは、第１圧縮機８ａと、第１四路切換弁７ａと、第１室外熱交換器４ａと、第１室外膨張弁３ａと、第１液側閉鎖弁２４ａと、第１ガス側閉鎖弁２５ａとが接続されることによって、冷媒回路１０の一部である第１室外側冷媒回路１４ａが構成されている。   The first outdoor unit 1a mainly includes a first compressor 8a, a first four-way switching valve 7a, a first outdoor heat exchanger 4a, a first outdoor expansion valve 3a, a first outdoor fan 9a, 1 liquid side closing valve 24a, the 1st gas side closing valve 25a, the 1st outdoor heat exchange liquid temperature sensor 22a, and the 1st outdoor heat exchange liquid side temperature sensor 23a are provided. In the first outdoor unit 1a, the first compressor 8a, the first four-way switching valve 7a, the first outdoor heat exchanger 4a, the first outdoor expansion valve 3a, and the first liquid side closing valve 24a are provided. The first outdoor side refrigerant circuit 14a which is a part of the refrigerant circuit 10 is configured by connecting the first gas side shut-off valve 25a.

第１圧縮機８ａは、吸入側から吸入された低圧のガス冷媒を圧縮し、この圧縮された高圧のガス冷媒を吐出側に吐出する装置である。また、第１圧縮機８ａは、運転容量を可変することが可能な圧縮機であり、インバータにより制御されるモータによって駆動される。   The first compressor 8a is a device that compresses the low-pressure gas refrigerant sucked from the suction side and discharges the compressed high-pressure gas refrigerant to the discharge side. The first compressor 8a is a compressor whose operating capacity can be varied, and is driven by a motor controlled by an inverter.

第１四路切換弁７ａは、冷媒の流れの方向を切り換えるための弁であり、冷房運転時および冷媒充填運転時には、第１圧縮機８ａの吐出側と第１室外熱交換器４ａのガス側とを接続するとともに第１圧縮機８ａの吸入側とガス冷媒連絡配管１２とを接続する（図１の第１四路切換弁７ａの実線を参照）。したがって、冷房運転時および冷媒充填運転時には、第１室外熱交換器４ａは第１圧縮機８ａにおいて圧縮される冷媒の凝縮器として機能し、かつ、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃは第１室外熱交換器４ａにおいて凝縮される冷媒の蒸発器として機能する。また、第１四路切換弁７ａは、暖房運転時には、第１圧縮機８ａの吐出側とガス冷媒連絡配管１２側とを接続するとともに第１圧縮機８ａの吸入側と第１室外熱交換器４ａのガス側とを接続する（図１の第１四路切換弁７ａの破線を参照）。したがって、暖房運転時には、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃは第１圧縮機８ａにおいて圧縮される冷媒の凝縮器として機能し、かつ、第１室外熱交換器４ａは第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃにおいて凝縮される冷媒の蒸発器として機能する。   The first four-way switching valve 7a is a valve for switching the direction of the refrigerant flow. During the cooling operation and the refrigerant charging operation, the discharge side of the first compressor 8a and the gas side of the first outdoor heat exchanger 4a Are connected to the suction side of the first compressor 8a and the gas refrigerant communication pipe 12 (see the solid line of the first four-way switching valve 7a in FIG. 1). Therefore, during the cooling operation and the refrigerant charging operation, the first outdoor heat exchanger 4a functions as a refrigerant condenser compressed in the first compressor 8a, and the first indoor heat exchanger 6a and the second indoor heat The exchanger 6b and the third indoor heat exchanger 6c function as a refrigerant evaporator that is condensed in the first outdoor heat exchanger 4a. The first four-way switching valve 7a connects the discharge side of the first compressor 8a and the gas refrigerant communication pipe 12 side during heating operation, and also connects the suction side of the first compressor 8a and the first outdoor heat exchanger. 4a is connected to the gas side (see the broken line of the first four-way selector valve 7a in FIG. 1). Therefore, during the heating operation, the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c function as a condenser for the refrigerant compressed in the first compressor 8a, and The one outdoor heat exchanger 4a functions as an evaporator for refrigerant condensed in the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c.

第１室外熱交換器４ａは、伝熱管と多数のフィンとにより構成されたクロスフィン式のフィン・アンド・チューブ型熱交換器であり、冷房運転時には冷媒の凝縮器として機能し、暖房運転時には冷媒の蒸発器として機能する。第１室外熱交換器４ａは、そのガス側が第１四路切換弁７ａに接続され、その液側が第１室外膨張弁３ａに接続されている。   The first outdoor heat exchanger 4a is a cross fin type fin-and-tube heat exchanger composed of heat transfer tubes and a large number of fins, and functions as a refrigerant condenser during cooling operation and during heating operation. It functions as a refrigerant evaporator. The gas side of the first outdoor heat exchanger 4a is connected to the first four-way switching valve 7a, and the liquid side thereof is connected to the first outdoor expansion valve 3a.

第１室外膨張弁３ａは、第１室外側冷媒回路１４ａ内を流れる冷媒の流量の調節等を行うために、第１室外熱交換器４ａの液側に接続された電動膨張弁である。   The first outdoor expansion valve 3a is an electric expansion valve connected to the liquid side of the first outdoor heat exchanger 4a in order to adjust the flow rate of the refrigerant flowing in the first outdoor refrigerant circuit 14a.

第１室外ファン９ａは、第１室外熱交換器４ａに室外空気を供給するために、第１室外熱交換器４ａ近傍に配置されるプロペラファンである。   The first outdoor fan 9a is a propeller fan disposed near the first outdoor heat exchanger 4a in order to supply outdoor air to the first outdoor heat exchanger 4a.

第１液側閉鎖弁２４ａは、液冷媒連絡配管１１と第１室外ユニット１ａとの接続口に設けられている弁である。また、第１ガス側閉鎖弁２５ａは、ガス冷媒連絡配管１２と第１室外ユニット１ａとの接続口に設けられた弁である。第１液側閉鎖弁２４ａは、第１室外膨張弁３ａに接続されている。第１ガス側閉鎖弁２５ａは、第１四路切換弁７ａに接続されている。   The first liquid side shut-off valve 24a is a valve provided at a connection port between the liquid refrigerant communication pipe 11 and the first outdoor unit 1a. Moreover, the 1st gas side closing valve 25a is a valve provided in the connection port of the gas refrigerant communication piping 12 and the 1st outdoor unit 1a. The first liquid side closing valve 24a is connected to the first outdoor expansion valve 3a. The first gas side closing valve 25a is connected to the first four-way switching valve 7a.

第１室外熱交温度センサ２２ａは、第１室外熱交換器４ａに設けられており、第１室外熱交換器４ａ内を流れる冷媒の温度を検出する。第１室外熱交液側温度センサ２３ａは、第１室外熱交換器４ａの液側に設けられており、液状または気液二相状態の冷媒の温度を検出する。なお、本実施形態において、第１室外熱交温度センサ２２ａおよび第１室外熱交液側温度センサ２３ａは、サーミスタからなる。   The first outdoor heat exchange temperature sensor 22a is provided in the first outdoor heat exchanger 4a, and detects the temperature of the refrigerant flowing in the first outdoor heat exchanger 4a. The first outdoor heat exchange liquid side temperature sensor 23a is provided on the liquid side of the first outdoor heat exchanger 4a, and detects the temperature of the refrigerant in a liquid or gas-liquid two-phase state. In the present embodiment, the first outdoor heat exchange temperature sensor 22a and the first outdoor heat exchange liquid side temperature sensor 23a are composed of thermistors.

また、第１室外ユニット１ａは、図２に示すように、第１室外ユニット１ａの各種機器および弁を制御する第１室外側制御部６８ａを備えている。第１室外側制御部６８ａは、第１室外側判定部６２ａと第１室外側開度調節部６４ａとを有している。第１室外側判定部６２ａは、第１室外熱交温度センサ２２ａおよび第１室外熱交液側温度センサ２３ａに接続されており、第１室外熱交温度センサ２２ａおよび第１室外熱交液側温度センサ２３ａによって検知された冷媒の温度に基づいて、凝縮器として機能する第１室外熱交換器４ａの液側における過冷却度を算出する。第１室外側開度調節部６４ａは、室外側判定部６２ａ，６２ｂによって算出された過冷却度のうちの最も大きい過冷却度が算出された室外熱交換器を有する室外ユニットを非対象ユニットに設定し、非対象ユニット以外の室外ユニットを対象ユニットに設定する。また、第１室外側開度調節部６４ａは、第１室外膨張弁３ａに接続されており、第１室外側判定部６２ａが算出した過冷却度に基づいて、第１室外膨張弁３ａの開度を調節する。さらに、第１室外側制御部６８ａは、非対象ユニットの過冷却度と冷媒充填完了の目標値として設定されている所定値との比較を行い、さらに、対象ユニットと非対象ユニットとの比較を行う。また、第１室外側制御部６８ａは、第１室外ユニット１ａの制御を行うために設けられたマイクロコンピュータ、メモリやモータを制御するインバータ回路等を有しており、第１室内側制御部６７ａ、第２室内側制御部６７ｂおよび第３室内側制御部６７ｃとの間で制御信号等のやりとりを行うことができる。   Moreover, the 1st outdoor unit 1a is provided with the 1st outdoor side control part 68a which controls the various apparatus and valve | bulb of the 1st outdoor unit 1a, as shown in FIG. The 1st outdoor side control part 68a has the 1st outdoor side determination part 62a and the 1st outdoor side opening degree adjustment part 64a. The first outdoor side determination unit 62a is connected to the first outdoor heat exchange temperature sensor 22a and the first outdoor heat exchange liquid side temperature sensor 23a, and the first outdoor heat exchange temperature sensor 22a and the first outdoor heat exchange liquid side. Based on the temperature of the refrigerant detected by the temperature sensor 23a, the degree of supercooling on the liquid side of the first outdoor heat exchanger 4a that functions as a condenser is calculated. The 1st outdoor side opening degree adjustment part 64a makes the non-target unit the outdoor unit which has the outdoor heat exchanger by which the largest supercooling degree was calculated among the supercooling degrees calculated by the outdoor side determination parts 62a and 62b. Set and set outdoor units other than non-target units as target units. The first outdoor opening degree adjusting unit 64a is connected to the first outdoor expansion valve 3a, and the first outdoor expansion valve 3a is opened based on the degree of supercooling calculated by the first outdoor side determination unit 62a. Adjust the degree. Further, the first outdoor side control unit 68a compares the degree of supercooling of the non-target unit with a predetermined value set as the target value for completion of refrigerant filling, and further compares the target unit with the non-target unit. Do. The first outdoor control unit 68a includes a microcomputer provided for controlling the first outdoor unit 1a, an inverter circuit for controlling a memory, a motor, and the like, and a first indoor control unit 67a. Control signals and the like can be exchanged between the second indoor side control unit 67b and the third indoor side control unit 67c.

以上のように、第１室内側冷媒回路１３ａ、第２室内側冷媒回路１３ｂおよび第３室内側冷媒回路１３ｃと第１室外側冷媒回路１４ａおよび第２室外側冷媒回路１４ｂとが冷媒連絡配管によって接続されることで、空気調和装置１００の冷媒回路１０が構成されている。また、図２に示すように、第１室内側制御部６７ａ、第２室内側制御部６７ｂ、第３室内側制御部６７ｃ、第１室外側制御部６８ａおよび第２室外側制御部６８ｂによって主制御部６０が構成されている。また、主制御部６０は、第１四路切換弁７ａ、第２四路切換弁７ｂ、第１圧縮機８ａおよび第２圧縮機８ｂを制御することができるように、これらに接続されている。主制御部６０は、第１四路切換弁７ａおよび第２四路切換弁７ｂを切り換えることで冷房運転と暖房運転とを行うとともに、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃの運転負荷に応じて、第１室外ユニット１ａの第１圧縮機８ａおよび第２室外ユニット１ｂの第２圧縮機８ｂ等の各機器の制御を行うようになっている。これによって、主制御部６０は空気調和装置１００全体の運転制御を行うことができる。   As described above, the first indoor-side refrigerant circuit 13a, the second indoor-side refrigerant circuit 13b, the third indoor-side refrigerant circuit 13c, the first outdoor-side refrigerant circuit 14a, and the second outdoor-side refrigerant circuit 14b are connected by the refrigerant communication pipe. By being connected, the refrigerant circuit 10 of the air conditioning apparatus 100 is configured. Further, as shown in FIG. 2, the first indoor side control unit 67a, the second indoor side control unit 67b, the third indoor side control unit 67c, the first outdoor side control unit 68a, and the second outdoor side control unit 68b are used. A control unit 60 is configured. The main controller 60 is connected to the first four-way switching valve 7a, the second four-way switching valve 7b, the first compressor 8a, and the second compressor 8b so as to control them. . The main controller 60 performs the cooling operation and the heating operation by switching the first four-way switching valve 7a and the second four-way switching valve 7b, and the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit. In accordance with the operation load of the unit 2c, each device such as the first compressor 8a of the first outdoor unit 1a and the second compressor 8b of the second outdoor unit 1b is controlled. Accordingly, the main control unit 60 can perform operation control of the entire air conditioner 100.

＜空気調和装置の動作＞
次に、本実施形態の空気調和装置１００の動作について説明する。 <Operation of air conditioner>
Next, operation | movement of the air conditioning apparatus 100 of this embodiment is demonstrated.

本実施形態の空気調和装置１００の運転モードとしては、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃの運転負荷に応じて第１室外ユニット１ａ、第２室外ユニット１ｂ、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃの有する各種機器の制御を行う通常運転モードと、空気調和装置１００の設置後に行われる冷媒回路１０への冷媒充填を行うための冷媒充填運転モードとがある。そして、通常運転モードには、主として、冷房運転と暖房運転とが含まれている。   As the operation mode of the air conditioner 100 of the present embodiment, the first outdoor unit 1a, the second outdoor unit 1b, the first outdoor unit 1a, the second indoor unit 2b, and the third indoor unit 2c are operated according to the operating loads. A normal operation mode for controlling various devices included in the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c, and a refrigerant for charging the refrigerant into the refrigerant circuit 10 performed after the air conditioner 100 is installed. There is a filling operation mode. The normal operation mode mainly includes a cooling operation and a heating operation.

以下、空気調和装置１００の各運転モードにおける動作について説明する。   Hereinafter, the operation | movement in each operation mode of the air conditioning apparatus 100 is demonstrated.

〔通常運転モード〕
まず、通常運転モードにおける冷房運転について、図１を用いて説明する。 [Normal operation mode]
First, the cooling operation in the normal operation mode will be described with reference to FIG.

冷房運転は、第１四路切換弁７ａおよび第２四路切換弁７ｂが図１の実線で示される状態、すなわち、第１圧縮機８ａの吐出側が第１室外熱交換器４ａのガス側に、第２圧縮機８ｂの吐出側が第２室外熱交換器４ｂのガス側に接続され、かつ、第１圧縮機８ａおよび第２圧縮機８ｂの吸入側が第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側に接続された状態となっている。第１室外膨張弁３ａおよび第２室外膨張弁３ｂは開状態とされ、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃは第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃそれぞれのガス側における冷媒の各過熱度が所定値になるように開度調節されるようになっている。なお、本実施形態において、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側における冷媒の各過熱度は、第１室内熱交ガス側温度センサ２１ａ、第２室内熱交ガス側温度センサ２１ｂおよび第３室内熱交ガス側温度センサ２１ｃにより検出されるそれぞれの冷媒温度値から第１室内熱交液側温度センサ２０ａ、第２室内熱交液側温度センサ２０ｂおよび第３室内熱交液側温度センサ２０ｃにより検出されるそれぞれの冷媒温度を差し引くことによって検出される。   In the cooling operation, the first four-way switching valve 7a and the second four-way switching valve 7b are in the state indicated by the solid lines in FIG. 1, that is, the discharge side of the first compressor 8a is placed on the gas side of the first outdoor heat exchanger 4a. The discharge side of the second compressor 8b is connected to the gas side of the second outdoor heat exchanger 4b, and the suction sides of the first compressor 8a and the second compressor 8b are the first indoor heat exchanger 6a and the second indoor It is in the state connected to the gas side of the heat exchanger 6b and the 3rd indoor heat exchanger 6c. The first outdoor expansion valve 3a and the second outdoor expansion valve 3b are opened, and the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c are the first indoor heat exchanger 6a, second The opening degree is adjusted so that each superheat degree of the refrigerant on the gas side of each of the indoor heat exchanger 6b and the third indoor heat exchanger 6c becomes a predetermined value. In the present embodiment, the degree of superheat of the refrigerant on the gas side of the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c is the first indoor heat exchange gas side temperature sensor. 21a, the first indoor heat exchange liquid side temperature sensor 20a, the second indoor heat exchange liquid from the respective refrigerant temperature values detected by the second indoor heat exchange gas side temperature sensor 21b and the third indoor heat exchange gas side temperature sensor 21c. It is detected by subtracting the respective refrigerant temperatures detected by the side temperature sensor 20b and the third indoor heat exchange liquid temperature sensor 20c.

この冷媒回路１０の状態で第１圧縮機８ａおよび第２圧縮機８ｂを起動すると、低圧のガス冷媒は、第１圧縮機８ａおよび第２圧縮機８ｂに吸入されて圧縮され、高圧のガス冷媒となる。この高圧のガス冷媒は、第１四路切換弁７ａおよび第２四路切換弁７ｂを経由して、第１室外熱交換器４ａおよび第２室外熱交換器４ｂにそれぞれ送られる。第１室外熱交換器４ａおよび第２室外熱交換器４ｂに送られた高圧のガス冷媒は、室外空気と熱交換を行い凝縮されて高圧の液冷媒となる。   When the first compressor 8a and the second compressor 8b are started in the state of the refrigerant circuit 10, the low-pressure gas refrigerant is sucked and compressed by the first compressor 8a and the second compressor 8b, and the high-pressure gas refrigerant It becomes. The high-pressure gas refrigerant is sent to the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b via the first four-way switching valve 7a and the second four-way switching valve 7b, respectively. The high-pressure gas refrigerant sent to the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b exchanges heat with the outdoor air and is condensed to become a high-pressure liquid refrigerant.

そして、この高圧の液冷媒は、第１室外膨張弁３ａおよび第２室外膨張弁３ｂを経由して、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃにそれぞれ送られる。第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃに送られた高圧の液冷媒は、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃによって減圧されて低圧の気液二相状態の冷媒となって第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃにそれぞれ送られ、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃで室内空気と熱交換を行って蒸発されて低圧のガス冷媒となる。ここで、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃは、それぞれ、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側における各過熱度が所定値になるように第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃ内を流れる冷媒の流量をそれぞれ制御している。この低圧のガス冷媒は、ガス冷媒連絡配管１２を経由して第１室外ユニット１ａおよび第２室外ユニット１ｂに送られ、第１四路切換弁７ａおよび第２四路切換弁７ｂを経由して、再び、第１圧縮機８ａおよび第２圧縮機８ｂにそれぞれ吸入される。   The high-pressure liquid refrigerant is sent to the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c via the first outdoor expansion valve 3a and the second outdoor expansion valve 3b. The high-pressure liquid refrigerant sent to the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c is decompressed by the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c. The low-pressure gas-liquid two-phase refrigerant is sent to the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c, respectively, and the first indoor heat exchanger 6a, The two indoor heat exchangers 6b and the third indoor heat exchanger 6c exchange heat with room air and are evaporated to become a low-pressure gas refrigerant. Here, the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c are respectively a first indoor heat exchanger 6a, a second indoor heat exchanger 6b, and a third indoor heat exchanger 6c. The flow rates of the refrigerant flowing in the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c are controlled so that the degree of superheat on the gas side becomes a predetermined value. This low-pressure gas refrigerant is sent to the first outdoor unit 1a and the second outdoor unit 1b via the gas refrigerant communication pipe 12, and via the first four-way switching valve 7a and the second four-way switching valve 7b. Again, the air is sucked into the first compressor 8a and the second compressor 8b, respectively.

次に、通常運転モードにおける暖房運転について説明する。   Next, the heating operation in the normal operation mode will be described.

暖房運転時は、第１四路切換弁７ａおよび第２四路切換弁７ｂが図１の破線で示される状態、すなわち、第１圧縮機８ａおよび第２圧縮機８ｂの吐出側が第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側に接続され、かつ、第１圧縮機８ａおよび第２圧縮機８ｂの吸入側が、それぞれ、第１室外熱交換器４ａおよび第２室外熱交換器４ｂのガス側に接続された状態となっている。また、第１室外膨張弁３ａおよび第２室外膨張弁３ｂは開状態にされ、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃは第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃの液側における冷媒の各過冷却度が所定値になるように開度調節されるようになっている。なお、本実施形態において、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃの液側における冷媒の各過冷却度は、第１室内熱交温度センサ２６ａ、第２室内熱交温度センサ２６ｂおよび第３室内熱交温度センサ２６ｃによりそれぞれ検出される冷媒温度から、第１室内熱交液側温度センサ２０ａ、第２室内熱交液側温度センサ２０ｂおよび第３室内熱交液側温度センサ２０ｃによりそれぞれ検出される冷媒温度を差し引くことによって検出される。   During the heating operation, the first four-way switching valve 7a and the second four-way switching valve 7b are in the state indicated by the broken lines in FIG. 1, that is, the discharge sides of the first compressor 8a and the second compressor 8b are in the first indoor heat. It is connected to the gas side of the exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c, and the first outdoor heat exchange is performed on the suction side of the first compressor 8a and the second compressor 8b, respectively. It is in the state connected to the gas side of the container 4a and the 2nd outdoor heat exchanger 4b. The first outdoor expansion valve 3a and the second outdoor expansion valve 3b are opened, and the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c are the first indoor heat exchanger 6a, The opening degree is adjusted so that the degree of subcooling of the refrigerant on the liquid side of the second indoor heat exchanger 6b and the third indoor heat exchanger 6c becomes a predetermined value. In the present embodiment, the degree of subcooling of the refrigerant on the liquid side of the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c is determined by the first indoor heat exchanger temperature sensor 26a. From the refrigerant temperatures detected by the second indoor heat exchange temperature sensor 26b and the third indoor heat exchange temperature sensor 26c, the first indoor heat exchange liquid side temperature sensor 20a, the second indoor heat exchange liquid side temperature sensor 20b, and the second It is detected by subtracting the refrigerant temperature detected by each of the three indoor heat exchange liquid temperature sensors 20c.

この冷媒回路１０の状態で第１圧縮機８ａおよび第２圧縮機８ｂを起動すると、低圧のガス冷媒は、第１圧縮機８ａおよび第２圧縮機８ｂに吸入されて圧縮されて高圧のガス冷媒となり、第１四路切換弁７ａおよび第２四路切換弁７ｂを経由して、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃに送られる。   When the first compressor 8a and the second compressor 8b are started in the state of the refrigerant circuit 10, the low-pressure gas refrigerant is sucked into the first compressor 8a and the second compressor 8b and compressed to be high-pressure gas refrigerant. And is sent to the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c via the first four-way switching valve 7a and the second four-way switching valve 7b.

そして、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃに送られた高圧のガス冷媒は、それぞれ、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃにおいて、室内空気と熱交換を行って凝縮されて高圧の液冷媒となった後、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃによって減圧されて低圧の気液二相の冷媒となる。ここで、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃは、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃの液側における各過冷却度が所定値になるように第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃ内を流れる冷媒の流量をそれぞれ制御している。この低圧の気液二相の冷媒は、液冷媒連絡配管１１を経由して第１室外ユニット１ａおよび第２室外ユニット１ｂに送られる。第１室外ユニット１ａおよび第２室外ユニット１ｂに送られた低圧の気液二相の冷媒は、第１室外熱交換器４ａおよび第２室外熱交換器４ｂにそれぞれ送られ、室外空気と熱交換を行って凝縮されて低圧のガス冷媒となり、第１四路切換弁７ａおよび第２四路切換弁７ｂを経由して、再び、第１圧縮機８ａおよび第２圧縮機８ｂにそれぞれ吸入される。   The high-pressure gas refrigerant sent to the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c is the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor, respectively. In the heat exchanger 6c, the heat is exchanged with the room air to be condensed into a high-pressure liquid refrigerant, and then decompressed by the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c. It becomes a low-pressure gas-liquid two-phase refrigerant. Here, the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c are liquids of the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c. The flow rate of the refrigerant flowing through the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c is controlled so that the degree of subcooling on the side becomes a predetermined value. The low-pressure gas-liquid two-phase refrigerant is sent to the first outdoor unit 1a and the second outdoor unit 1b via the liquid refrigerant communication pipe 11. The low-pressure gas-liquid two-phase refrigerant sent to the first outdoor unit 1a and the second outdoor unit 1b is sent to the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b, respectively, and exchanges heat with outdoor air. And is condensed into a low-pressure gas refrigerant, and is again sucked into the first compressor 8a and the second compressor 8b via the first four-way switching valve 7a and the second four-way switching valve 7b, respectively. .

このように、空気調和装置１００において通常運転を行う場合、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃには、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃが設置されている空調空間において要求される運転負荷に応じた冷媒量がそれぞれ流れている。   Thus, when normal operation is performed in the air conditioner 100, the first indoor unit 2a and the second indoor heat exchanger 6c are provided in the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c. Refrigerant amounts corresponding to the operating loads required in the air-conditioned space in which the unit 2b and the third indoor unit 2c are installed flow respectively.

〔冷媒充填運転モード〕
次に、冷媒充填運転モードについて、図１、図２、図３、図４および図５を用いて説明する。 [Refrigerant charging operation mode]
Next, the refrigerant charging operation mode will be described with reference to FIGS. 1, 2, 3, 4, and 5.

本実施形態では、現地において、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃと所定量の冷媒が予め充填されている第１室外ユニット１ａおよび第２室外ユニット１ｂとを設置し、液冷媒連絡配管１１およびガス冷媒連絡配管１２を介して第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃと第１室外ユニット１ａおよび第２室外ユニット１ｂとを接続して冷媒回路１０を構成した後に、液冷媒連絡配管１１およびガス冷媒連絡配管１２の長さに応じて不足する冷媒を冷媒回路１０内に追加充填した場合を例にして説明する。以下、後述する冷媒充填運転において、ステップＳ１からステップＳ３までを冷媒充填開始運転と、ステップＳ４からステップＳ８までを冷媒安定運転と、ステップＳ９からステップＳ１４までを冷媒充填完了運転という。   In the present embodiment, the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c, and the first outdoor unit 1a and the second outdoor unit 1b that are pre-filled with a predetermined amount of refrigerant are installed in the field. Then, the first indoor unit 2a, the second indoor unit 2b and the third indoor unit 2c are connected to the first outdoor unit 1a and the second outdoor unit 1b via the liquid refrigerant communication pipe 11 and the gas refrigerant communication pipe 12. An example will be described in which after the refrigerant circuit 10 is configured, the refrigerant circuit 10 is additionally filled with a refrigerant that is insufficient in accordance with the lengths of the liquid refrigerant communication pipe 11 and the gas refrigerant communication pipe 12. Hereinafter, in the refrigerant charging operation described later, Steps S1 to S3 are referred to as refrigerant charging start operation, Steps S4 to S8 are referred to as refrigerant stable operation, and Steps S9 to S14 are referred to as refrigerant charging completion operation.

まず、冷媒充填を行う作業者が、第１室外ユニット１ａおよび第２室外ユニット１ｂの第１液側閉鎖弁２４ａおよび第２液側閉鎖弁２４ｂと第１ガス側閉鎖弁２５ａおよび第２ガス側閉鎖弁２５ｂとをそれぞれ開けて、第１室外ユニット１ａおよび第２室外ユニット１ｂに予め充填されている冷媒を冷媒回路１０内に充満させる。   First, the operator who fills the refrigerant has the first liquid side closing valve 24a and the second liquid side closing valve 24b, the first gas side closing valve 25a and the second gas side of the first outdoor unit 1a and the second outdoor unit 1b. Each of the shut-off valves 25b is opened, and the refrigerant circuit 10 is filled with the refrigerant preliminarily charged in the first outdoor unit 1a and the second outdoor unit 1b.

次に、冷媒充填を行う作業者が、第１ガス側閉鎖弁２５ａ近くに設置したチャージポートと、冷媒が封入されたボンベ（図示せず）とを、充填バルブが設けられている充填配管を用いて接続する。そして、冷媒充填を行う作業者が、主制御部６０に対して直接に、または、リモコン等を通じて遠隔に、冷媒充填を開始する冷媒充填運転の指令を出すと、主制御部６０によって図３に示されるステップＳ１の処理が行われる。   Next, an operator who performs the refrigerant charging includes a charge port installed near the first gas side closing valve 25a and a cylinder (not shown) in which the refrigerant is sealed, and a charging pipe provided with the charging valve. Use to connect. Then, when an operator who performs refrigerant filling issues a refrigerant charging operation command for starting refrigerant charging directly to the main control unit 60 or remotely through a remote controller or the like, the main control unit 60 causes the operation shown in FIG. The process of step S1 shown is performed.

冷媒充填運転の開始指令が出されると、第１室外ユニット１ａおよび第２室外ユニット１ｂにおいて第１四路切換弁７ａおよび第２四路切換弁７ｂが図１の実線で示される状態に、第１室外膨張弁３ａおよび第２室外膨張弁３ｂがそれぞれ開状態に、かつ、第１室内ユニット２ａ、第２室内ユニット２ｂおよび第３室内ユニット２ｃの第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃがそれぞれ開状態にされる。この冷媒回路１０の状態で第１圧縮機８ａおよび第２圧縮機８ｂを起動すると、強制的に冷房運転が行われる。この冷房運転を所定時間行うことで、既に冷媒回路１０に充填されている冷媒を安定させることができる。冷房運転が行われてから所定時間が経過したあと、引き続き冷房運転を行いながら充填バルブが開状態にされ、ボンベから冷媒回路１０内に冷媒が供給される。これによって、冷媒充填運転が開始される。   When a command to start the refrigerant charging operation is issued, the first four-way switching valve 7a and the second four-way switching valve 7b in the first outdoor unit 1a and the second outdoor unit 1b are in the state shown by the solid line in FIG. The first outdoor expansion valve 3a and the second outdoor expansion valve 3b are opened, and the first indoor expansion valve 5a and the second indoor expansion valve of the first indoor unit 2a, the second indoor unit 2b, and the third indoor unit 2c. 5b and the third indoor expansion valve 5c are each opened. When the first compressor 8a and the second compressor 8b are started in the state of the refrigerant circuit 10, the cooling operation is forcibly performed. By performing this cooling operation for a predetermined time, the refrigerant already filled in the refrigerant circuit 10 can be stabilized. After a predetermined time has passed since the cooling operation, the charging valve is opened while continuing the cooling operation, and the refrigerant is supplied into the refrigerant circuit 10 from the cylinder. Thereby, the refrigerant charging operation is started.

すると、冷媒回路１０において、第１圧縮機８ａおよび第２圧縮機８ｂから凝縮器として機能する第１室外熱交換器４ａおよび第２室外熱交換器４ｂまでの流路には第１圧縮機８ａおよび第２圧縮機８ｂにおいて圧縮され吐出された高圧のガス冷媒が流れ、凝縮器として機能する第１室外熱交換器４ａおよび第２室外熱交換器４ｂ内には室外空気との熱交換によってガス状態から液状態に相変化する高圧の冷媒が流れ、第１室外熱交換器４ａおよび第２室外熱交換器４ｂから第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃまでの第１室外膨張弁３ａおよび第２室外膨張弁３ｂを介し液冷媒連絡配管１１を含む流路には高圧の液冷媒が流れ、蒸発器として機能する第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃ内には室内空気との熱交換によって気液二相状態からガス状態に相変化する低圧の冷媒が流れ、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃから第１圧縮機８ａおよび第２圧縮機８ｂまでのガス冷媒連絡配管１２を含む流路には低圧のガス冷媒が流れるようになる。このとき、各室内側開度調節部６７ａ，６７ｂ，６７ｃは、蒸発器として機能する第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側における冷媒の各過熱度が所定値となるように第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃの開度をそれぞれ調節する。また、第１室外側判定部６２ａは凝縮器として機能する第１室外熱交換器４ａの液側における冷媒の過冷却度として第１過冷却度を、第２室外側判定部６２ｂは第２室外熱交換器４ｂの液側における冷媒の過冷却度として第２過冷却度をそれぞれ算出する（ステップＳ２）。そして、第１室外側判定部６２ａおよび第２室外側判定部６２ｂにおいて算出された第１過冷却度および第２過冷却度のうちの過冷却度が大きい方の室外熱交換器を有する室外ユニットを非対象ユニットに設定し、他方を対象ユニットに設定する（ステップＳ３）。これによって、冷媒充填開始運転が完了する。   Then, in the refrigerant circuit 10, the first compressor 8a is provided in the flow path from the first compressor 8a and the second compressor 8b to the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b functioning as a condenser. The high-pressure gas refrigerant compressed and discharged in the second compressor 8b flows, and gas is exchanged in the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b functioning as a condenser by heat exchange with outdoor air. The high-pressure refrigerant that changes phase from the liquid state flows, and the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c from the first outdoor heat exchanger 4a and the second outdoor heat exchanger 4b. High-pressure liquid refrigerant flows through the flow path including the liquid refrigerant communication pipe 11 via the first outdoor expansion valve 3a and the second outdoor expansion valve 3b until the first indoor heat exchanger 6a and second that function as an evaporator. Indoor heat exchanger 6b and third A low-pressure refrigerant that changes phase from a gas-liquid two-phase state to a gas state flows through the internal heat exchanger 6c by heat exchange with room air, and the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the second The low-pressure gas refrigerant flows through the flow path including the gas refrigerant communication pipe 12 from the three indoor heat exchanger 6c to the first compressor 8a and the second compressor 8b. At this time, each indoor side opening degree adjustment part 67a, 67b, 67c is the refrigerant | coolant in the gas side of the 1st indoor heat exchanger 6a which functions as an evaporator, the 2nd indoor heat exchanger 6b, and the 3rd indoor heat exchanger 6c. The degree of opening of each of the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c is adjusted so that the respective superheat degrees become predetermined values. Further, the first outdoor side determination unit 62a uses the first subcooling degree as the refrigerant subcooling degree on the liquid side of the first outdoor heat exchanger 4a functioning as a condenser, and the second outdoor side determination unit 62b uses the second outdoor side. A second degree of subcooling is calculated as the degree of subcooling of the refrigerant on the liquid side of the heat exchanger 4b (step S2). And the outdoor unit which has an outdoor heat exchanger with the larger supercooling degree of the 1st subcooling degree calculated in the 1st outdoor side determination part 62a and the 2nd outdoor side determination part 62b, and the 2nd subcooling degree Is set as a non-target unit, and the other is set as a target unit (step S3). Thereby, the refrigerant charging start operation is completed.

冷媒充填開始運転が完了すると、図４に示すように、非対象ユニットの室外膨張弁の開度が全開状態に固定され、対象ユニットおよび非対象ユニットのそれぞれの過冷却度が再び算出される（ステップＳ４）。そして、再び算出された対象ユニットの過冷却度と再び算出された非対象ユニットの過冷却度とが比較される（ステップＳ５）。対象ユニットの過冷却度が非対象ユニットの過冷却度以下である場合、対象ユニットの室外膨張弁の開度を小さくする（ステップＳ６）。また、対象ユニットの過冷却度が非対象ユニットの過冷却度よりも大きい場合、対象ユニットの室外膨張弁の開度を大きくする（ステップＳ７）。対象ユニットの室外膨張弁の開度が調節されたあと、再び、対象ユニットの過冷却度および非対象ユニットの過冷却度が算出され、それぞれの過冷却度が比較される（ステップＳ８）。このとき、それぞれの過冷却度が一致している場合、冷媒安定運転が完了する。また、それぞれの過冷却度が一致していない場合、ステップＳ５に移行し、対象ユニットおよび非対象ユニットの過冷却度が比較される。なお、この冷媒安定運転は以下に説明する冷媒充填完了運転と並行して行われる。   When the refrigerant charging start operation is completed, as shown in FIG. 4, the opening degree of the outdoor expansion valve of the non-target unit is fixed to the fully open state, and the respective subcooling degrees of the target unit and the non-target unit are calculated again ( Step S4). Then, the subcooling degree of the target unit calculated again is compared with the subcooling degree of the non-target unit calculated again (step S5). When the degree of supercooling of the target unit is less than or equal to the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the target unit is reduced (step S6). Further, when the degree of supercooling of the target unit is larger than the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the target unit is increased (step S7). After the opening degree of the outdoor expansion valve of the target unit is adjusted, the degree of supercooling of the target unit and the degree of supercooling of the non-target unit are calculated again, and the respective subcooling degrees are compared (step S8). At this time, when the respective subcooling degrees coincide, the refrigerant stable operation is completed. If the respective subcooling degrees do not match, the process proceeds to step S5, and the subcooling degrees of the target unit and the non-target unit are compared. The refrigerant stable operation is performed in parallel with the refrigerant charging completion operation described below.

冷媒安定運転が所定時間行われた状態で、図５に示すように、再び、非対象ユニットの過冷却度が算出される（ステップＳ９）。このとき算出された非対象ユニットの過冷却度と冷媒充填完了の目標値として設定されている所定値との比較が行われる（ステップＳ１０）。このときの非対象ユニット過冷却度が所定値以上である場合、非対象ユニットの過冷却度と対象ユニットの過冷却度とが比較される（ステップＳ１１）。比較されたそれぞれの過冷却度が一致している場合、充填バルブを閉状態にし、ボンベからの冷媒の供給を停止する（ステップＳ１２）。これによって、冷媒充填完了運転が完了する。したがって、冷媒充填運転が完了する。また、ステップＳ１１において、非対象ユニットの過冷却度と対象ユニットの過冷却度とが比較されたとき、それぞれの過冷却度が一致していない場合もまた、充填バルブを閉状態にし、ボンベからの冷媒の供給を停止する。そして、ボンベからの冷媒の供給を停止した状態で、冷媒安定運転を所定時間行う（ステップＳ１３）。冷媒安定運転が所定時間行われたあと、ステップＳ９に移行し、非対象ユニットの過冷却度が算出され、非対象ユニットと所定値との比較が行われる（ステップＳ１０）。このとき、非対象ユニットの過冷却度が所定値以上でない場合、充填バルブを開状態にし、再び、ボンベから冷媒の供給を開始する（ステップＳ１４）。なお、本実施形態では、ステップＳ８およびステップＳ１１は対象ユニットの過冷却度と非対象ユニットの過冷却度とが一致するまで行われているが、それぞれの過冷却度が所定の範囲内に入るまで行われてもよい。   With the refrigerant stable operation performed for a predetermined time, as shown in FIG. 5, the degree of supercooling of the non-target unit is calculated again (step S9). The degree of supercooling of the non-target unit calculated at this time is compared with a predetermined value set as a target value for completion of refrigerant charging (step S10). If the non-target unit supercooling degree at this time is equal to or greater than a predetermined value, the supercooling degree of the non-target unit and the supercooling degree of the target unit are compared (step S11). If the compared subcooling degrees match, the charging valve is closed and the supply of refrigerant from the cylinder is stopped (step S12). Thereby, the refrigerant filling completion operation is completed. Therefore, the refrigerant charging operation is completed. In step S11, when the degree of supercooling of the non-target unit and the degree of supercooling of the target unit are compared, if the degree of supercooling does not match, the charging valve is also closed and Stop supplying the refrigerant. Then, in a state where the supply of the refrigerant from the cylinder is stopped, the refrigerant stable operation is performed for a predetermined time (step S13). After the refrigerant stable operation is performed for a predetermined time, the process proceeds to step S9, the degree of supercooling of the non-target unit is calculated, and the non-target unit is compared with the predetermined value (step S10). At this time, if the degree of supercooling of the non-target unit is not equal to or greater than the predetermined value, the charging valve is opened, and the supply of refrigerant from the cylinder is started again (step S14). In this embodiment, step S8 and step S11 are performed until the degree of supercooling of the target unit and the degree of supercooling of the non-target unit match, but each degree of supercooling falls within a predetermined range. It may be done.

＜特徴＞
（１）
従来、１つの室外ユニットを備える空気調和装置では、冷媒回路に冷媒が充填されるとき、室外熱交換器を凝縮器として機能させ、室外熱交換器の液側における冷媒の過冷却度を検出し、その過冷却度によって冷媒回路への冷媒の充填量を判断するものがある。 <Features>
(1)
Conventionally, in an air conditioner equipped with one outdoor unit, when the refrigerant circuit is filled with refrigerant, the outdoor heat exchanger functions as a condenser to detect the degree of refrigerant subcooling on the liquid side of the outdoor heat exchanger. In some cases, the amount of refrigerant charged in the refrigerant circuit is determined based on the degree of supercooling.

しかしながら、複数の室外ユニットを備える空気調和装置において、冷媒回路に冷媒を充填する場合、各室外ユニットの設置状況や温度状況等によって冷媒が偏流し、各室外熱交換器の各過冷却度が偏ることがある。このため、室外熱交換器の液側における冷媒の過冷却度によって冷媒回路へ充填されている冷媒量を判断する精度が低下するおそれがあった。   However, in an air conditioner equipped with a plurality of outdoor units, when the refrigerant is filled in the refrigerant circuit, the refrigerant drifts depending on the installation status, temperature status, etc. of each outdoor unit, and each subcooling degree of each outdoor heat exchanger is biased. Sometimes. For this reason, there exists a possibility that the precision which judges the refrigerant | coolant amount with which the refrigerant circuit is filled with the subcooling degree of the refrigerant | coolant in the liquid side of an outdoor heat exchanger may fall.

これに対して、上記実施形態では、第１室外膨張弁３ａおよび第２室外膨張弁３ｂを制御する第１室外側開度調節部６４ａおよび第２室外側開度調節部６４ｂを備えている。第１室外側開度調節部６４ａおよび第２室外側開度調節部６４ｂは、冷媒充填開始運転において、算出される第１過冷却度および第２過冷却度のうち過冷却度が大きい方の室外熱交換器を有する室外ユニットを非対象ユニットに設定し、他方を対象ユニットに設定する（ステップＳ３）。また、第１室外側開度調節部６４ａおよび第２室外側開度調節部６４ｂは、冷媒安定運転において、非対象ユニットの有する室外膨張弁の開度を全開状態に固定し、対象ユニットの有する室外膨張弁の開度を調節する（ステップＳ４〜ステップＳ７）。このため、対象ユニットと非対象ユニットとの過冷却度が等しくなっていく。したがって、対象ユニットの有する室外熱交換器および非対称ユニットの有する室外熱交換器において冷媒の偏流が発生し難くなる。   On the other hand, in the said embodiment, the 1st outdoor side opening degree adjustment part 64a and the 2nd outdoor side opening degree adjustment part 64b which control the 1st outdoor expansion valve 3a and the 2nd outdoor expansion valve 3b are provided. The first outdoor side opening degree adjusting unit 64a and the second outdoor side opening degree adjusting unit 64b have a larger supercooling degree among the calculated first and second subcooling degrees in the refrigerant charging start operation. An outdoor unit having an outdoor heat exchanger is set as a non-target unit, and the other is set as a target unit (step S3). Moreover, the 1st outdoor side opening degree adjustment part 64a and the 2nd outdoor side opening degree adjustment part 64b fix the opening degree of the outdoor expansion valve which a non-target unit has in a full open state, and have a target unit in refrigerant | coolant stable operation. The opening degree of the outdoor expansion valve is adjusted (steps S4 to S7). For this reason, the degree of supercooling of the target unit and the non-target unit becomes equal. Therefore, refrigerant drift hardly occurs in the outdoor heat exchanger of the target unit and the outdoor heat exchanger of the asymmetric unit.

これによって、冷媒回路１０への冷媒充填時、冷媒回路１０へ充填されている冷媒量を判断する精度を向上させることができる。   Accordingly, it is possible to improve the accuracy of determining the amount of refrigerant charged in the refrigerant circuit 10 when the refrigerant circuit 10 is filled with refrigerant.

（２）
上記実施形態では、第１室外熱交換器４ａの液側における冷媒の第１過冷却度を算出するために第１室外熱交液側温度センサ２３ａおよび第１室外熱交温度センサ２２ａが、第２室外熱交換器４ｂの液側における冷媒の第２過冷却度を算出するために第２室外熱交液側温度センサ２３ｂおよび第２室外熱交温度センサ２２ｂがそれぞれ設けられている。このため、第１室外側判定部６２ａおよび第２室外側判定部６２ｂは、第１過冷却度および第２過冷却度を冷媒の温度によって算出することができる。 (2)
In the above embodiment, the first outdoor heat exchange liquid temperature sensor 23a and the first outdoor heat exchange temperature sensor 22a are used to calculate the first subcooling degree of the refrigerant on the liquid side of the first outdoor heat exchanger 4a. In order to calculate the second subcooling degree of the refrigerant on the liquid side of the two outdoor heat exchanger 4b, a second outdoor heat exchange liquid side temperature sensor 23b and a second outdoor heat exchange temperature sensor 22b are provided. For this reason, the 1st outdoor side determination part 62a and the 2nd outdoor side determination part 62b can calculate a 1st supercooling degree and a 2nd supercooling degree with the temperature of a refrigerant | coolant.

これによって、この空気調和装置１００では、簡易な構成によって過冷却度を判定することができる。   Thereby, in this air conditioning apparatus 100, the degree of supercooling can be determined with a simple configuration.

（３）
上記実施形態では、冷媒充填運転が行われているとき、第１室内膨張弁５ａ、第２室内膨張弁５ｂおよび第３室内膨張弁５ｃは、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃのガス側における各過熱度に基づいてそれぞれの開度が調節される。このため、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃに流れる冷媒量をそれぞれ調節することができる。したがって、第１室内熱交換器６ａ、第２室内熱交換器６ｂおよび第３室内熱交換器６ｃを流れる冷媒量を一定に保つことができる。 (3)
In the above embodiment, when the refrigerant charging operation is performed, the first indoor expansion valve 5a, the second indoor expansion valve 5b, and the third indoor expansion valve 5c are the first indoor heat exchanger 6a and the second indoor heat exchange. Each opening degree is adjusted based on each superheat degree in the gas side of the heat exchanger 6b and the 3rd indoor heat exchanger 6c. For this reason, the refrigerant | coolants amount which flows into the 1st indoor heat exchanger 6a, the 2nd indoor heat exchanger 6b, and the 3rd indoor heat exchanger 6c can each be adjusted. Therefore, the amount of refrigerant flowing through the first indoor heat exchanger 6a, the second indoor heat exchanger 6b, and the third indoor heat exchanger 6c can be kept constant.

これによって、冷媒回路１０への冷媒充填時、冷媒回路１０内に充填されている冷媒量を判断する精度を向上させることができる。   Accordingly, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit 10 when the refrigerant circuit 10 is filled with refrigerant.

＜変形例＞
（Ａ）
上記実施形態では、空気調和装置１００は２台の室外ユニットを備えているが、３台以上の室外ユニットを備えていてもよい。例えば、３台の室外ユニット１０１ａ，１０１ｂ，１０１ｃと、室外ユニット１０１ａ，１０１ｂ，１０１ｃに並列に接続された２台の室内ユニット１０２ａ，１０２ｂと、室外ユニット１０１ａ，１０１ｂ，１０１ｃと室内ユニット１０２ａ，１０２ｂとを接続する冷媒連絡配管とを備えている空気調和装置２００の構成について、図６を用いて説明する。また、冷媒連絡配管は液冷媒連絡配管１１１およびガス冷媒連絡配管１１２から構成される
以下、図６、図７、図８、図９および図１０を用いて、この空気調和装置２００における冷媒充填運転モードについて説明する。 <Modification>
(A)
In the above embodiment, the air conditioner 100 includes two outdoor units, but may include three or more outdoor units. For example, three outdoor units 101a, 101b, 101c, two indoor units 102a, 102b connected in parallel to the outdoor units 101a, 101b, 101c, outdoor units 101a, 101b, 101c, and indoor units 102a, 102b The structure of the air conditioning apparatus 200 provided with the refrigerant | coolant communication piping which connects is demonstrated using FIG. The refrigerant communication pipe is composed of a liquid refrigerant communication pipe 111 and a gas refrigerant communication pipe 112. Hereinafter, the refrigerant charging operation in the air conditioner 200 will be described with reference to FIGS. 6, 7, 8, 9 and 10. The mode will be described.

また、本実施形態では、上記実施形態と同様に、現地において、第１室内ユニット１０２ａおよび第２室内ユニット１０２ｂと所定量の冷媒が予め充填されている第１室外ユニット１０１ａ、第２室外ユニット１０１ｂおよび第３室外ユニット１０１ｃとを設置し、液冷媒連絡配管１１１およびガス冷媒連絡配管１１２を接続して冷媒回路１１０を構成した後に、液冷媒連絡配管１１１およびガス冷媒連絡配管１１２の長さに応じて不足する冷媒を冷媒回路１１０内に追加充填した場合を例にして説明する。以下、後述する冷媒充填運転において、ステップＳ３１からステップＳ３３までを冷媒充填開始運転と、ステップＳ３４からステップＳ４１までを冷媒安定運転と、ステップＳ４２からステップＳ４７までを冷媒充填完了運転という。   Further, in the present embodiment, similarly to the above-described embodiment, the first outdoor unit 101a and the second outdoor unit 101b that are pre-filled with a predetermined amount of refrigerant and the first indoor unit 102a and the second indoor unit 102b in the field. And the third outdoor unit 101c are installed, and the liquid refrigerant communication pipe 111 and the gas refrigerant communication pipe 112 are connected to configure the refrigerant circuit 110, and then the length of the liquid refrigerant communication pipe 111 and the gas refrigerant communication pipe 112 is determined. The case where additional refrigerant is additionally filled in the refrigerant circuit 110 will be described as an example. Hereinafter, in the refrigerant charging operation described later, steps S31 to S33 are referred to as refrigerant charging start operation, steps S34 to S41 are referred to as refrigerant stable operation, and steps S42 to S47 are referred to as refrigerant charging completion operation.

まず、冷媒充填を行う作業者が、第１室外ユニット１０１ａ、第２室外ユニット１０１ｂおよび第３室外ユニット１０１ｃの第１液側閉鎖弁１２４ａ、第２液側閉鎖弁１２４ｂおよび第３液側閉鎖弁１２４ｃと第１ガス側閉鎖弁１２５ａ、第２ガス側閉鎖弁１２５ｂおよび第３ガス側閉鎖弁１２５ｃとをそれぞれ開けて、第１室外ユニット１０１ａ、第２室外ユニット１０１ｂおよび第３室外ユニット１０１ｃに予め充填されている冷媒を冷媒回路１１０内に充満させる。   First, the operator who fills the refrigerant has the first liquid side closing valve 124a, the second liquid side closing valve 124b, and the third liquid side closing valve of the first outdoor unit 101a, the second outdoor unit 101b, and the third outdoor unit 101c. 124c, the first gas side closing valve 125a, the second gas side closing valve 125b, and the third gas side closing valve 125c are opened, and the first outdoor unit 101a, the second outdoor unit 101b, and the third outdoor unit 101c are preliminarily opened. The refrigerant filled is filled in the refrigerant circuit 110.

次に、冷媒充填を行う作業者、第１ガス側閉鎖弁１２５ａ近くに設置したチャージポートと冷媒が封入されたボンベ（図示せず）とを充填バルブが設けられている充填配管を用いて接続する。そして、冷媒充填を行う作業者が、主制御部１６０に対して直接に、または、リモコン等を通じて遠隔に、冷媒充填を開始する冷媒充填運転の指令を出と、主制御部１６０によって図８に示されるステップＳ３１の処理が行われる。   Next, an operator who performs refrigerant charging, a charge port installed near the first gas-side closing valve 125a and a cylinder (not shown) filled with the refrigerant are connected using a charging pipe provided with a charging valve. To do. Then, an operator who performs refrigerant charging issues a refrigerant charging operation command for starting refrigerant charging directly to the main control unit 160 or remotely through a remote controller or the like. The process of step S31 shown is performed.

冷媒充填運転の開始指令がなされると、第１室外ユニット１０１ａ、第２室外ユニット１０１ｂおよび第３室外ユニット１０１ｃにおいて第１四路切換弁１０７ａ、第２四路切換弁１０７ｂおよび第３四路切換弁１０７ｃが図６の実線で示される状態に、第１室外膨張弁１０３ａ、第２室外膨張弁１０３ｂおよび第３室外膨張弁１０３ｃがそれぞれ開状態に、かつ、第１室内ユニット１０２ａおよび第２室内ユニット１０２ｂの第１室内膨張弁１０５ａおよび第２室内膨張弁１０５ｂがそれぞれ開状態にされる。この冷媒回路１１０の状態で第１圧縮機１０８ａ、第２圧縮機１０８ｂおよび第３圧縮機１０８ｃを起動すると、強制的に冷房運転が行われる。この冷房運転を所定時間行うことで、既に冷媒回路１１０に充填されている冷媒を安定させることができる。冷房運転が行われてから所定時間が経過したあと、引き続き冷房運転を行いながら充填バルブを開状態にし、ボンベから冷媒回路１１０内に冷媒を供給する。これによって、冷媒充填運転が開始される。   When an instruction to start the refrigerant charging operation is made, the first four-way switching valve 107a, the second four-way switching valve 107b, and the third four-way switching are performed in the first outdoor unit 101a, the second outdoor unit 101b, and the third outdoor unit 101c. The first outdoor expansion valve 103a, the second outdoor expansion valve 103b, and the third outdoor expansion valve 103c are opened, and the first indoor unit 102a and the second indoor The first indoor expansion valve 105a and the second indoor expansion valve 105b of the unit 102b are opened. When the first compressor 108a, the second compressor 108b, and the third compressor 108c are started in the state of the refrigerant circuit 110, the cooling operation is forcibly performed. By performing this cooling operation for a predetermined time, the refrigerant already filled in the refrigerant circuit 110 can be stabilized. After a predetermined time has elapsed since the cooling operation, the charging valve is opened while continuing the cooling operation, and the refrigerant is supplied into the refrigerant circuit 110 from the cylinder. Thereby, the refrigerant charging operation is started.

すると、冷媒回路１１０において、第１圧縮機１０８ａ、第２圧縮機１０８ｂおよび第３圧縮機１０８ｃから凝縮器として機能する第１室外熱交換器１０４ａ、第２室外熱交換器１０４ｂおよび第３室外熱交換器１０４ｃまでの流路には第１圧縮機１０８ａ、第２圧縮機１０８ｂおよび第３圧縮機１０８ｃにおいて圧縮され吐出された高圧のガス冷媒が流れ、凝縮器として機能する第１室外熱交換器１０４ａ、第２室外熱交換器１０４ｂおよび第３室外熱交換器１０４ｃ内には室外空気との熱交換によってガス状態から液状態に相変化する高圧の冷媒が流れ、第１室外熱交換器１０４ａ、第２室外熱交換器１０４ｂおよび第３室外熱交換器１０４ｃから第１室内膨張弁１０５ａおよび第２室内膨張弁１０５ｂまでの第１室外膨張弁１０３ａ、第２室外膨張弁１０３ｂおよび第３室外膨張弁１０３ｃを介し液冷媒連絡配管１１１を含む流路には高圧の液冷媒が流れ、蒸発器として機能する第１室内熱交換器１０６ａおよび第２室内熱交換器１０６ｂ内には室内空気との熱交換によって気液二相状態からガス状態に相変化する低圧の冷媒が流れ、第１室内熱交換器１０６ａおよび第２室内熱交換器１０６ｂから第１圧縮機１０８ａ、第２圧縮機１０８ｂおよび第３圧縮機１０８ｃまでのガス冷媒連絡配管１１２を含む流路には低圧のガス冷媒が流れるようになる。このとき、各室内側開度調節部１６１ａ，１６１ｂは、蒸発器として機能する第１室内熱交換器１０６ａおよび第２室内熱交換器１０６ｂのガス側における冷媒の各過熱度が所定値となるように第１室内膨張弁１０５ａおよび第２室内膨張弁１０５ｂの開度をそれぞれ調節する。また、第１室外側判定部１６２ａは凝縮器として機能する第１室外熱交換器１０４ａの液側における冷媒の過冷却度として第１過冷却度を、第２室外側判定部１６２ｂは第２室外熱交換器１０４ｂの液側における冷媒の過冷却度として第２過冷却度を、第３室外側判定部１６２ｃは第３室外熱交換器１０４ｃの液側における冷媒の過冷却度として第３過冷却度をそれぞれ算出する（ステップＳ３２）。   Then, in the refrigerant circuit 110, the first outdoor heat exchanger 104a, the second outdoor heat exchanger 104b, and the third outdoor heat functioning as a condenser from the first compressor 108a, the second compressor 108b, and the third compressor 108c. A high-pressure gas refrigerant compressed and discharged in the first compressor 108a, the second compressor 108b, and the third compressor 108c flows through the flow path to the exchanger 104c, and functions as a condenser. 104a, the second outdoor heat exchanger 104b, and the third outdoor heat exchanger 104c flow a high-pressure refrigerant that changes phase from a gas state to a liquid state by heat exchange with outdoor air, and the first outdoor heat exchanger 104a, A first outdoor expansion valve 103a from the second outdoor heat exchanger 104b and the third outdoor heat exchanger 104c to the first indoor expansion valve 105a and the second indoor expansion valve 105b; High-pressure liquid refrigerant flows through the flow path including the liquid refrigerant communication pipe 111 via the two outdoor expansion valves 103b and the third outdoor expansion valve 103c, and the first indoor heat exchanger 106a and the second indoor heat exchange functioning as an evaporator. A low-pressure refrigerant that changes phase from a gas-liquid two-phase state to a gas state flows through the heat exchange with the room air in the heat exchanger 106b, and the first compressor from the first indoor heat exchanger 106a and the second indoor heat exchanger 106b. A low-pressure gas refrigerant flows through the flow path including the gas refrigerant communication pipe 112 to 108a, the second compressor 108b, and the third compressor 108c. At this time, each indoor side opening degree adjustment part 161a, 161b is set so that each superheat degree of the refrigerant | coolant in the gas side of the 1st indoor heat exchanger 106a which functions as an evaporator and the 2nd indoor heat exchanger 106b becomes a predetermined value. The opening degrees of the first indoor expansion valve 105a and the second indoor expansion valve 105b are respectively adjusted. The first outdoor side determination unit 162a uses the first supercooling degree as the refrigerant subcooling degree on the liquid side of the first outdoor heat exchanger 104a functioning as a condenser, and the second outdoor side determination unit 162b uses the second outdoor side. The second subcooling degree is used as the refrigerant subcooling degree on the liquid side of the heat exchanger 104b, and the third outdoor side determination unit 162c is the third subcooling degree as the refrigerant subcooling degree on the liquid side of the third outdoor heat exchanger 104c. Each degree is calculated (step S32).

そして、第１室外側判定部１６２ａ、第２室外側判定部１６２ｂおよび第３室外側判定部１６２ｃにおいて算出された第１過冷却度、第２過冷却度および第３過冷却度のうち最も大きい過冷却度が算出された室外熱交換器を有する室外ユニットを非対象ユニットに設定し、他の室外ユニットを第１対象ユニットおよび第２対象ユニットに設定する（ステップＳ３３）。これによって、冷媒充填開始運転が完了する。   And it is the largest among the 1st subcooling degree, the 2nd subcooling degree, and the 3rd subcooling degree computed in the 1st outdoor side judging part 162a, the 2nd outdoor side judging part 162b, and the 3rd outdoor side judging part 162c. The outdoor unit having the outdoor heat exchanger for which the degree of supercooling is calculated is set as a non-target unit, and the other outdoor units are set as a first target unit and a second target unit (step S33). Thereby, the refrigerant charging start operation is completed.

冷媒充填運転が完了すると、図９に示されるように、非対象ユニットの室外膨張弁の開度が全開状態に固定され、非対象ユニット、第１対象ユニットおよび第２対象ユニットのそれぞれの過冷却度が再び算出される（ステップＳ３４）。そして、再び算出された第１対象ユニットの過冷却度と再び算出された非対象ユニットの過冷却度とが比較される（ステップＳ３５）。第１対象ユニットの過冷却度が非対象ユニットの過冷却度以下である場合、第１対象ユニットの室外膨張弁の開度を小さくする（ステップＳ３６）。また、第１対象ユニットの過冷却度が非対象ユニットの過冷却度より大きい場合、第１対象ユニットの室外膨張弁の開度を大きくする（ステップＳ３７）。第１対象ユニットの室外膨張弁の開度が調節されたあと、ステップＳ３４において算出された第２対象ユニットの過冷却度と非対象ユニットの過冷却度とが比較される（ステップＳ３８）。第２対象ユニットの過冷却度が非対象ユニットの過冷却度以下である場合、第２対象ユニットの室外膨張弁の開度を小さくする（ステップＳ３９）。また、第２対象ユニットの過冷却度が非対象ユニットの過冷却度より大きい場合、第２対象ユニットの室外膨張弁の開度を大きくする（ステップＳ４０）。第１対象ユニットおよび第２対象ユニットの各室外膨張弁の開度が調節されたあと、再び、非対象ユニットの過冷却度、第１対象ユニットの過冷却度および第２対象ユニットの過冷却度が算出され、それぞれの過冷却度が一致しているか否かが判定される（ステップＳ４１）。このとき、それぞれの過冷却度が一致している場合、冷媒安定運転が完了する（ステップＳ８）。また、それぞれの過冷却度が一致していない場合、ステップＳ３５に移行し、再び、第１対象ユニットの過冷却度と非対象ユニットの過冷却度とが比較される。なお、この冷媒安定運転は、以下に説明する冷媒充填完了運転と並行して行われる。   When the refrigerant charging operation is completed, as shown in FIG. 9, the opening degree of the outdoor expansion valve of the non-target unit is fixed to the fully open state, and each of the non-target unit, the first target unit, and the second target unit is supercooled. The degree is calculated again (step S34). Then, the subcooling degree of the first target unit calculated again is compared with the subcooling degree of the non-target unit calculated again (step S35). When the degree of supercooling of the first target unit is less than or equal to the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the first target unit is reduced (step S36). Further, when the degree of supercooling of the first target unit is larger than the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the first target unit is increased (step S37). After the opening degree of the outdoor expansion valve of the first target unit is adjusted, the degree of supercooling of the second target unit calculated in step S34 is compared with the degree of supercooling of the non-target unit (step S38). When the degree of supercooling of the second target unit is less than or equal to the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the second target unit is reduced (step S39). Further, when the degree of supercooling of the second target unit is larger than the degree of supercooling of the non-target unit, the opening degree of the outdoor expansion valve of the second target unit is increased (step S40). After the opening degree of each outdoor expansion valve of the first target unit and the second target unit is adjusted, the degree of supercooling of the non-target unit, the degree of supercooling of the first target unit, and the degree of supercooling of the second target unit are again. Is calculated, and it is determined whether or not the respective subcooling degrees match (step S41). At this time, when the respective subcooling degrees coincide with each other, the refrigerant stable operation is completed (step S8). If the respective subcooling degrees do not match, the process proceeds to step S35, and the supercooling degree of the first target unit is again compared with the supercooling degree of the non-target unit. The refrigerant stable operation is performed in parallel with the refrigerant charging completion operation described below.

冷媒安定運転が所定時間行われた状態で、図１０に示されるように、再び、非対象ユニットの過冷却度が算出される（ステップＳ４２）。このとき算出された非対象ユニットの過冷却度と冷媒充填完了の目標値として設定されている所定値との比較が行われる（ステップＳ４３）。このときの非対象ユニット過冷却度が所定値以上である場合、非対象ユニットの過冷却度、第１対象ユニットおよび第２対象ユニットの過冷却度がそれぞれ比較される（ステップＳ４４）。比較されたそれぞれの過冷却度が一致している場合、充填バルブを閉状態にし、ボンベからの冷媒の供給を停止する（ステップＳ４５）。これによって、冷媒充填完了運転が完了する。したがって、冷媒充填運転が完了する。また、非対象ユニットの過冷却度が所定値以上であり、非対象ユニットの過冷却度、第１対象ユニットの過冷却度および第２対象ユニットの過冷却度が比較されたとき、それぞれの過冷却度が一致していない場合もまた、充填バルブを閉状態にし、ボンベからの冷媒の供給を停止する。そして、ボンベからの冷媒の供給を停止した状態で、冷媒安定運転が所定時間行われる（ステップＳ４６）。冷媒安定運転が所定時間行われたあと、ステップＳ４２に移行し、非対象ユニットの過冷却度が算出され、非対象ユニットと所定値との比較が行われる（ステップＳ４３）。このとき、非対象ユニットの過冷却度が所定値以上でない場合、充填バルブを開状態にし、再び、ボンベから冷媒の供給を開始する（ステップＳ４７）。なお、本実施形態では、ステップＳ４１およびステップＳ４４では、非対象ユニット、第１対象ユニットおよび第２対象ユニットの過冷却度がそれぞれ一致するまで行われているが、それぞれの過冷却度が所定の範囲内に入るまで行われてもよい。   With the refrigerant stable operation performed for a predetermined time, as shown in FIG. 10, the degree of supercooling of the non-target unit is calculated again (step S42). The degree of supercooling of the non-target unit calculated at this time is compared with a predetermined value set as a target value for completion of refrigerant charging (step S43). If the non-target unit supercooling degree at this time is equal to or greater than a predetermined value, the supercooling degree of the non-target unit and the supercooling degrees of the first target unit and the second target unit are compared (step S44). When the compared supercooling degrees match, the filling valve is closed and the supply of the refrigerant from the cylinder is stopped (step S45). Thereby, the refrigerant filling completion operation is completed. Therefore, the refrigerant charging operation is completed. In addition, when the degree of supercooling of the non-target unit is equal to or greater than a predetermined value and the degree of supercooling of the non-target unit, the degree of supercooling of the first target unit, and the degree of supercooling of the second target unit are compared, When the degree of cooling does not match, the filling valve is also closed and the supply of the refrigerant from the cylinder is stopped. Then, the refrigerant stable operation is performed for a predetermined time with the supply of the refrigerant from the cylinder stopped (step S46). After the refrigerant stable operation is performed for a predetermined time, the process proceeds to step S42, the degree of supercooling of the non-target unit is calculated, and the non-target unit is compared with the predetermined value (step S43). At this time, if the degree of supercooling of the non-target unit is not equal to or greater than the predetermined value, the charging valve is opened, and the supply of refrigerant from the cylinder is started again (step S47). In the present embodiment, in step S41 and step S44, the process is performed until the subcooling degrees of the non-target unit, the first target unit, and the second target unit match. It may be performed until it falls within the range.

（Ｂ）
上記実施形態では、室外側制御部６８ａ，６８ｂは、非対象ユニットの過冷却度と所定値とを比較することによって、冷媒回路１０内に充填されている冷媒量を判断している。しかしながら、この空気調和装置１００では、冷媒回路１０内に充填されている冷媒量が判断される冷媒充填完了運転と並行して室外熱交換器１ａ，１ｂの偏流を抑制する運転である冷媒安定運転が行われている。このため、対象ユニットの過冷却度と非対称ユニットの過冷却度とは等しくなっていく。したがって、対象ユニットの過冷却度と所定値とを比較することによって、冷媒回路１０に充填されている冷媒量が判断されてもよい。 (B)
In the above embodiment, the outdoor side control units 68a and 68b determine the amount of refrigerant charged in the refrigerant circuit 10 by comparing the degree of supercooling of the non-target units with a predetermined value. However, in this air conditioner 100, the refrigerant stable operation that is an operation that suppresses the drift of the outdoor heat exchangers 1a and 1b in parallel with the refrigerant filling completion operation in which the amount of refrigerant charged in the refrigerant circuit 10 is determined. Has been done. For this reason, the degree of supercooling of the target unit becomes equal to the degree of supercooling of the asymmetric unit. Therefore, the refrigerant amount filled in the refrigerant circuit 10 may be determined by comparing the degree of supercooling of the target unit with a predetermined value.

（Ｃ）
上記実施形態では、対象ユニットの過冷却度と非対象ユニットの過冷却度とが等しくなるように、第１過冷却度および第２過冷却度に基づいて、第１室外膨張弁３ａおよび第２室外膨張弁３ｂの開度が調節されている。 (C)
In the above embodiment, the first outdoor expansion valve 3a and the second outdoor cooling valve 3a and the second subcooling degree are based on the first and second subcooling degrees so that the degree of supercooling of the target unit and the degree of subcooling of the non-target units are equal. The opening degree of the outdoor expansion valve 3b is adjusted.

これに代えて、対象ユニットの過冷却度と非対象ユニットの過冷却度とが等しくなるように、第１過冷却度および第２過冷却度に基づいて、第１室外ユニット１ａの有する第１圧縮機８ａの回転数と第２室外ユニット１ｂの有する第２圧縮機８ｂの回転数とが調節されてもよい。以下に、冷媒安定運転において、対象ユニットの過冷却度と非対象ユニットの過冷却度との差が小さくなるように、第１圧縮機８ａの回転数および第２圧縮機８ｂの回転数を調節する空気調和装置の動作を説明する。なお、冷媒充填開始運転および冷媒充填完了運転は、上記実施形態と同様のため説明を省略する。   Instead, the first outdoor unit 1a has the first subcooling degree and the second subcooling degree so that the supercooling degree of the target unit is equal to the supercooling degree of the non-target unit. The rotational speed of the compressor 8a and the rotational speed of the second compressor 8b included in the second outdoor unit 1b may be adjusted. Hereinafter, in the refrigerant stable operation, the rotation speed of the first compressor 8a and the rotation speed of the second compressor 8b are adjusted so that the difference between the subcooling degree of the target unit and the subcooling degree of the non-target unit is reduced. The operation of the air conditioner will be described. Note that the refrigerant charging start operation and the refrigerant charging completion operation are the same as in the above embodiment, and thus the description thereof is omitted.

冷媒充填開始運転（図３のステップＳ１からステップＳ３）が完了すると、図１１に示すように、対象ユニットの圧縮機の回転数が小さくされ、対象ユニットおよび非対象ユニットのそれぞれの過冷却度が再び算出される（ステップＳ５１）。そして、再び算出された対象ユニットの過冷却度と再び算出された非対象ユニットの過冷却度とが比較される（ステップＳ５２）。対象ユニットの過冷却度が非対象ユニットの過冷却度以下である場合、対象ユニットの圧縮機の回転数を小さくする（ステップＳ５３）。また、対象ユニットの過冷却度が非対象ユニットの過冷却度よりも大きい場合、対象ユニットの圧縮機の回転数を大きくする（ステップＳ５４）。対象ユニットの圧縮機の回転数が調節されたあと、再び、対象ユニットの過冷却度および非対象ユニットの過冷却度が算出され、それぞれの過冷却度が比較される（ステップＳ５５）。このとき、それぞれの過冷却度が一致している場合、冷媒安定運転が完了する。また、それぞれの過冷却度が一致していない場合、ステップＳ５２に移行し、対象ユニットおよび非対象ユニットの過冷却度が比較される。なお、この冷媒安定運転は冷媒充填完了運転（図５のステップＳ９からステップＳ１４）と並行して行われる。   When the refrigerant charging start operation (step S1 to step S3 in FIG. 3) is completed, as shown in FIG. 11, the rotation speed of the compressor of the target unit is reduced, and the respective subcooling degrees of the target unit and the non-target unit are set. It is calculated again (step S51). Then, the subcooling degree of the target unit calculated again is compared with the subcooling degree of the non-target unit calculated again (step S52). When the degree of supercooling of the target unit is less than or equal to the degree of supercooling of the non-target unit, the rotational speed of the compressor of the target unit is reduced (step S53). Further, when the degree of supercooling of the target unit is larger than the degree of supercooling of the non-target unit, the rotational speed of the compressor of the target unit is increased (step S54). After the rotation speed of the compressor of the target unit is adjusted, the degree of supercooling of the target unit and the degree of supercooling of the non-target unit are calculated again, and the respective subcooling degrees are compared (step S55). At this time, when the respective subcooling degrees coincide, the refrigerant stable operation is completed. If the respective subcooling degrees do not match, the process proceeds to step S52, and the subcooling degrees of the target unit and the non-target unit are compared. The refrigerant stable operation is performed in parallel with the refrigerant charging completion operation (step S9 to step S14 in FIG. 5).

このように冷媒安定運転が行われることによって、対象ユニットの有する室外熱交換器を流れる冷媒の流量と、非対象ユニットの有する室外熱交換器の冷媒の流量との差を小さくすることができる。したがって、対象ユニットの有する室外熱交換器および非対称ユニットの有する室外熱交換器において冷媒の偏流を発生させ難くすることができる。   By performing the refrigerant stable operation in this way, the difference between the flow rate of the refrigerant flowing through the outdoor heat exchanger of the target unit and the flow rate of the refrigerant of the outdoor heat exchanger of the non-target unit can be reduced. Therefore, it is possible to make it difficult for refrigerant drift to occur in the outdoor heat exchanger of the target unit and the outdoor heat exchanger of the asymmetric unit.

これによって、冷媒回路への冷媒充填時、冷媒回路へ充填されている冷媒量を判断する精度を向上させることができる。   Accordingly, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit when the refrigerant circuit is filled with the refrigerant.

また、対象ユニットの過冷却度と非対象ユニットの過冷却度とが等しくなるように、第１過冷却度および第２過冷却度に基づいて、第１室外ユニット１ａの有する第１室外ファン９ａの回転数と第２室外ユニット１ｂの有する第２室外ファン９ｂの回転数とが調節されてもよい。以下に、冷媒安定運転において、対象ユニットの過冷却度と非対象ユニットの過冷却度との差を小さくするために、第１室外ファン９ａの回転数および第２室外ファン９ｂの回転数を調節する空気調和装置の動作を説明する。なお、冷媒充填開始運転および冷媒充填完了運転は、上記実施形態と同様のため説明を省略する。   Further, the first outdoor fan 9a of the first outdoor unit 1a is based on the first and second subcooling degrees so that the subcooling degree of the target unit and the non-target unit are equal. And the rotation speed of the second outdoor fan 9b of the second outdoor unit 1b may be adjusted. Below, in the refrigerant stable operation, the rotational speed of the first outdoor fan 9a and the rotational speed of the second outdoor fan 9b are adjusted in order to reduce the difference between the degree of supercooling of the target unit and the degree of supercooling of the non-target unit. The operation of the air conditioner will be described. Note that the refrigerant charging start operation and the refrigerant charging completion operation are the same as in the above embodiment, and thus the description thereof is omitted.

冷媒充填開始運転（図３のステップＳ１からステップＳ３）が完了すると、図１２に示すように、対象ユニットの室外ファンの回転数が増加され、対象ユニットおよび非対象ユニットのそれぞれの過冷却度が再び算出される（ステップＳ６１）。そして、再び算出された対象ユニットの過冷却度と再び算出された非対象ユニットの過冷却度とが比較される（ステップＳ６２）。対象ユニットの過冷却度が非対象ユニットの過冷却度以下である場合、対象ユニットの室外ファンの回転数を増加させる（ステップＳ６３）。また、対象ユニットの過冷却度が非対象ユニットの過冷却度よりも大きい場合、対象ユニットの室外ファンの回転数を減少させる（ステップＳ６４）。対象ユニットの室外ファンの回転数が調節されたあと、再び、対象ユニットの過冷却度および非対象ユニットの過冷却度が算出され、それぞれの過冷却度が比較される（ステップＳ６５）。このとき、それぞれの過冷却度が一致している場合、冷媒安定運転が完了する。また、それぞれの過冷却度が一致していない場合、ステップＳ６２に移行し、対象ユニットおよび非対象ユニットの過冷却度が比較される。なお、この冷媒安定運転は冷媒充填完了運転（図５のステップＳ９からステップＳ１４）と並行して行われる。   When the refrigerant charging start operation (step S1 to step S3 in FIG. 3) is completed, as shown in FIG. 12, the rotational speed of the outdoor fan of the target unit is increased, and the degree of supercooling of each of the target unit and the non-target unit is increased. It is calculated again (step S61). Then, the subcooling degree of the target unit calculated again is compared with the subcooling degree of the non-target unit calculated again (step S62). When the degree of supercooling of the target unit is less than or equal to the degree of supercooling of the non-target unit, the rotational speed of the outdoor fan of the target unit is increased (step S63). Further, when the degree of supercooling of the target unit is larger than the degree of supercooling of the non-target unit, the rotational speed of the outdoor fan of the target unit is decreased (step S64). After the rotation speed of the outdoor fan of the target unit is adjusted, the degree of supercooling of the target unit and the degree of supercooling of the non-target unit are calculated again, and the respective subcooling degrees are compared (step S65). At this time, when the respective subcooling degrees coincide, the refrigerant stable operation is completed. If the respective subcooling degrees do not match, the process proceeds to step S62, and the subcooling degrees of the target unit and the non-target unit are compared. The refrigerant stable operation is performed in parallel with the refrigerant charging completion operation (step S9 to step S14 in FIG. 5).

このように冷媒安定運転が行われることによって、対象ユニットの過冷却度と非対象ユニットの過冷却度との差を小さくすることができる。   By performing the refrigerant stable operation in this manner, the difference between the degree of supercooling of the target unit and the degree of supercooling of the non-target unit can be reduced.

これによって、冷媒回路への冷媒充填時、冷媒回路へ充填されている冷媒量を判断する精度を向上させることができる。   Accordingly, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit when the refrigerant circuit is filled with the refrigerant.

また、冷媒安定運転において、対象ユニットの過冷却度と非対象ユニットの過冷却度とが等しくなるように、圧縮機の回転数を調節する圧縮機調節手段、室外膨張弁の開度を調節する膨張弁調節手段、および、室外ファンの回転数を調節するファン調節手段のうちのいずれかの手段が組み合わされて制御されてもよい。   Further, in the refrigerant stable operation, the opening degree of the compressor adjusting means for adjusting the rotation speed of the compressor and the outdoor expansion valve are adjusted so that the degree of supercooling of the target unit and that of the non-target unit are equal. Any of the expansion valve adjusting means and the fan adjusting means for adjusting the rotation speed of the outdoor fan may be combined and controlled.

本発明によれば、冷媒回路へ冷媒を充填するときに、冷媒回路に充填されている冷媒量を判断する精度を向上することができるようになるため、複数の熱源ユニットを備える空気調和装置への適用が有効である。   According to the present invention, when the refrigerant circuit is filled with the refrigerant, it is possible to improve the accuracy of determining the amount of refrigerant filled in the refrigerant circuit. Therefore, to the air conditioner including a plurality of heat source units. Is effective.

本発明の実施形態に係る空気調和装置の概略の冷媒回路図。1 is a schematic refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention. 本発明の実施形態に係る空気調和装置の制御ブロック図。The control block diagram of the air conditioning apparatus which concerns on embodiment of this invention. 本発明の実施形態に係る空気調和装置における冷媒充填開始運転のフローチャート。The flowchart of the refrigerant | coolant filling start operation in the air conditioning apparatus which concerns on embodiment of this invention. 本発明の実施形態に係る空気調和装置における冷媒安定運転のフローチャート。The flowchart of the refrigerant | coolant stable driving | operation in the air conditioning apparatus which concerns on embodiment of this invention. 本発明の実施形態に係る空気調和装置における冷媒充填完了運転のフローチャート。The flowchart of the refrigerant | coolant filling completion operation | movement in the air conditioning apparatus which concerns on embodiment of this invention. 本発明の変形例（Ａ）に係る空気調和装置の概略の冷媒回路図。The schematic refrigerant circuit figure of the air conditioning apparatus which concerns on the modification (A) of this invention. 本発明の変形例（Ａ）に係る空気調和装置の制御ブロック図。The control block diagram of the air conditioning apparatus which concerns on the modification (A) of this invention. 本発明の変形例（Ａ）に係る空気調和装置における冷媒充填開始運転のフローチャート。The flowchart of the refrigerant | coolant filling start operation | movement in the air conditioning apparatus which concerns on the modification (A) of this invention. 本発明の変形例（Ａ）に係る空気調和装置における冷媒安定運転のフローチャート。The flowchart of the refrigerant | coolant stable operation | movement in the air conditioning apparatus which concerns on the modification (A) of this invention. 本発明の変形例（Ａ）に係る空気調和装置における冷媒充填完了運転のフローチャート。The flowchart of the refrigerant | coolant filling completion operation | movement in the air conditioning apparatus which concerns on the modification (A) of this invention. 本発明の変形例（Ｃ）に係る空気調和装置における冷媒安定運転のフローチャート。The flowchart of the refrigerant | coolant stable driving | operation in the air conditioning apparatus which concerns on the modification (C) of this invention. 本発明の変形例（Ｃ）に係る空気調和装置における冷媒安定運転のフローチャート。The flowchart of the refrigerant | coolant stable driving | operation in the air conditioning apparatus which concerns on the modification (C) of this invention.

符号の説明Explanation of symbols

１ａ 第１室外ユニット（第１熱源ユニット）
１ｂ 第２室外ユニット（第２熱源ユニット）
４ａ 第１室外熱交換器（第１熱源側熱交換器）
４ｂ 第２室外熱交換器（第２熱源側熱交換器）
８ａ 第１圧縮機（第１熱源側過冷却度調節手段）
８ｂ 第２圧縮機（第２熱源側過冷却度調節手段）
９ａ 第１室外ファン（第１熱源側過冷却度調節手段，第１熱源側ファン）
９ｂ 第２室外ファン（第２熱源側過冷却度調節手段，第２熱源側ファン）
１０ 主冷媒回路（冷媒回路）
６２ａ 第１室外側判定部（第１判定部）
６２ｂ 第２室外側判定部（第２判定部）
６８ａ 第１室外側制御部（制御部）
６８ｂ 第２室外側制御部（制御部）
１００ 空気調和装置 1a First outdoor unit (first heat source unit)
1b Second outdoor unit (second heat source unit)
4a First outdoor heat exchanger (first heat source side heat exchanger)
4b Second outdoor heat exchanger (second heat source side heat exchanger)
8a 1st compressor (1st heat source side supercooling degree adjustment means)
8b 2nd compressor (2nd heat source side supercooling degree adjustment means)
9a First outdoor fan (first heat source side supercooling degree adjusting means, first heat source side fan)
9b Second outdoor fan (second heat source side supercooling degree adjusting means, second heat source side fan)
10 Main refrigerant circuit (refrigerant circuit)
62a 1st outdoor side determination part (1st determination part)
62b 2nd outdoor side determination part (2nd determination part)
68a 1st outdoor side control part (control part)
68b 2nd outdoor side control part (control part)
100 Air conditioner

Claims (2)

少なくとも凝縮器として機能する第１熱源側熱交換器（４ａ）と前記第１熱源側熱交換器（４ａ）の出口側における第１過冷却度を調節する第１熱源側過冷却度調節手段（８ａ）とを含む第１熱源ユニット（１ａ）と、
少なくとも凝縮器として機能する第２熱源側熱交換器（４ｂ）と前記第２熱源側熱交換器（４ｂ）の出口側における第２過冷却度を調節する第２熱源側過冷却度調節手段（８ｂ）とを含む第２熱源ユニット（１ｂ）と、
前記第１過冷却度を判定する第１判定部（６２ａ）と、
前記第２過冷却度を判定する第２判定部（６２ｂ）と、
前記第１熱源側熱交換器（４ａ）と前記第２熱源側熱交換器（４ｂ）とを有する冷媒回路（１０）に冷媒が充填されるときに、前記第１過冷却度と前記第２過冷却度との差が小さくなるように前記第１熱源側過冷却度調節手段（８ａ）および前記第２熱源側過冷却度調節手段（８ｂ）を制御し、前記第１過冷却度および前記第２過冷却度のいずれか一方に基づいて前記冷媒回路（１０）内の冷媒量を判断する制御部（６８ａ，６８ｂ）と、を備え、
前記第１熱源側過冷却度調節手段（８ａ）は、前記冷媒回路を流れる冷媒を圧縮する第１圧縮機（８ａ）であり、
前記第２熱源側過冷却度調節手段（８ｂ）は、前記冷媒回路を流れる冷媒を圧縮する第２圧縮機（８ｂ）であり、
前記制御部は、
前記第１過冷却度が前記第２過冷却度よりも大きいときに、前記第２圧縮機（８ｂ）の回転数が前記第１圧縮機（８ａ）の回転数よりも小さくなるように、前記第１圧縮機（８ａ）および前記第２圧縮機（８ｂ）を制御し、
前記第１過冷却度が前記第２過冷却度よりも小さいときに、前記第１圧縮機（８ａ）の回転数が前記第２圧縮機（８ｂ）の回転数よりも小さくなるように、前記第１圧縮機（８ａ）および前記第２圧縮機（８ｂ）を制御する、
空気調和機。 First heat source side subcooling degree adjusting means for adjusting a first subcooling degree at the outlet side of the first heat source side heat exchanger (4a) functioning as at least a condenser and the first heat source side heat exchanger (4a) ( A first heat source unit (1a) comprising:
Second heat source side subcooling degree adjusting means for adjusting a second subcooling degree at the outlet side of the second heat source side heat exchanger (4b) functioning as at least a condenser and the second heat source side heat exchanger (4b) ( A second heat source unit (1b) comprising:
A first determination unit (62a) for determining the first degree of supercooling;
A second determination unit (62b) for determining the second degree of supercooling;
When the refrigerant is filled in the refrigerant circuit (10) having the first heat source side heat exchanger (4a) and the second heat source side heat exchanger (4b), the first supercooling degree and the second The first heat source side subcooling degree adjusting means (8a) and the second heat source side subcooling degree adjusting means (8b) are controlled so that the difference from the supercooling degree is small, A controller (68a, 68b) that determines the amount of refrigerant in the refrigerant circuit (10) based on one of the second degree of subcooling,
The first heat source side supercooling degree adjusting means (8a) is a first compressor (8a) that compresses the refrigerant flowing through the refrigerant circuit,
The second heat source side subcooling degree adjusting means (8b) is a second compressor (8b) that compresses the refrigerant flowing through the refrigerant circuit,
The controller is
When the first subcooling degree is larger than the second subcooling degree, the rotational speed of the second compressor (8b) is smaller than the rotational speed of the first compressor (8a). Controlling the first compressor (8a) and the second compressor (8b);
When the first subcooling degree is smaller than the second subcooling degree, the rotational speed of the first compressor (8a) is smaller than the rotational speed of the second compressor (8b). Controlling the first compressor (8a) and the second compressor (8b);
Air conditioner. 少なくとも凝縮器として機能する第１熱源側熱交換器（４ａ）と前記第１熱源側熱交換器（４ａ）の出口側における第１過冷却度を調節する第１熱源側過冷却度調節手段（９ａ）とを含む第１熱源ユニット（１ａ）と、
少なくとも凝縮器として機能する第２熱源側熱交換器（４ｂ）と前記第２熱源側熱交換器（４ｂ）の出口側における第２過冷却度を調節する第２熱源側過冷却度調節手段（９ｂ）とを含む第２熱源ユニット（１ｂ）と、
前記第１過冷却度を判定する第１判定部（６２ａ）と、
前記第２過冷却度を判定する第２判定部（６２ｂ）と、
前記第１熱源側熱交換器（４ａ）と前記第２熱源側熱交換器（４ｂ）とを有する冷媒回路（１０）に冷媒が充填されるときに、前記第１過冷却度と前記第２過冷却度との差が小さくなるように前記第１熱源側過冷却度調節手段（９ａ）および前記第２熱源側過冷却度調節手段（９ｂ）を制御し、前記第１過冷却度および前記第２過冷却度のいずれか一方に基づいて前記冷媒回路（１０）内の冷媒量を判断する制御部（６８ａ，６８ｂ）と、を備え、
前記第１熱源側過冷却度調節手段（９ａ）は、前記第１熱源側熱交換器に空気を送る第１熱源側ファン（９ａ）であり、
前記第２熱源側過冷却度調節手段（９ｂ）は、前記第２熱源側熱交換器に空気を送る第２熱源側ファン（９ｂ）であり、
前記制御部は、
前記第１過冷却度が前記第２過冷却度よりも大きいときに、前記第２熱源側ファン（９ｂ）の回転数が前記第１熱源側ファン（９ａ）の回転数よりも大きくなるように、前記第１熱源側ファン（９ａ）および前記第２熱源側ファン（９ｂ）を制御し、
前記第１過冷却度が前記第２過冷却度よりも小さいときに、前記第１熱源側ファン（９ａ）の回転数が前記第２熱源側ファン（９ｂ）の回転数よりも大きくなるように、前記第１熱源側ファン（９ａ）および前記第２熱源側ファン（９ｂ）を制御する、
空気調和機。 First heat source side subcooling degree adjusting means for adjusting a first subcooling degree at the outlet side of the first heat source side heat exchanger (4a) functioning as at least a condenser and the first heat source side heat exchanger (4a) ( 9a) a first heat source unit (1a),
Second heat source side subcooling degree adjusting means for adjusting a second subcooling degree at the outlet side of the second heat source side heat exchanger (4b) functioning as at least a condenser and the second heat source side heat exchanger (4b) ( 9b) a second heat source unit (1b),
A first determination unit (62a) for determining the first degree of supercooling;
A second determination unit (62b) for determining the second degree of supercooling;
When the refrigerant is filled in the refrigerant circuit (10) having the first heat source side heat exchanger (4a) and the second heat source side heat exchanger (4b), the first supercooling degree and the second The first heat source side subcooling degree adjusting means (9a) and the second heat source side subcooling degree adjusting means (9b) are controlled so that the difference from the supercooling degree is small, A controller (68a, 68b) that determines the amount of refrigerant in the refrigerant circuit (10) based on one of the second degree of subcooling,
The first heat source side subcooling degree adjusting means (9a) is a first heat source side fan (9a) for sending air to the first heat source side heat exchanger,
The second heat source side subcooling degree adjusting means (9b) is a second heat source side fan (9b) for sending air to the second heat source side heat exchanger,
The controller is
When the first subcooling degree is larger than the second subcooling degree, the rotational speed of the second heat source side fan (9b) is larger than the rotational speed of the first heat source side fan (9a). , Controlling the first heat source side fan (9a) and the second heat source side fan (9b),
When the first supercooling degree is smaller than the second supercooling degree, the rotational speed of the first heat source side fan (9a) is larger than the rotational speed of the second heat source side fan (9b). Controlling the first heat source side fan (9a) and the second heat source side fan (9b),
Air conditioner.
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