WO2020157788A1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
WO2020157788A1
WO2020157788A1 PCT/JP2019/002650 JP2019002650W WO2020157788A1 WO 2020157788 A1 WO2020157788 A1 WO 2020157788A1 JP 2019002650 W JP2019002650 W JP 2019002650W WO 2020157788 A1 WO2020157788 A1 WO 2020157788A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
flow rate
capacity
heat exchange
heat exchanger
Prior art date
Application number
PCT/JP2019/002650
Other languages
French (fr)
Japanese (ja)
Inventor
雄亮 田代
佐藤　正典
早丸　靖英
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to US17/288,999 priority Critical patent/US20210404710A1/en
Priority to JP2020568881A priority patent/JP7086231B2/en
Priority to CN201980088167.9A priority patent/CN113302436A/en
Priority to EP19912296.1A priority patent/EP3919835A4/en
Priority to PCT/JP2019/002650 priority patent/WO2020157788A1/en
Publication of WO2020157788A1 publication Critical patent/WO2020157788A1/en

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Classifications

    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/02—Compression machines, plants or systems, with several condenser circuits arranged in parallel
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor 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
    • F25B2313/025—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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
    • 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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2104—Temperatures of an indoor room or compartment

Definitions

  • the present invention relates to an air conditioner.
  • the operating capacity of the compressor can be increased or decreased by changing the operating frequency by inverter control, which can reduce the air conditioning capacity.
  • the lower limit of the operating frequency of the compressor is set, and it is impossible to continuously perform the air conditioning operation with a very low capacity. Therefore, even when inverter control is used, room temperature may fluctuate due to repeated operation and stop of the compressor.
  • Patent Document 1 discloses a technique of circulating a more appropriate amount of refrigerant in an air conditioner capable of switching between a natural circulation cycle and a forced circulation cycle. However, in this technique, the amount of refrigerant is adjusted appropriately for the circulation system, but the amount of refrigerant is not positively adjusted to adjust the air conditioning capacity.
  • the present invention has been made in view of such problems, and an object thereof is to provide an air conditioner capable of significantly lowering the lower limit capacity during operation as compared with the conventional air conditioner.
  • the present disclosure relates to an air conditioner in which a refrigerant circulates in the order of a compressor, a condenser, an expander, and an evaporator during operation.
  • the condenser includes a first heat exchange section and a second heat exchange section configured to allow the refrigerant to flow in parallel with each other, a flow rate of the refrigerant passing through the first heat exchange section, and a refrigerant passing through the second heat exchange section.
  • a flow rate limiting unit configured to be capable of providing a flow rate difference with the flow rate of
  • the air conditioner includes a control device that controls the compressor and the flow rate limiting unit. The control device uses the frequency of the compressor and the flow rate difference in combination when changing the air conditioning capacity of the air conditioner.
  • the condenser is divided into the first heat exchange section and the second heat exchange section, and the refrigerant is stored in one of the heat exchange sections, so that it is possible to further lower the air conditioning lower limit capacity. ..
  • FIG. 6 is a PH diagram of a refrigeration cycle during operation when the amount of refrigerant is normal. It is a figure showing the flow of the refrigerant of air conditioning operation at the time of low capacity.
  • FIG. 6 is a PH diagram of the refrigeration cycle during operation when the refrigerant is stored in the heat exchanger. It is a flow chart for explaining the refrigerant storage control during the cooling operation. It is the figure which showed the flow of the refrigerant
  • FIG. 1 is a configuration diagram of an air conditioner 1 according to the present embodiment.
  • the air conditioning apparatus 1 includes a compressor 10, an indoor heat exchanger 20, an expansion valve 30, an outdoor heat exchanger 40, and a four-way valve 91.
  • the outdoor heat exchanger 40 includes a first heat exchange section 40A and a second heat exchange section 40B.
  • the first heat exchanging section 40A and the second heat exchanging section 40B are, for example, the outdoor heat exchanger 40 divided into upper and lower parts.
  • the indoor heat exchanger 20 includes a first heat exchange section 20A and a second heat exchange section 20B.
  • the first heat exchanging unit 20A and the second heat exchanging unit 20B are, for example, the indoor heat exchanger 20 divided into two parts, that is, the upper and lower parts or the left and right parts.
  • the outdoor unit 2 includes stop valves 110 and 112, a four-way valve 91, a compressor 10, an outdoor heat exchanger 40, an expansion valve 30, and pipes interconnecting these.
  • the pipe 90 connects the port H of the four-way valve 91 and the stop valve 110 on the gas side.
  • the pipe 92 connects the stop valve 112 on the liquid side and the expansion valve 30.
  • the expansion valve 30 is arranged between the pipe 92 and the pipe 94.
  • the pipe 94 branches into a pipe 94A and a pipe 94B from the middle, and connects the expansion valve 30 to the first heat exchange section 40A and the second heat exchange section 40B.
  • a flow rate adjusting valve 34 is arranged at a branch portion between the pipe 94A and the pipe 94B.
  • the discharge port and the suction port of the compressor 10 are connected to the ports G and E of the four-way valve 91 by pipes 99 and 98, respectively.
  • One end of the pipe 96 is connected to the port F of the four-way valve 91, and the other end branches into pipes 96A and 96B from the middle.
  • the branched pipes 96A and 96B are connected to the first heat exchange unit 40A and the second heat exchange unit 40B, respectively.
  • the air conditioner 1 further includes a control device 200, a refrigerant pressure sensor (not shown), and a refrigerant temperature sensor.
  • the control device 200 includes a communication circuit 201, a processor 202, and a memory 203.
  • the memory 203 includes, for example, a ROM (Read Only Memory), a RAM (Random Access Memory), and a flash memory.
  • the flash memory stores an operating system, application programs, and various data.
  • the processor 202 controls the overall operation of the air conditioning apparatus 1.
  • the functions of the control device 200 are realized by the processor 202 executing the operating system and application programs stored in the memory 203. When executing the application program, various data stored in the memory 203 are referenced.
  • the communication circuit 201 is configured to transmit a control signal to the compressor 10, the four-way valve 91, the expansion valve 30, and the fan 42 flow rate adjusting valve 34 which are control targets.
  • the communication circuit 201 is further configured to transmit a control signal to the fan 22 and the flow rate control valve 32 that are the control targets.
  • the communication circuit 201 may be configured to receive a control signal from a remote controller (not shown) that remotely controls the control device 200.
  • the control device 200 may be divided into a plurality of control units and arranged in the outdoor unit 2, the indoor unit 3, and the remote controller.
  • each of the plurality of control units includes a processor.
  • a plurality of processors cooperate to perform overall control of the air conditioner 1.
  • the compressor 10 is configured to change the operating frequency according to a control signal received from the control device 200.
  • the output of the compressor 10 is adjusted by changing the operating frequency of the compressor 10.
  • Various types of compressors can be adopted, for example, rotary type, reciprocating type, scroll type, screw type, etc. can be adopted.
  • the pipe 96 connects the first heat exchange unit 40A and the second heat exchange unit 40B to the port F of the four-way valve 91.
  • the four-way valve 91 communicates with the pipe 99 and the pipe 96 to which the discharge port of the compressor 10 is connected as shown by the solid line during the cooling operation, and also to the pipe 98 and the pipe 98 to which the suction port of the compressor 10 is connected. Connect with 90.
  • the four-way valve 91 connects the pipe 99 and the pipe 90 to which the discharge port of the compressor 10 is connected with each other as shown by a broken line during the heating operation, and also connects the pipe 98 and the pipe 98 to which the suction port of the compressor 10 is connected. 96 and communication.
  • the indoor unit 3 includes an indoor heat exchanger 20, a fan 22, pipes 101 and 102, and a room temperature sensor 24.
  • One end of the pipe 101 is branched into a pipe 101A and a pipe 101B from the middle, and the pipe 101A and the pipe 101B are connected to the first heat exchange unit 20A and the second heat exchange unit 20B, respectively.
  • the other end of the pipe 101 is connected to the stop valve 110 by an extension pipe 100.
  • the one end of the pipe 102 is branched into a pipe 102A and a pipe 102B from the middle, and is connected to the first heat exchange unit 20A and the second heat exchange unit 20B, respectively.
  • a flow rate adjusting valve 32 is arranged at a branch portion between the pipe 102A and the pipe 102B.
  • the other end of the pipe 102 is connected to the stop valve 112 by an extension pipe 103.
  • the stop valves 110 and 112 are brought into communication with each other when the connection of the refrigerant circuit is completed during construction.
  • the room temperature sensor 24 detects the room temperature and transmits it to the control device 200. It should be noted that the room temperature sensor 24 does not necessarily have to be arranged inside the indoor unit 3, and may be arranged in a remote controller or the like in the same room as the indoor unit 3.
  • FIG. 2 is a diagram showing the flow of the refrigerant in the cooling operation during normal operation.
  • the refrigerant flows in the direction shown by the arrow in FIG.
  • the compressor 10 draws in and compresses the refrigerant from the pipe 90 via the four-way valve 91 and the pipe 98.
  • the compressed refrigerant flows to the pipe 96 via the four-way valve 91.
  • each heat exchanger functions as a condenser or an evaporator will be described together for easy understanding.
  • the outdoor heat exchanger 40 condenses the refrigerant that has flowed into the pipe 96 from the compressor 10 via the four-way valve 91 and flows it into the pipe 94.
  • the outdoor heat exchanger 40 (condenser) is configured so that the refrigerant, which has been discharged from the compressor 10 and has become high-temperature and high-pressure superheated steam, exchanges heat with the outside air to radiate heat. By this heat exchange, the refrigerant is condensed and liquefied near the outlet of the outdoor heat exchanger 40.
  • the fan 42 is provided side by side with the outdoor heat exchanger 40 (condenser), and the control device 200 adjusts the rotation speed of the fan 42 by a control signal. By changing the rotation speed of the fan 42, the amount of heat exchange between the refrigerant and the outside air in the outdoor heat exchanger 40 (condenser) can be adjusted.
  • the expansion valve 30 reduces the pressure of the refrigerant flowing from the outdoor heat exchanger 40 (condenser) to the pipe 94.
  • the depressurized refrigerant flows into the pipe 92.
  • the expansion valve 30 is configured so that the opening degree can be adjusted by a control signal received from the control device 200.
  • the opening degree of the expansion valve 30 is changed to the closing direction, the refrigerant pressure on the outlet side of the expansion valve 30 decreases and the dryness of the refrigerant increases.
  • the opening degree of the expansion valve 30 is changed to the opening direction, the refrigerant pressure at the outlet side of the expansion valve 30 increases and the dryness of the refrigerant decreases.
  • the indoor heat exchanger 20 evaporates the refrigerant flowing from the expansion valve 30 to the pipe 92, the extension pipe 103, and the pipe 102.
  • the evaporated refrigerant flows into the pipe 98 via the pipe 101, the extension pipe 100, the stop valve 110 and the four-way valve 91.
  • the indoor heat exchanger 20 (evaporator) is configured such that the refrigerant decompressed by the expansion valve 30 exchanges heat with the indoor air to absorb heat. By this heat exchange, the refrigerant evaporates and becomes superheated steam near the outlet of the indoor heat exchanger 20.
  • the fan 22 is attached to the indoor heat exchanger 20 (evaporator).
  • the control device 200 adjusts the rotation speed of the fan 22 according to the control signal. By changing the rotation speed of the fan 22, the amount of heat exchange between the refrigerant and the indoor air in the indoor heat exchanger 20 (evaporator) can be adjusted.
  • FIG. 3 is a PH diagram of the refrigeration cycle during operation when the amount of refrigerant is normal.
  • the refrigerant is R32 will be described as an example.
  • points A1 and A2 are compression processing by the compressor 10
  • points A2 and A3 are condensation processing by a condenser
  • points A3 and A4 are decompression by the expansion valve 30.
  • the processing, point A4 to point A1 respectively correspond to the evaporation processing by the evaporator.
  • the refrigerating capacity is a value obtained by multiplying the enthalpy difference dH between the points A1 and A4 by the refrigerant circulation amount Gr per unit time.
  • the refrigerating capacity Q is expressed by the following equation (1), where enthalpy difference dH and refrigerant circulation amount Gr per unit time are given.
  • FIG. 4 is a diagram showing the flow of the refrigerant in the cooling operation when the capacity is low.
  • the state shown in FIG. 4 is different from the state shown in FIG. 2 in that the flow rate adjusting valve 34 limits the flow rate of the second heat exchange section 40B.
  • the fan 42 continues to blow air.
  • the liquefied refrigerant is not discharged while the refrigerant is condensed, so that the liquid refrigerant is stored inside the second heat exchange section 40B.
  • the flow of the refrigerant in the other portions is the same as that in FIG. 2, and therefore the description will not be repeated in FIG.
  • the flow rate adjusting valve 34 is configured not to completely close the pipe 94B side to ensure a minute flow rate.
  • the two-phase refrigerant flows into the expansion valve 30 as the amount of circulating refrigerant decreases, it is preferable to use a valve having a larger diameter than the conventional one as the expansion valve 30.
  • FIG. 5 is a PH diagram of the refrigeration cycle during operation when the refrigerant is stored in the heat exchanger.
  • points B1 and B2 are compression processing by the compressor 10
  • points B2 and B4 are condensation processing by a condenser
  • points B4 and B5 are decompression by the expansion valve 30.
  • Processing, point B5 to point B1 respectively correspond to the evaporation processing by the evaporator.
  • the refrigerating capacity is a value obtained by multiplying the enthalpy difference dH between the points B1 and B5 by the refrigerant circulation amount Gr per unit time.
  • Point B3 in FIG. 5 indicates the state of the outlet of the condenser (second heat exchange section 40B) in FIG.
  • Point B4 in FIG. 5 shows the state of the outlet of the condenser (first heat exchange section 40A) in FIG.
  • the enthalpy Hj after the two have joined together is given by the following equation using the enthalpies H40A and H40B at the outlets of the first heat exchange section 40A and the second heat exchange section 40B and the refrigerant flow rates Gr40A and Gr40B.
  • Hj (H40A*Gr40A+H40B*Gr40B)/(Gr40A+Gr40B) That is, as shown in FIG. 5, when the pipe 94B side of the flow rate adjusting valve 34 is closed and the flow rate is small, the enthalpy Hj after the merging is substantially equal to the enthalpy H40A on the pipe 94A side with a large refrigerant flow rate. Further, the enthalpy at the point B4, that is, the enthalpy at the point B5 at the evaporator inlet can be adjusted by the flow rate of the refrigerant flowing to the pipe 94B side.
  • FIG. 6 is a flowchart for explaining refrigerant storage control during the cooling operation.
  • control device 200 determines whether the room temperature detected by room temperature sensor 24 is lower than the set temperature set by a remote controller or the like.
  • the control device 200 determines in step S2 whether the operating frequency f of the compressor 10 is higher than the lower limit frequency fmin. If f>fmin (YES in S2), the control device 200 reduces the operating frequency f of the compressor 10 by ⁇ 2 in step S3 to reduce the cooling capacity of the air conditioner 1.
  • step S4 the control device 200 determines whether or not the room temperature detected by the room temperature sensor 24 is lower than the set temperature set by the remote controller or the like. If the room temperature is less than the set temperature (YES in S4), the process returns to step S2. On the other hand, when the indoor temperature ⁇ the set temperature (NO in S4), in step S5, the control device 200 increases the operating frequency f of the compressor 10 by ⁇ 1 and increases the cooling capacity of the air conditioner 1.
  • steps S1 to S5 are processes for adjusting the operating frequency of the compressor 10 by inverter control so that the air conditioning capacity of the air conditioner 1 in operation matches the air conditioning load.
  • the process proceeds to the process of adjusting the refrigerant circulation amount after step S6. ..
  • step S6 the operation of storing the refrigerant in the outdoor heat exchanger 40 is started.
  • the control device 200 sets the opening degree L of the flow rate adjusting valve 34 that determines the flow rate of the second heat exchange section 40B to the maximum opening degree Lmax.
  • the maximum opening Lmax is the opening L in the initial state.
  • control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is lower than the set temperature set by the remote controller or the like.
  • step S8 the control device 200 narrows the opening degree L of the flow rate adjusting valve 34 by ⁇ 3 to store the liquid refrigerant in the second heat exchange section 40B. Increase the amount. As a result, the refrigerant circulation amount Gr decreases. Then, in step S9, the control device 200 determines whether or not the opening L of the flow rate adjusting valve 34 is the lower limit opening Lmin.
  • step S7 When the opening L of the flow rate adjusting valve 34 is not the lower limit opening Lmin (NO in S9), the process of step S7 is executed again. If the indoor temperature is equal to or higher than the set temperature in step S7 (NO in S7), it is considered that there is no need to further reduce the cooling capacity and the air conditioning load and the air conditioning capacity are in balance, so that the flow rate adjustment valve 34 is opened in step S10. Control ends, and the process returns to the main routine in step S11.
  • the control device 200 stops the compressor 10 in step S12. , Prevent the room temperature from dropping too low.
  • FIG. 7 is the figure which showed the flow of the refrigerant
  • the refrigerant flows in the direction shown by the arrow in FIG. 7.
  • the compressor 10 draws in and compresses the refrigerant from the pipe 96 via the four-way valve 91 and the pipe 98.
  • the compressed refrigerant flows to the pipe 90 via the four-way valve 91.
  • each heat exchanger functions as a condenser or an evaporator will be described together for easy understanding.
  • the indoor heat exchanger 20 condenses the refrigerant that has flowed into the pipe 101 from the compressor 10 via the four-way valve 91, the pipe 90, and the extension pipe 100 to flow into the pipe 102.
  • the indoor heat exchanger 20 (condenser) is configured so that the refrigerant, which has been discharged from the compressor 10 and has become high-temperature and high-pressure superheated steam, exchanges heat with the indoor air to radiate heat. By this heat exchange, the refrigerant is condensed and liquefied near the outlet of the indoor heat exchanger 20.
  • the fan 22 is attached to the indoor heat exchanger 20 (condenser), and the control device 200 adjusts the rotation speed of the fan 22 by a control signal. By changing the rotation speed of the fan 22, the amount of heat exchange between the refrigerant and the indoor air in the indoor heat exchanger 20 (condenser) can be adjusted.
  • the expansion valve 30 reduces the pressure of the refrigerant flowing from the indoor heat exchanger 20 (condenser) to the pipe 92 via the pipe 102 and the extension pipe 103.
  • the depressurized refrigerant flows to the pipe 94.
  • the expansion valve 30 is configured so that the opening degree can be adjusted by a control signal received from the control device 200.
  • the opening degree of the expansion valve 30 is changed to the closing direction, the refrigerant pressure on the outlet side of the expansion valve 30 decreases and the dryness of the refrigerant increases.
  • the opening degree of the expansion valve 30 is changed to the opening direction, the refrigerant pressure at the outlet side of the expansion valve 30 increases and the dryness of the refrigerant decreases.
  • the outdoor heat exchanger 40 evaporates the refrigerant flowing from the expansion valve 30 to the pipe 94.
  • the evaporated refrigerant flows to the pipe 98 via the pipe 96 and the four-way valve 91.
  • the outdoor heat exchanger 40 (evaporator) is configured such that the refrigerant decompressed by the expansion valve 30 exchanges heat with the outside air and absorbs heat. By this heat exchange, the refrigerant evaporates and becomes superheated steam near the outlet of the outdoor heat exchanger 40.
  • the fan 42 is attached to the outdoor heat exchanger 40 (evaporator).
  • the control device 200 adjusts the rotation speed of the fan 42 according to the control signal. By changing the rotation speed of the fan 42, the amount of heat exchange between the refrigerant and the outside air in the outdoor heat exchanger 40 (evaporator) can be adjusted.
  • FIG. 8 is a diagram showing the flow of the refrigerant in the heating operation when the capacity is low.
  • the state shown in FIG. 8 differs from the state shown in FIG. 7 in that the flow rate adjusting valve 32 limits the flow rate of the second heat exchange section 20B.
  • the fan 22 continues to blow air.
  • the liquefied refrigerant is not discharged while the refrigerant is condensed, so that the liquid refrigerant is stored inside the second heat exchange section 20B.
  • the flow of the refrigerant in the other parts is the same as that in FIG. 7, and therefore the description will not be repeated in FIG.
  • the flow rate adjusting valve 32 is configured not to completely close the pipe 102B side to ensure a minute flow rate.
  • the PH diagram corresponding to FIG. 7 and the PH diagram corresponding to FIG. 8 differ from FIGS. 3 and 5 in the condensation temperature and the evaporation temperature, but when the refrigerant is R32, Regarding the point that the enthalpy difference is smaller in the operation shown in FIG. 8 than in FIG. 7, there is a tendency similar to the relationship in FIGS. 3 and 5.
  • the condensing capacity can be kept smaller than before even in the case of heating.
  • FIG. 9 is a flowchart for explaining refrigerant storage control during heating operation.
  • control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is higher than the set temperature set by a remote controller or the like.
  • the control device 200 determines in step S12 whether the operating frequency f of the compressor 10 is higher than the lower limit frequency fmin. When f>fmin (YES in S12), the control device 200 reduces the operating frequency f of the compressor 10 by ⁇ 2 in step S13 to reduce the heating capacity of the air conditioner 1.
  • step S14 the control device 200 determines whether or not the room temperature detected by the room temperature sensor 24 is higher than the set temperature set by the remote controller or the like. If the room temperature>the set temperature (YES in S14), the process returns to step S12. On the other hand, when the indoor temperature ⁇ the set temperature (NO in S14), the control device 200 increases the operating frequency f of the compressor 10 by ⁇ 1 and increases the heating capacity of the air conditioning device 1 in step S15.
  • steps S11 to S15 are processes for adjusting the operating frequency of the compressor 10 by inverter control so that the air conditioning capacity of the air conditioner 1 in operation matches the air conditioning load.
  • the operating frequency f becomes equal to or lower than the lower limit value fmin (NO in S12)
  • it is impossible to suppress the air conditioning capacity by further lowering the operating frequency so that the process proceeds to the process of adjusting the refrigerant circulation amount after step S16. ..
  • step S16 the operation of storing the refrigerant in the indoor heat exchanger 20 is started.
  • the control device 200 sets the opening L of the flow rate adjusting valve 32 that determines the flow rate of the second heat exchange unit 20B to the maximum opening Lmax.
  • the maximum opening Lmax is the opening L in the initial state.
  • control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is higher than the set temperature set by the remote controller or the like.
  • step S18 the control device 200 narrows the opening degree L of the flow rate adjusting valve 32 by ⁇ 3 to store the liquid refrigerant in the second heat exchange section 20B. Increase the amount. Then, in step S19, the control device 200 determines whether or not the opening L of the flow rate adjusting valve 32 is the lower limit opening Lmin.
  • step S17 When the opening L of the flow rate adjusting valve 32 is not the lower limit opening Lmin (NO in S19), the process of step S17 is executed again. If the indoor temperature is equal to or lower than the set temperature in step S17 (NO in S17), it is considered that there is no need to further reduce the heating capacity, and the air conditioning load and the air conditioning capacity are in balance, so the flow control valve 32 is opened in step S20. Control is completed, and the process returns to the main routine in step S21.
  • the control device 200 stops the compressor 10 in step S22. , Prevent the room temperature from rising too high.
  • FIG. 10 is a diagram showing the lower limit capabilities of the case where the control of the present embodiment is performed and the case where the normal control is performed, in comparison.
  • the rated capacity is set to 100%
  • the lower limit capacity when only the frequency control of the compressor 10 is executed is 15%
  • the lower limit capacity when controlling the refrigerant storage amount was 10%.
  • the lower limit capacity of the air conditioner of the present embodiment can be reduced to 66.7% compared to the normal machine.
  • FIG. 11 is a diagram showing a modified example in which the flow rate adjusting valve is modified.
  • the flow rate adjusting valves 32 and 34 in FIG. 1 are changed to flow rate adjusting units 32A and 34A, respectively.
  • the flow rate adjusting valves 32 and 34 are specifically intended to be three-way valves having a flow rate adjusting function.
  • the amount of circulating refrigerant can be adjusted by slightly opening the three-way valve, so the adjustment range of the air-conditioning capacity can be increased by adjusting the compressor frequency and the three-way valve ( The lower limit capacity can be further reduced).
  • the refrigerant is a compressor 10, a condenser (outdoor heat exchanger 40/indoor heat exchanger 20), an expansion device (expansion valve 30), and an evaporator (indoor heat exchanger 20/outdoor heat exchange).
  • the air conditioner 1 that circulates in the order of the device 40).
  • the condenser (outdoor heat exchanger 40/indoor heat exchanger 20) includes a first heat exchange section 40A/20A and a second heat exchange section 40B/20B configured to allow the refrigerant to flow in parallel with each other.
  • a flow rate restricting unit (flow rate adjusting valve 34/32) configured to be able to make a flow rate difference between the flow rate of the refrigerant passing through the heat exchange section 40A/20A and the flow rate of the refrigerant passing through the second heat exchange section 40B/20B. ) And.
  • the air conditioner 1 includes a control device 200 that controls the compressor 10 and the flow rate limiting unit (flow rate adjusting valve 34/32). The control device 200 uses the frequency and the flow rate difference of the compressor 10 in combination when changing the air conditioning capacity of the air conditioner 1.
  • the expansion device corresponds to the expansion valve 30, but is not necessarily a valve and may be, for example, a capillary tube.
  • the refrigerant circulation amount can be increased or decreased without using a refrigerant container such as an accumulator and a receiver, and the lower limit capacity can be used. Can be kept small. Further, even when using a refrigerant container such as an accumulator and a receiver, a small size is sufficient.
  • the control device 200 reduces the frequency f of the compressor 10 when changing (a) the air conditioning capacity from the first capacity to the second capacity that is smaller than the first capacity, and (b) sets the air conditioning capacity to the first capacity.
  • the flow rate of the refrigerant passing through the second heat exchange section 40B/20B is changed by the flow rate restriction section (flow rate adjusting valve 34/32) to the first heat exchange section.
  • Changing the operating frequency of the compressor 10 to lower the air conditioning capacity has better response than lowering the air conditioning capacity by increasing the refrigerant storage amount by the flow rate limiting unit. Therefore, when lowering the air conditioning capacity, it is better to lower the air conditioning capacity by lowering the operating frequency first, and at the same time or after that, increasing the refrigerant storage amount by the flow rate limiting unit to lower the air conditioning capacity, and the fluctuation of room temperature can be small. ..
  • the air conditioner 1 further includes a four-way valve 91 that switches the circulation direction of the refrigerant between cooling operation and heating operation.
  • the indoor heat exchanger 20 and the outdoor heat exchanger 40 are both divided into two.
  • the outdoor heat exchanger 40 functions as a condenser during the cooling operation, and the indoor heat exchanger 20 functions as a condenser during the heating operation.
  • one of the flow paths of the flow rate adjusting valve 34 arranged on the outdoor heat exchanger 40 side is closed. Since the fan 42 of the outdoor heat exchanger 40 is rotating, the refrigerant is stored in the heat exchanger on the closed side (the second heat exchange unit 40B in FIG. 4).
  • one of the flow paths of the flow rate adjusting valve 32 arranged on the indoor heat exchanger 20 side is closed. Since the fan of the indoor heat exchanger 20 is rotating, the refrigerant is stored in the heat exchanger on the closed side (the second heat exchange section 20B in FIG. 8).
  • one of the features is that the rotation of the condenser fan is maintained in order to positively let the refrigerant lie in the heat exchanger in order to reduce the air conditioning capacity.
  • the fan of the condenser in the outdoor heat exchanger, in the normal configuration, is one fan shared by the two divided heat exchange sections.
  • the fan of the condenser In the indoor heat exchanger, the fan of the condenser is one fan that is common to the line flow fan, but in the case of a configuration having two propeller fans on the left and right, both fans will rotate.

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  • Air Conditioning Control Device (AREA)

Abstract

The present invention provides an air conditioner (1), wherein during operation, a refrigerant circulates through a compressor (10), a condenser (40/20), an expansion device (30), and an evaporator (20/ 40) in the stated order. The condenser (40/20) includes a first heat exchanger unit (40A/20A) and a second heat exchanger unit (40B/20B) that are configured to channel the refrigerant parallel to each other, and a flow-rate-restricting unit (34/32) configured so as to be capable of producing a flow rate difference between the flow rate of the refrigerant passing through the first heat exchanger unit (40A/20A) and the flow rate of the refrigerant passing through the second heat exchanger unit (40B/20B). The air conditioner (1) comprises a control device (200) for controlling the compressor (10) and the flow-rate-restricting unit (34/32). When changing the air conditioning performance of the air conditioner (1), the control device (200) uses, in combination, the frequency of the compressor (10) and the flow rate difference of the refrigerant passing through the two heat exchanger units.

Description

空気調和装置Air conditioner
　この発明は、空気調和装置に関する。 The present invention relates to an air conditioner.
　近年、高気密高断熱住宅の普及により、一旦快適な温度になった部屋を快適に維持するための空調負荷は非常に小さくて済むようになった。一方で、空調のオンオフ制御によって室温を適温に維持しようとすると、どうしても室温が変動する。室温の変動幅を小さく抑えるためには、小さな空調負荷と均衡する低い空調能力で空気調和装置を連続的に運転することが必要である。 In recent years, the spread of airtight and highly insulated houses has made it possible to reduce the air-conditioning load to maintain a comfortable temperature in a room. On the other hand, if an attempt is made to maintain the room temperature at an appropriate temperature by controlling the on/off of the air conditioning, the room temperature will fluctuate. In order to reduce the fluctuation range of room temperature to a small level, it is necessary to continuously operate the air conditioner with a low air conditioning capacity that balances a small air conditioning load.
　したがって、空気調和装置は、室温を早期に適温に到達させるための定格能力に加えて運転時の下限能力をより低下させることが必要となってきた。 Therefore, it has become necessary for the air conditioner to lower the lower limit capacity during operation in addition to the rated capacity for early reaching room temperature to an appropriate temperature.
特許第５６３９６６４号公報Japanese Patent No. 5639664.
　圧縮機の運転能力は、インバータ制御によって運転周波数を変えることによって増減させることができ、これによって空調能力を下げることができる。しかし、圧縮機は、運転周波数の下限が定められており、ごく低い能力の空調運転を連続して行なうことができない。したがって、インバータ制御を用いる場合であっても、圧縮機の運転と停止を繰返すことによって室温に変動が生じてしまうことがある。 The operating capacity of the compressor can be increased or decreased by changing the operating frequency by inverter control, which can reduce the air conditioning capacity. However, the lower limit of the operating frequency of the compressor is set, and it is impossible to continuously perform the air conditioning operation with a very low capacity. Therefore, even when inverter control is used, room temperature may fluctuate due to repeated operation and stop of the compressor.
　一方、空調能力の調節のために、冷凍サイクル中を循環する冷媒量を変更することが考えられる。特許第５６３９６６４号公報（特許文献１）には、自然循環サイクルと強制循環サイクルとを切替えることが可能な空気調和装置において、より適正な冷媒量を循環させる技術が開示されている。しかし、この技術では循環方式に対して適正な冷媒量に調整を行なうが、空調能力の調節のために積極的に冷媒量を調整するものではない。 On the other hand, it is possible to change the amount of refrigerant circulating in the refrigeration cycle in order to adjust the air conditioning capacity. Japanese Patent No. 5639664 (Patent Document 1) discloses a technique of circulating a more appropriate amount of refrigerant in an air conditioner capable of switching between a natural circulation cycle and a forced circulation cycle. However, in this technique, the amount of refrigerant is adjusted appropriately for the circulation system, but the amount of refrigerant is not positively adjusted to adjust the air conditioning capacity.
　この発明は、かかる課題に鑑みてなされたものであり、その目的は、運転時の下限能力を従来よりも大幅に下げることが可能な空気調和装置を提供することである。 The present invention has been made in view of such problems, and an object thereof is to provide an air conditioner capable of significantly lowering the lower limit capacity during operation as compared with the conventional air conditioner.
　本開示は、運転中に、冷媒が圧縮機、凝縮器、膨張装置および蒸発器の順に循環する空気調和装置に関する。凝縮器は、冷媒が互いに並行して流れるように構成された第１熱交換部および第２熱交換部と、第１熱交換部を通過する冷媒の流量と第２熱交換部を通過する冷媒の流量とに流量差をつけることが可能に構成された流量制限部とを含む。空気調和装置は、圧縮機と流量制限部とを制御する制御装置を備える。制御装置は、空気調和装置の空調能力を変更する場合に、圧縮機の周波数と流量差とを組み合わせて使用する。 The present disclosure relates to an air conditioner in which a refrigerant circulates in the order of a compressor, a condenser, an expander, and an evaporator during operation. The condenser includes a first heat exchange section and a second heat exchange section configured to allow the refrigerant to flow in parallel with each other, a flow rate of the refrigerant passing through the first heat exchange section, and a refrigerant passing through the second heat exchange section. And a flow rate limiting unit configured to be capable of providing a flow rate difference with the flow rate of The air conditioner includes a control device that controls the compressor and the flow rate limiting unit. The control device uses the frequency of the compressor and the flow rate difference in combination when changing the air conditioning capacity of the air conditioner.
　本開示に係る空気調和装置は、凝縮器を第１熱交換部と第２熱交換部に分け、一方の熱交換部に冷媒を貯留するので、空調下限能力をより低下させることが可能となる。 In the air conditioner according to the present disclosure, the condenser is divided into the first heat exchange section and the second heat exchange section, and the refrigerant is stored in one of the heat exchange sections, so that it is possible to further lower the air conditioning lower limit capacity. ..
本実施の形態に従う空気調和装置１の構成図である。It is a block diagram of the air conditioning apparatus 1 according to this Embodiment. 通常時の冷房運転の冷媒の流れを示した図である。It is the figure which showed the flow of the refrigerant|coolant of the cooling operation at the time of normal. 冷媒量が通常である場合の運転時の冷凍サイクルのＰ－Ｈ線図である。FIG. 6 is a PH diagram of a refrigeration cycle during operation when the amount of refrigerant is normal. 低能力時の冷房運転の冷媒の流れを示した図である。It is a figure showing the flow of the refrigerant of air conditioning operation at the time of low capacity. 冷媒を熱交換器内に貯留させた場合の運転時の冷凍サイクルのＰ－Ｈ線図である。FIG. 6 is a PH diagram of the refrigeration cycle during operation when the refrigerant is stored in the heat exchanger. 冷房運転中における冷媒貯留制御を説明するためのフローチャートである。It is a flow chart for explaining the refrigerant storage control during the cooling operation. 通常時の暖房運転の冷媒の流れを示した図である。It is the figure which showed the flow of the refrigerant|coolant of heating operation at the time of normal. 低能力時の暖房運転の冷媒の流れを示した図である。It is a figure showing the flow of the refrigerant of heating operation at the time of low capacity. 暖房運転中における冷媒貯留制御を説明するためのフローチャートである。It is a flow chart for explaining refrigerant storage control in heating operation. 本実施の形態の制御を行なった場合と通常の制御を行なった場合の下限能力を対比して示す図である。It is a figure which shows in comparison the lower limit capability when performing control of this Embodiment, and when performing normal control. 流量調整弁を変形した変形例を示す図である。It is a figure which shows the modification which deformed the flow control valve.
　以下、本発明の実施の形態について、図面を参照しながら詳細に説明する。以下では、複数の実施の形態について説明するが、各実施の形態で説明された構成を適宜組み合わせることは出願当初から予定されている。なお、図中同一又は相当部分には同一符号を付してその説明は繰返さない。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Hereinafter, a plurality of embodiments will be described, but it is planned from the beginning of the application to appropriately combine the configurations described in the embodiments. In the drawings, the same or corresponding parts will be denoted by the same reference symbols and description thereof will not be repeated.
　図１は、本実施の形態に従う空気調和装置１の構成図である。図１を参照して、空気調和装置１は、圧縮機１０と、室内熱交換器２０と、膨張弁３０と、室外熱交換器４０と、四方弁９１とを含む。室外熱交換器４０は、第１熱交換部４０Ａと、第２熱交換部４０Ｂとを含む。第１熱交換部４０Ａと、第２熱交換部４０Ｂとは、たとえば、上下に室外熱交換器４０が２分割されたものである。室内熱交換器２０は、第１熱交換部２０Ａと、第２熱交換部２０Ｂとを含む。第１熱交換部２０Ａと、第２熱交換部２０Ｂとは、たとえば、上下または左右に室内熱交換器２０が２分割されたものである。 FIG. 1 is a configuration diagram of an air conditioner 1 according to the present embodiment. With reference to FIG. 1, the air conditioning apparatus 1 includes a compressor 10, an indoor heat exchanger 20, an expansion valve 30, an outdoor heat exchanger 40, and a four-way valve 91. The outdoor heat exchanger 40 includes a first heat exchange section 40A and a second heat exchange section 40B. The first heat exchanging section 40A and the second heat exchanging section 40B are, for example, the outdoor heat exchanger 40 divided into upper and lower parts. The indoor heat exchanger 20 includes a first heat exchange section 20A and a second heat exchange section 20B. The first heat exchanging unit 20A and the second heat exchanging unit 20B are, for example, the indoor heat exchanger 20 divided into two parts, that is, the upper and lower parts or the left and right parts.
　室外機２は、ストップバルブ１１０，１１２と、四方弁９１と、圧縮機１０と、室外熱交換器４０と、膨張弁３０と、これらを相互に接続する管とを含む。 The outdoor unit 2 includes stop valves 110 and 112, a four-way valve 91, a compressor 10, an outdoor heat exchanger 40, an expansion valve 30, and pipes interconnecting these.
　管９０は、四方弁９１のポートＨとガス側のストップバルブ１１０とを接続する。管９２は、液側のストップバルブ１１２と膨張弁３０とを接続する。膨張弁３０は、管９２と管９４との間に配置される。管９４は、途中から管９４Ａと管９４Ｂに分岐しており、膨張弁３０と第１熱交換部４０Ａおよび第２熱交換部４０Ｂとを接続する。管９４Ａと管９４Ｂの分岐部には、流量調整弁３４が配置される。 The pipe 90 connects the port H of the four-way valve 91 and the stop valve 110 on the gas side. The pipe 92 connects the stop valve 112 on the liquid side and the expansion valve 30. The expansion valve 30 is arranged between the pipe 92 and the pipe 94. The pipe 94 branches into a pipe 94A and a pipe 94B from the middle, and connects the expansion valve 30 to the first heat exchange section 40A and the second heat exchange section 40B. A flow rate adjusting valve 34 is arranged at a branch portion between the pipe 94A and the pipe 94B.
　圧縮機１０の吐出口と吸入口とは、それぞれ管９９，９８によって、四方弁９１のポートＧ，Ｅに接続される。管９６は、一端が四方弁９１のポートＦに接続され、他端は途中から管９６Ａ，９６Ｂに分岐する。分岐した管９６Ａ，９６Ｂは、それぞれ第１熱交換部４０Ａ、第２熱交換部４０Ｂに接続される。 The discharge port and the suction port of the compressor 10 are connected to the ports G and E of the four-way valve 91 by pipes 99 and 98, respectively. One end of the pipe 96 is connected to the port F of the four-way valve 91, and the other end branches into pipes 96A and 96B from the middle. The branched pipes 96A and 96B are connected to the first heat exchange unit 40A and the second heat exchange unit 40B, respectively.
　空気調和装置１は、さらに、制御装置２００と、図示しない冷媒圧力センサと、冷媒温度センサとを含む。 The air conditioner 1 further includes a control device 200, a refrigerant pressure sensor (not shown), and a refrigerant temperature sensor.
　制御装置２００は、通信回路２０１と、プロセッサ２０２と、メモリ２０３とを含む。
　メモリ２０３は、たとえば、ＲＯＭ（Read　Only　Memory）と、ＲＡＭ（Random　Access　Memory）と、フラッシュメモリとを含んで構成される。なお、フラッシュメモリには、オペレーティングシステム、アプリケーションプログラム、各種のデータが記憶される。 The control device 200 includes a communication circuit 201, a processor 202, and a memory 203.
The memory 203 includes, for example, a ROM (Read Only Memory), a RAM (Random Access Memory), and a flash memory. The flash memory stores an operating system, application programs, and various data.
　プロセッサ２０２は、空気調和装置１の全体の動作を制御する。なお、制御装置２００の機能は、プロセッサ２０２がメモリ２０３に記憶されたオペレーティングシステムおよびアプリケーションプログラムを実行することにより実現される。なお、アプリケーションプログラムの実行の際には、メモリ２０３に記憶されている各種のデータが参照される。通信回路２０１は、制御対象とする圧縮機１０、四方弁９１、膨張弁３０、ファン４２流量調整弁３４に対して制御信号を送信するように構成される。通信回路２０１は、さらに、制御対象とするファン２２、流量調整弁３２に対して制御信号を送信するように構成される。 The processor 202 controls the overall operation of the air conditioning apparatus 1. The functions of the control device 200 are realized by the processor 202 executing the operating system and application programs stored in the memory 203. When executing the application program, various data stored in the memory 203 are referenced. The communication circuit 201 is configured to transmit a control signal to the compressor 10, the four-way valve 91, the expansion valve 30, and the fan 42 flow rate adjusting valve 34 which are control targets. The communication circuit 201 is further configured to transmit a control signal to the fan 22 and the flow rate control valve 32 that are the control targets.
　なお、通信回路２０１は、制御装置２００を遠隔制御するリモコン（図示せず）からの制御信号を受信するように構成しても良い。 Note that the communication circuit 201 may be configured to receive a control signal from a remote controller (not shown) that remotely controls the control device 200.
　制御装置２００は、室外機２、室内機３、およびリモコンに、複数の制御部に分割されて配置されていても良い。制御装置が複数の制御部に分割されている場合には、複数の制御部の各々にプロセッサが含まれる。このような場合には、複数のプロセッサが連携して空気調和装置１の全体制御を行なう。 The control device 200 may be divided into a plurality of control units and arranged in the outdoor unit 2, the indoor unit 3, and the remote controller. When the control device is divided into a plurality of control units, each of the plurality of control units includes a processor. In such a case, a plurality of processors cooperate to perform overall control of the air conditioner 1.
　圧縮機１０は、制御装置２００から受ける制御信号によって運転周波数を変更するように構成される。圧縮機１０の運転周波数を変更することにより圧縮機１０の出力が調整される。圧縮機１０には種々のタイプを採用可能であり、たとえば、ロータリータイプ、往復タイプ、スクロールタイプ、スクリュータイプ等のものを採用し得る。 The compressor 10 is configured to change the operating frequency according to a control signal received from the control device 200. The output of the compressor 10 is adjusted by changing the operating frequency of the compressor 10. Various types of compressors can be adopted, for example, rotary type, reciprocating type, scroll type, screw type, etc. can be adopted.
　図１に示す構成では、管９６は、第１熱交換部４０Ａおよび第２熱交換部４０Ｂを四方弁９１のポートＦに接続する。四方弁９１は、冷房運転のときは実線で示すように圧縮機１０の吐出口が接続された管９９と管９６とを連通させるとともに、圧縮機１０の吸入口が接続された管９８と管９０とを連通させる。四方弁９１は、暖房運転のときは破線で示すように圧縮機１０の吐出口が接続された管９９と管９０とを連通させるとともに、圧縮機１０の吸入口が接続された管９８と管９６とを連通させる。 In the configuration shown in FIG. 1, the pipe 96 connects the first heat exchange unit 40A and the second heat exchange unit 40B to the port F of the four-way valve 91. The four-way valve 91 communicates with the pipe 99 and the pipe 96 to which the discharge port of the compressor 10 is connected as shown by the solid line during the cooling operation, and also to the pipe 98 and the pipe 98 to which the suction port of the compressor 10 is connected. Connect with 90. The four-way valve 91 connects the pipe 99 and the pipe 90 to which the discharge port of the compressor 10 is connected with each other as shown by a broken line during the heating operation, and also connects the pipe 98 and the pipe 98 to which the suction port of the compressor 10 is connected. 96 and communication.
　室内機３は、室内熱交換器２０と、ファン２２と、管１０１，１０２と、室温センサ２４とを含む。 The indoor unit 3 includes an indoor heat exchanger 20, a fan 22, pipes 101 and 102, and a room temperature sensor 24.
　管１０１の一端は、途中から管１０１Ａと管１０１Ｂに分岐しており、管１０１Ａと管１０１Ｂは、第１熱交換部２０Ａおよび第２熱交換部２０Ｂにそれぞれ接続される。管１０１の他端は、延長配管１００によって、ストップバルブ１１０に接続される。 One end of the pipe 101 is branched into a pipe 101A and a pipe 101B from the middle, and the pipe 101A and the pipe 101B are connected to the first heat exchange unit 20A and the second heat exchange unit 20B, respectively. The other end of the pipe 101 is connected to the stop valve 110 by an extension pipe 100.
　管１０２の一端は、途中から管１０２Ａと管１０２Ｂに分岐しており第１熱交換部２０Ａおよび第２熱交換部２０Ｂにそれぞれ接続される。管１０２Ａと管１０２Ｂの分岐部には、流量調整弁３２が配置される。管１０２の他端は、延長配管１０３によって、ストップバルブ１１２に接続される。 The one end of the pipe 102 is branched into a pipe 102A and a pipe 102B from the middle, and is connected to the first heat exchange unit 20A and the second heat exchange unit 20B, respectively. A flow rate adjusting valve 32 is arranged at a branch portion between the pipe 102A and the pipe 102B. The other end of the pipe 102 is connected to the stop valve 112 by an extension pipe 103.
　ストップバルブ１１０，１１２は、施工時に冷媒回路の接続が完了すると、各々連通状態とされる。 The stop valves 110 and 112 are brought into communication with each other when the connection of the refrigerant circuit is completed during construction.
　室温センサ２４は、室温を検出して制御装置２００に送信する。なお、室温センサ２４は、必ずしも室内機３の内部に配置されていなくても良く、室内機３と同じ部屋にあるリモコンなどに配置されていても良い。 The room temperature sensor 24 detects the room temperature and transmits it to the control device 200. It should be noted that the room temperature sensor 24 does not necessarily have to be arranged inside the indoor unit 3, and may be arranged in a remote controller or the like in the same room as the indoor unit 3.
　（冷房運転中の冷媒量制御）
　まず、冷房運転の基本的な動作について説明する。図２は、通常時の冷房運転の冷媒の流れを示した図である。冷房運転では、図２に矢印で示した向きに冷媒が流れる。圧縮機１０は管９０から四方弁９１および管９８を経由して冷媒を吸入し、圧縮する。圧縮された冷媒は四方弁９１を経由して管９６へ流れる。以下、各熱交換器が凝縮器として働くのか蒸発器として働くのかを、理解の容易のために併記する。 (Control of refrigerant amount during cooling operation)
First, the basic operation of the cooling operation will be described. FIG. 2 is a diagram showing the flow of the refrigerant in the cooling operation during normal operation. In the cooling operation, the refrigerant flows in the direction shown by the arrow in FIG. The compressor 10 draws in and compresses the refrigerant from the pipe 90 via the four-way valve 91 and the pipe 98. The compressed refrigerant flows to the pipe 96 via the four-way valve 91. Hereinafter, whether each heat exchanger functions as a condenser or an evaporator will be described together for easy understanding.
　室外熱交換器４０（凝縮器）は、圧縮機１０から四方弁９１を経由して管９６に流入した冷媒を凝縮して管９４へ流す。室外熱交換器４０（凝縮器）は、圧縮機１０から吐出された高温高圧の過熱蒸気となった冷媒が外気と熱交換して放熱を行なうように構成される。この熱交換により、冷媒は凝縮されて室外熱交換器４０の出口付近で液化する。ファン４２が、室外熱交換器４０（凝縮器）に併設され、制御装置２００は制御信号によってファン４２の回転速度を調整する。ファン４２の回転速度を変更することにより、室外熱交換器４０（凝縮器）における冷媒と外気との熱交換量を調整することができる。 The outdoor heat exchanger 40 (condenser) condenses the refrigerant that has flowed into the pipe 96 from the compressor 10 via the four-way valve 91 and flows it into the pipe 94. The outdoor heat exchanger 40 (condenser) is configured so that the refrigerant, which has been discharged from the compressor 10 and has become high-temperature and high-pressure superheated steam, exchanges heat with the outside air to radiate heat. By this heat exchange, the refrigerant is condensed and liquefied near the outlet of the outdoor heat exchanger 40. The fan 42 is provided side by side with the outdoor heat exchanger 40 (condenser), and the control device 200 adjusts the rotation speed of the fan 42 by a control signal. By changing the rotation speed of the fan 42, the amount of heat exchange between the refrigerant and the outside air in the outdoor heat exchanger 40 (condenser) can be adjusted.
　膨張弁３０は、室外熱交換器４０（凝縮器）から管９４へ流れた冷媒を減圧する。減圧された冷媒は管９２へ流れる。膨張弁３０は、制御装置２００から受ける制御信号によって開度を調整可能に構成される。膨張弁３０の開度を閉方向に変化させると、膨張弁３０出口側の冷媒圧力は低下し、冷媒の乾き度は上昇する。一方、膨張弁３０の開度を開方向に変化させると、膨張弁３０出口側の冷媒圧力は上昇し、冷媒の乾き度は低下する。 The expansion valve 30 reduces the pressure of the refrigerant flowing from the outdoor heat exchanger 40 (condenser) to the pipe 94. The depressurized refrigerant flows into the pipe 92. The expansion valve 30 is configured so that the opening degree can be adjusted by a control signal received from the control device 200. When the opening degree of the expansion valve 30 is changed to the closing direction, the refrigerant pressure on the outlet side of the expansion valve 30 decreases and the dryness of the refrigerant increases. On the other hand, when the opening degree of the expansion valve 30 is changed to the opening direction, the refrigerant pressure at the outlet side of the expansion valve 30 increases and the dryness of the refrigerant decreases.
　室内熱交換器２０（蒸発器）は、膨張弁３０から管９２，延長配管１０３、管１０２へ流れた冷媒を蒸発させる。蒸発した冷媒は、管１０１、延長配管１００、ストップバルブ１１０および四方弁９１を経由して管９８へ流れる。室内熱交換器２０（蒸発器）は、膨張弁３０により減圧された冷媒が室内空気と熱交換し、吸熱を行なうように構成される。この熱交換により、冷媒は蒸発して室内熱交換器２０の出口付近で過熱蒸気となる。ファン２２が、室内熱交換器２０（蒸発器）に併設される。制御装置２００は、制御信号によってファン２２の回転速度を調整する。ファン２２の回転速度を変更することにより、室内熱交換器２０（蒸発器）における冷媒と室内空気との熱交換量を調整することができる。 The indoor heat exchanger 20 (evaporator) evaporates the refrigerant flowing from the expansion valve 30 to the pipe 92, the extension pipe 103, and the pipe 102. The evaporated refrigerant flows into the pipe 98 via the pipe 101, the extension pipe 100, the stop valve 110 and the four-way valve 91. The indoor heat exchanger 20 (evaporator) is configured such that the refrigerant decompressed by the expansion valve 30 exchanges heat with the indoor air to absorb heat. By this heat exchange, the refrigerant evaporates and becomes superheated steam near the outlet of the indoor heat exchanger 20. The fan 22 is attached to the indoor heat exchanger 20 (evaporator). The control device 200 adjusts the rotation speed of the fan 22 according to the control signal. By changing the rotation speed of the fan 22, the amount of heat exchange between the refrigerant and the indoor air in the indoor heat exchanger 20 (evaporator) can be adjusted.
　図３は、冷媒量が通常である場合の運転時の冷凍サイクルのＰ－Ｈ線図である。冷媒がＲ３２である場合を例として説明する。図３に示すＰ－Ｈ線図において、点Ａ１－点Ａ２は、圧縮機１０による圧縮処理、点Ａ２－点Ａ３は、凝縮器による凝縮処理、点Ａ３－点Ａ４は、膨張弁３０による減圧処理、点Ａ４－点Ａ１は、蒸発器による蒸発処理に、それぞれ対応する。冷凍能力は、点Ａ１と点Ａ４のエンタルピー差ｄＨに単位時間当たりの冷媒循環量Ｇｒを掛けた値となる。 FIG. 3 is a PH diagram of the refrigeration cycle during operation when the amount of refrigerant is normal. A case where the refrigerant is R32 will be described as an example. In the PH diagram shown in FIG. 3, points A1 and A2 are compression processing by the compressor 10, points A2 and A3 are condensation processing by a condenser, and points A3 and A4 are decompression by the expansion valve 30. The processing, point A4 to point A1, respectively correspond to the evaporation processing by the evaporator. The refrigerating capacity is a value obtained by multiplying the enthalpy difference dH between the points A1 and A4 by the refrigerant circulation amount Gr per unit time.
　定格運転時の性能改善および能力確保のため、凝縮器出口部分に相当する点Ａ３で過冷却（ＳＣ：subcool）状態が十分に確保できるように、冷媒回路には十分な量の冷媒が封入されている。そのため、低能力で運転するときでも十分な冷媒量があるため凝縮器出口に相当する点Ａ３では冷媒は過冷却状態となる。このため冷凍能力Ｑは、エンタルピー差ｄＨ、単位時間当たりの冷媒循環量Ｇｒとすると、次式（１）で示される。
Ｑ＝Ｇｒ＊ｄＨ　　…　（１）
　循環する冷媒の量が一定量の場合、ｄＨが固定となり、圧縮機の運転周波数を下げて冷媒循環量Ｇｒを落として低能力を実現している。しかし、圧縮機の下限周波数は潤滑油の供給等により限界がある。 In order to improve performance and ensure capacity during rated operation, a sufficient amount of refrigerant is filled in the refrigerant circuit so that a supercooled (SC: subcool) state can be sufficiently ensured at point A3 corresponding to the condenser outlet. ing. Therefore, the refrigerant is in a supercooled state at the point A3 corresponding to the outlet of the condenser because there is a sufficient amount of the refrigerant even when operating with low capacity. Therefore, the refrigerating capacity Q is expressed by the following equation (1), where enthalpy difference dH and refrigerant circulation amount Gr per unit time are given.
Q=Gr*dH (1)
When the amount of circulating refrigerant is constant, dH is fixed, and the operating frequency of the compressor is lowered to reduce the refrigerant circulation amount Gr to realize low capacity. However, the lower limit frequency of the compressor is limited due to the supply of lubricating oil and the like.
　本実施の形態では、上記の式中のｄＨを小さくすることによって、従来以上に大幅に低能力が実現できる。 In the present embodiment, by lowering dH in the above formula, it is possible to achieve a significantly lower capacity than before.
　図４は、低能力時の冷房運転の冷媒の流れを示した図である。図４に示す状態が図２に示す状態と異なる点は、流量調整弁３４によって第２熱交換部４０Ｂの流量が制限されている点である。一方で、ファン４２による送風は継続されている。第２熱交換部４０Ｂにおいて、冷媒の凝縮が行なわれる一方で液化した冷媒が排出されないため、第２熱交換部４０Ｂの内部に液冷媒が貯留された状態となる。他の部分の冷媒の流れについては、図２と同じであるので、図４では説明は繰返さない。 FIG. 4 is a diagram showing the flow of the refrigerant in the cooling operation when the capacity is low. The state shown in FIG. 4 is different from the state shown in FIG. 2 in that the flow rate adjusting valve 34 limits the flow rate of the second heat exchange section 40B. On the other hand, the fan 42 continues to blow air. In the second heat exchange section 40B, the liquefied refrigerant is not discharged while the refrigerant is condensed, so that the liquid refrigerant is stored inside the second heat exchange section 40B. The flow of the refrigerant in the other portions is the same as that in FIG. 2, and therefore the description will not be repeated in FIG.
　図４に示すように、第２熱交換部４０Ｂの内部に液冷媒が貯留されると、冷媒回路を循環する冷媒の量が減少する。なお、第２熱交換部４０Ｂの液封を避けるため、流量調整弁３４は、管９４Ｂ側を完全に閉止せず微少の流量を確保するように構成されることが好ましい。また、循環する冷媒量の減少に伴い、膨張弁３０には二相冷媒が流入するため、膨張弁３０として従来よりも口径が大きい弁を使用することが好ましい。 As shown in FIG. 4, when the liquid refrigerant is stored inside the second heat exchange section 40B, the amount of the refrigerant circulating in the refrigerant circuit decreases. In order to avoid liquid sealing of the second heat exchange section 40B, it is preferable that the flow rate adjusting valve 34 is configured not to completely close the pipe 94B side to ensure a minute flow rate. In addition, since the two-phase refrigerant flows into the expansion valve 30 as the amount of circulating refrigerant decreases, it is preferable to use a valve having a larger diameter than the conventional one as the expansion valve 30.
　図５は、冷媒を熱交換器内に貯留させた場合の運転時の冷凍サイクルのＰ－Ｈ線図である。図５に示すＰ－Ｈ線図において、点Ｂ１－点Ｂ２は、圧縮機１０による圧縮処理、点Ｂ２－点Ｂ４は、凝縮器による凝縮処理、点Ｂ４－点Ｂ５は、膨張弁３０による減圧処理、点Ｂ５－点Ｂ１は、蒸発器による蒸発処理に、それぞれ対応する。この場合、冷凍能力は、点Ｂ１と点Ｂ５のエンタルピー差ｄＨに単位時間あたりの冷媒循環量Ｇｒを掛けた値となる。 FIG. 5 is a PH diagram of the refrigeration cycle during operation when the refrigerant is stored in the heat exchanger. In the PH diagram shown in FIG. 5, points B1 and B2 are compression processing by the compressor 10, points B2 and B4 are condensation processing by a condenser, and points B4 and B5 are decompression by the expansion valve 30. Processing, point B5 to point B1, respectively correspond to the evaporation processing by the evaporator. In this case, the refrigerating capacity is a value obtained by multiplying the enthalpy difference dH between the points B1 and B5 by the refrigerant circulation amount Gr per unit time.
　図３と図５とを比較すると、冷凍能力に関する蒸発器のエンタルピー差ｄＨは、図５の場合が減少している。また、循環する冷媒の量も第２熱交換部４０Ｂの内部に液冷媒が貯留される分減少する。したがって、エンタルピー差ｄＨも冷媒循環量Ｇｒも両方とも減少するため、式（１）に示したようにそれらの積で表される冷凍能力Ｑは従来に比べて小さく抑えることができる。 Comparing FIG. 3 and FIG. 5, the enthalpy difference dH of the evaporator regarding the refrigerating capacity is reduced in the case of FIG. In addition, the amount of the circulating refrigerant is reduced by the amount of the liquid refrigerant stored inside the second heat exchange section 40B. Therefore, both the enthalpy difference dH and the refrigerant circulation amount Gr decrease, so that the refrigerating capacity Q represented by the product of them as shown in the equation (1) can be suppressed smaller than in the conventional case.
　ここで図５における蒸発器入口に相当する点Ｂ５が図３の点Ａ３よりエンタルピーＨの値が大きい理由について説明する。図５における点Ｂ３は図４の凝縮器（第２熱交換部４０Ｂ）の出口の状態を示す。図５における点Ｂ４は図４の凝縮器（第１熱交換部４０Ａ）の出口の状態を示す。両者が合流した後のエンタルピーＨｊは、第１熱交換部４０Ａ、第２熱交換部４０Ｂのそれぞれの出口のエンタルピーＨ４０Ａ，Ｈ４０Ｂおよび冷媒流量Ｇｒ４０Ａ，Ｇｒ４０Ｂを用いて、以下の式で与えられる。 Here, the reason why the point B5 corresponding to the evaporator inlet in FIG. 5 has a larger enthalpy H value than the point A3 in FIG. 3 will be described. Point B3 in FIG. 5 indicates the state of the outlet of the condenser (second heat exchange section 40B) in FIG. Point B4 in FIG. 5 shows the state of the outlet of the condenser (first heat exchange section 40A) in FIG. The enthalpy Hj after the two have joined together is given by the following equation using the enthalpies H40A and H40B at the outlets of the first heat exchange section 40A and the second heat exchange section 40B and the refrigerant flow rates Gr40A and Gr40B.
　Hj=(H40A*Gr40A+H40B*Gr40B)/(Gr40A+Gr40B)
　すなわち、図５に示したように、流量調整弁３４の管９４Ｂ側が閉じており流量が少ない場合、合流後のエンタルピーＨｊは冷媒流量の多い管９４Ａ側のエンタルピーＨ４０Ａとほぼ等しくなる。また、点Ｂ４のエンタルピー、すなわち蒸発器入口の点Ｂ５のエンタルピーは、管９４Ｂ側に流れる冷媒流量で調整可能である。 Hj=(H40A*Gr40A+H40B*Gr40B)/(Gr40A+Gr40B)
That is, as shown in FIG. 5, when the pipe 94B side of the flow rate adjusting valve 34 is closed and the flow rate is small, the enthalpy Hj after the merging is substantially equal to the enthalpy H40A on the pipe 94A side with a large refrigerant flow rate. Further, the enthalpy at the point B4, that is, the enthalpy at the point B5 at the evaporator inlet can be adjusted by the flow rate of the refrigerant flowing to the pipe 94B side.
　図６は、冷房運転中における冷媒貯留制御を説明するためのフローチャートである。図１、図６を参照して、ステップＳ１において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも低いか否かを判断する。 FIG. 6 is a flowchart for explaining refrigerant storage control during the cooling operation. Referring to FIGS. 1 and 6, in step S1, control device 200 determines whether the room temperature detected by room temperature sensor 24 is lower than the set temperature set by a remote controller or the like.
　室内温度＜設定温度であった場合（Ｓ１でＹＥＳ）、ステップＳ２において、制御装置２００は、圧縮機１０の運転周波数ｆが下限周波数ｆｍｉｎより高いか否かを判断する。ｆ＞ｆｍｉｎであった場合（Ｓ２でＹＥＳ）、ステップＳ３において制御装置２００は、圧縮機１０の運転周波数ｆをδ２だけ低下させて、空気調和装置１の冷房能力を低下させる。 When the room temperature is less than the set temperature (YES in S1), the control device 200 determines in step S2 whether the operating frequency f of the compressor 10 is higher than the lower limit frequency fmin. If f>fmin (YES in S2), the control device 200 reduces the operating frequency f of the compressor 10 by δ2 in step S3 to reduce the cooling capacity of the air conditioner 1.
　続いて、ステップＳ４において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも低いか否かを判断する。室内温度＜設定温度であった場合（Ｓ４でＹＥＳ）、再びステップＳ２に処理が戻る。一方、室内温度≧設定温度であった場合（Ｓ４でＮＯ）、ステップＳ５において、制御装置２００は、圧縮機１０の運転周波数ｆをδ１だけ増加させ、空気調和装置１の冷房能力を増加させる。 Subsequently, in step S4, the control device 200 determines whether or not the room temperature detected by the room temperature sensor 24 is lower than the set temperature set by the remote controller or the like. If the room temperature is less than the set temperature (YES in S4), the process returns to step S2. On the other hand, when the indoor temperature≧the set temperature (NO in S4), in step S5, the control device 200 increases the operating frequency f of the compressor 10 by δ1 and increases the cooling capacity of the air conditioner 1.
　以上のステップＳ１～Ｓ５の処理は、インバータ制御によって圧縮機１０の運転周波数を調整し、運転中の空気調和装置１の空調能力を空調負荷に一致させる処理である。しかし、運転周波数ｆが下限値ｆｍｉｎ以下となると（Ｓ２でＮＯ）、これ以上運転周波数を下げることによる空調能力の抑制が不可能であるため、ステップＳ６以降の冷媒循環量を調整する処理に移る。 The above steps S1 to S5 are processes for adjusting the operating frequency of the compressor 10 by inverter control so that the air conditioning capacity of the air conditioner 1 in operation matches the air conditioning load. However, when the operating frequency f becomes equal to or lower than the lower limit value fmin (NO in S2), it is impossible to suppress the air conditioning capacity by further lowering the operating frequency, and therefore, the process proceeds to the process of adjusting the refrigerant circulation amount after step S6. ..
　具体的にはステップＳ６において、冷媒を室外熱交換器４０に貯留させる運転が開始される。ステップＳ６では、制御装置２００は、第２熱交換部４０Ｂの流量を決定する流量調整弁３４の開度Ｌを最大開度Ｌｍａｘとする。最大開度Ｌｍａｘは、初期状態における開度Ｌである。そして、ステップＳ７において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも低いか否かを判断する。 Specifically, in step S6, the operation of storing the refrigerant in the outdoor heat exchanger 40 is started. In step S6, the control device 200 sets the opening degree L of the flow rate adjusting valve 34 that determines the flow rate of the second heat exchange section 40B to the maximum opening degree Lmax. The maximum opening Lmax is the opening L in the initial state. Then, in step S7, control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is lower than the set temperature set by the remote controller or the like.
　室内温度＜設定温度であった場合（Ｓ７でＹＥＳ）、ステップＳ８において、制御装置２００は、流量調整弁３４の開度Ｌをδ３だけ狭くし、第２熱交換部４０Ｂ内の液冷媒の貯留量を増加させる。これにより、冷媒循環量Ｇｒは減少する。そして、ステップＳ９において、制御装置２００は、流量調整弁３４の開度Ｌが下限開度Ｌｍｉｎであるか否かを判断する。 When the indoor temperature is less than the set temperature (YES in S7), in step S8, the control device 200 narrows the opening degree L of the flow rate adjusting valve 34 by δ3 to store the liquid refrigerant in the second heat exchange section 40B. Increase the amount. As a result, the refrigerant circulation amount Gr decreases. Then, in step S9, the control device 200 determines whether or not the opening L of the flow rate adjusting valve 34 is the lower limit opening Lmin.
　流量調整弁３４の開度Ｌが下限開度Ｌｍｉｎでない場合（Ｓ９でＮＯ）、再びステップＳ７の処理が実行される。ステップＳ７において室内温度が設定温度以上であれば（Ｓ７でＮＯ）、これ以上冷房能力を低下させる必要がなく、空調負荷と空調能力が釣り合ったと考えられるので、ステップＳ１０において流量調整弁３４の開度制御が終了し、ステップＳ１１においてメインルーチンに処理が戻る。 When the opening L of the flow rate adjusting valve 34 is not the lower limit opening Lmin (NO in S9), the process of step S7 is executed again. If the indoor temperature is equal to or higher than the set temperature in step S7 (NO in S7), it is considered that there is no need to further reduce the cooling capacity and the air conditioning load and the air conditioning capacity are in balance, so that the flow rate adjustment valve 34 is opened in step S10. Control ends, and the process returns to the main routine in step S11.
　一方、流量調整弁３４の開度Ｌが下限開度Ｌｍｉｎであった場合（Ｓ９でＹＥＳ）、これ以上冷媒を貯留させることができないので、制御装置２００は、ステップＳ１２において圧縮機１０を停止させ、室内温度が低下しすぎるのを防ぐ。 On the other hand, when the opening L of the flow rate adjusting valve 34 is the lower limit opening Lmin (YES in S9), the refrigerant cannot be stored any more, and therefore the control device 200 stops the compressor 10 in step S12. , Prevent the room temperature from dropping too low.
　（暖房運転中の冷媒量制御）
　次に、暖房運転の基本的な動作について説明する。図７は、通常時の暖房運転の冷媒の流れを示した図である。暖房運転では、図７に矢印で示した向きに冷媒が流れる。圧縮機１０は管９６から四方弁９１および管９８を経由して冷媒を吸入し、圧縮する。圧縮された冷媒は四方弁９１を経由して管９０へ流れる。以下、各熱交換器が凝縮器として働くのか蒸発器として働くのかを、理解の容易のために併記する。 (Control of refrigerant amount during heating operation)
Next, the basic operation of the heating operation will be described. FIG. 7: is the figure which showed the flow of the refrigerant|coolant of the heating operation at the time of normal. In the heating operation, the refrigerant flows in the direction shown by the arrow in FIG. 7. The compressor 10 draws in and compresses the refrigerant from the pipe 96 via the four-way valve 91 and the pipe 98. The compressed refrigerant flows to the pipe 90 via the four-way valve 91. Hereinafter, whether each heat exchanger functions as a condenser or an evaporator will be described together for easy understanding.
　室内熱交換器２０（凝縮器）は、圧縮機１０から四方弁９１、管９０、延長配管１００を経由して管１０１に流入した冷媒を凝縮して管１０２へ流す。室内熱交換器２０（凝縮器）は、圧縮機１０から吐出された高温高圧の過熱蒸気となった冷媒が室内空気と熱交換して放熱を行なうように構成される。この熱交換により、冷媒は凝縮されて室内熱交換器２０の出口付近で液化する。ファン２２が、室内熱交換器２０（凝縮器）に併設され、制御装置２００は制御信号によってファン２２の回転速度を調整する。ファン２２の回転速度を変更することにより、室内熱交換器２０（凝縮器）における冷媒と室内空気との熱交換量を調整することができる。 The indoor heat exchanger 20 (condenser) condenses the refrigerant that has flowed into the pipe 101 from the compressor 10 via the four-way valve 91, the pipe 90, and the extension pipe 100 to flow into the pipe 102. The indoor heat exchanger 20 (condenser) is configured so that the refrigerant, which has been discharged from the compressor 10 and has become high-temperature and high-pressure superheated steam, exchanges heat with the indoor air to radiate heat. By this heat exchange, the refrigerant is condensed and liquefied near the outlet of the indoor heat exchanger 20. The fan 22 is attached to the indoor heat exchanger 20 (condenser), and the control device 200 adjusts the rotation speed of the fan 22 by a control signal. By changing the rotation speed of the fan 22, the amount of heat exchange between the refrigerant and the indoor air in the indoor heat exchanger 20 (condenser) can be adjusted.
　膨張弁３０は、室内熱交換器２０（凝縮器）から管１０２および延長配管１０３を経由して管９２へ流れた冷媒を減圧する。減圧された冷媒は管９４へ流れる。膨張弁３０は、制御装置２００から受ける制御信号によって開度を調整可能に構成される。膨張弁３０の開度を閉方向に変化させると、膨張弁３０出口側の冷媒圧力は低下し、冷媒の乾き度は上昇する。一方、膨張弁３０の開度を開方向に変化させると、膨張弁３０出口側の冷媒圧力は上昇し、冷媒の乾き度は低下する。 The expansion valve 30 reduces the pressure of the refrigerant flowing from the indoor heat exchanger 20 (condenser) to the pipe 92 via the pipe 102 and the extension pipe 103. The depressurized refrigerant flows to the pipe 94. The expansion valve 30 is configured so that the opening degree can be adjusted by a control signal received from the control device 200. When the opening degree of the expansion valve 30 is changed to the closing direction, the refrigerant pressure on the outlet side of the expansion valve 30 decreases and the dryness of the refrigerant increases. On the other hand, when the opening degree of the expansion valve 30 is changed to the opening direction, the refrigerant pressure at the outlet side of the expansion valve 30 increases and the dryness of the refrigerant decreases.
　室外熱交換器４０（蒸発器）は、膨張弁３０から管９４へ流れた冷媒を蒸発させる。蒸発した冷媒は、管９６および四方弁９１を経由して管９８へ流れる。室外熱交換器４０（蒸発器）は、膨張弁３０により減圧された冷媒が外気と熱交換し、吸熱を行なうように構成される。この熱交換により、冷媒は蒸発して室外熱交換器４０の出口付近で過熱蒸気となる。ファン４２が、室外熱交換器４０（蒸発器）に併設される。制御装置２００は、制御信号によってファン４２の回転速度を調整する。ファン４２の回転速度を変更することにより、室外熱交換器４０（蒸発器）における冷媒と外気との熱交換量を調整することができる。 The outdoor heat exchanger 40 (evaporator) evaporates the refrigerant flowing from the expansion valve 30 to the pipe 94. The evaporated refrigerant flows to the pipe 98 via the pipe 96 and the four-way valve 91. The outdoor heat exchanger 40 (evaporator) is configured such that the refrigerant decompressed by the expansion valve 30 exchanges heat with the outside air and absorbs heat. By this heat exchange, the refrigerant evaporates and becomes superheated steam near the outlet of the outdoor heat exchanger 40. The fan 42 is attached to the outdoor heat exchanger 40 (evaporator). The control device 200 adjusts the rotation speed of the fan 42 according to the control signal. By changing the rotation speed of the fan 42, the amount of heat exchange between the refrigerant and the outside air in the outdoor heat exchanger 40 (evaporator) can be adjusted.
　図８は、低能力時の暖房運転の冷媒の流れを示した図である。図８に示す状態が図７に示す状態と異なる点は、流量調整弁３２によって第２熱交換部２０Ｂの流量が制限されている点である。一方で、ファン２２による送風は継続されている。第２熱交換部２０Ｂにおいて、冷媒の凝縮が行なわれる一方で液化した冷媒が排出されないため、第２熱交換部２０Ｂの内部に液冷媒が貯留された状態となる。他の部分の冷媒の流れについては、図７と同じであるので、図８では説明は繰返さない。 FIG. 8 is a diagram showing the flow of the refrigerant in the heating operation when the capacity is low. The state shown in FIG. 8 differs from the state shown in FIG. 7 in that the flow rate adjusting valve 32 limits the flow rate of the second heat exchange section 20B. On the other hand, the fan 22 continues to blow air. In the second heat exchange section 20B, the liquefied refrigerant is not discharged while the refrigerant is condensed, so that the liquid refrigerant is stored inside the second heat exchange section 20B. The flow of the refrigerant in the other parts is the same as that in FIG. 7, and therefore the description will not be repeated in FIG.
　図８に示すように、第２熱交換部２０Ｂの内部に液冷媒が貯留されると、冷媒回路を循環する冷媒の量が減少する。なお、第２熱交換部２０Ｂの液封を避けるため、流量調整弁３２は、管１０２Ｂ側を完全に閉止せず微少の流量を確保するように構成されることが好ましい。 As shown in FIG. 8, when the liquid refrigerant is stored inside the second heat exchange section 20B, the amount of the refrigerant circulating in the refrigerant circuit decreases. In order to avoid liquid sealing of the second heat exchange section 20B, it is preferable that the flow rate adjusting valve 32 is configured not to completely close the pipe 102B side to ensure a minute flow rate.
　図７に対応するＰ－Ｈ線図と図８に対応するＰ－Ｈ線図は、図３、図５とは凝縮温度、蒸発温度などが異なるが、冷媒がＲ３２である場合、凝縮器のエンタルピー差が図７よりも図８に示す運転の方が低減する点については図３、図５の関係と同様な傾向となる。 The PH diagram corresponding to FIG. 7 and the PH diagram corresponding to FIG. 8 differ from FIGS. 3 and 5 in the condensation temperature and the evaporation temperature, but when the refrigerant is R32, Regarding the point that the enthalpy difference is smaller in the operation shown in FIG. 8 than in FIG. 7, there is a tendency similar to the relationship in FIGS. 3 and 5.
　したがって、暖房時の凝縮器におけるエンタルピー差が減少するため、凝縮能力は暖房の場合でも従来に比べて小さく抑えることができる。 Therefore, since the enthalpy difference in the condenser during heating is reduced, the condensing capacity can be kept smaller than before even in the case of heating.
　図９は、暖房運転中における冷媒貯留制御を説明するためのフローチャートである。図１、図９を参照して、ステップＳ１１において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも高いか否かを判断する。 FIG. 9 is a flowchart for explaining refrigerant storage control during heating operation. Referring to FIGS. 1 and 9, in step S11, control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is higher than the set temperature set by a remote controller or the like.
　室内温度＞設定温度であった場合（Ｓ１１でＹＥＳ）、ステップＳ１２において、制御装置２００は、圧縮機１０の運転周波数ｆが下限周波数ｆｍｉｎより高いか否かを判断する。ｆ＞ｆｍｉｎであった場合（Ｓ１２でＹＥＳ）、ステップＳ１３において制御装置２００は、圧縮機１０の運転周波数ｆをδ２だけ低下させて、空気調和装置１の暖房能力を低下させる。 When the room temperature>the set temperature (YES in S11), the control device 200 determines in step S12 whether the operating frequency f of the compressor 10 is higher than the lower limit frequency fmin. When f>fmin (YES in S12), the control device 200 reduces the operating frequency f of the compressor 10 by δ2 in step S13 to reduce the heating capacity of the air conditioner 1.
　続いて、ステップＳ１４において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも高いか否かを判断する。室内温度＞設定温度であった場合（Ｓ１４でＹＥＳ）、再びステップＳ１２に処理が戻る。一方、室内温度≦設定温度であった場合（Ｓ１４でＮＯ）、ステップＳ１５において、制御装置２００は、圧縮機１０の運転周波数ｆをδ１だけ増加させ、空気調和装置１の暖房能力を増加させる。 Subsequently, in step S14, the control device 200 determines whether or not the room temperature detected by the room temperature sensor 24 is higher than the set temperature set by the remote controller or the like. If the room temperature>the set temperature (YES in S14), the process returns to step S12. On the other hand, when the indoor temperature≦the set temperature (NO in S14), the control device 200 increases the operating frequency f of the compressor 10 by δ1 and increases the heating capacity of the air conditioning device 1 in step S15.
　以上のステップＳ１１～Ｓ１５の処理は、インバータ制御によって圧縮機１０の運転周波数を調整し、運転中の空気調和装置１の空調能力を空調負荷に一致させる処理である。しかし、運転周波数ｆが下限値ｆｍｉｎ以下となると（Ｓ１２でＮＯ）、これ以上運転周波数を下げることによる空調能力の抑制が不可能であるため、ステップＳ１６以降の冷媒循環量を調整する処理に移る。 The above steps S11 to S15 are processes for adjusting the operating frequency of the compressor 10 by inverter control so that the air conditioning capacity of the air conditioner 1 in operation matches the air conditioning load. However, when the operating frequency f becomes equal to or lower than the lower limit value fmin (NO in S12), it is impossible to suppress the air conditioning capacity by further lowering the operating frequency, so that the process proceeds to the process of adjusting the refrigerant circulation amount after step S16. ..
　具体的にはステップＳ１６において、冷媒を室内熱交換器２０に貯留させる運転が開始される。ステップＳ１６では、制御装置２００は、第２熱交換部２０Ｂの流量を決定する流量調整弁３２の開度Ｌを最大開度Ｌｍａｘとする。最大開度Ｌｍａｘは初期状態における開度Ｌである。そして、ステップＳ１７において制御装置２００は、室温センサ２４で検出された室内温度がリモコンなどによって設定された設定温度よりも高いか否かを判断する。 Specifically, in step S16, the operation of storing the refrigerant in the indoor heat exchanger 20 is started. In step S16, the control device 200 sets the opening L of the flow rate adjusting valve 32 that determines the flow rate of the second heat exchange unit 20B to the maximum opening Lmax. The maximum opening Lmax is the opening L in the initial state. Then, in step S17, control device 200 determines whether or not the room temperature detected by room temperature sensor 24 is higher than the set temperature set by the remote controller or the like.
　室内温度＞設定温度であった場合（Ｓ１７でＹＥＳ）、ステップＳ１８において、制御装置２００は、流量調整弁３２の開度Ｌをδ３だけ狭くし、第２熱交換部２０Ｂ内の液冷媒の貯留量を増加させる。そして、ステップＳ１９において、制御装置２００は、流量調整弁３２の開度Ｌが下限開度Ｌｍｉｎであるか否かを判断する。 When the room temperature>the set temperature (YES in S17), in step S18, the control device 200 narrows the opening degree L of the flow rate adjusting valve 32 by δ3 to store the liquid refrigerant in the second heat exchange section 20B. Increase the amount. Then, in step S19, the control device 200 determines whether or not the opening L of the flow rate adjusting valve 32 is the lower limit opening Lmin.
　流量調整弁３２の開度Ｌが下限開度Ｌｍｉｎでない場合（Ｓ１９でＮＯ）、再びステップＳ１７の処理が実行される。ステップＳ１７において室内温度が設定温度以下であれば（Ｓ１７でＮＯ）、これ以上暖房能力を低下させる必要がなく、空調負荷と空調能力が釣り合ったと考えられるので、ステップＳ２０において流量調整弁３２の開度制御が終了し、ステップＳ２１においてメインルーチンに処理が戻る。 When the opening L of the flow rate adjusting valve 32 is not the lower limit opening Lmin (NO in S19), the process of step S17 is executed again. If the indoor temperature is equal to or lower than the set temperature in step S17 (NO in S17), it is considered that there is no need to further reduce the heating capacity, and the air conditioning load and the air conditioning capacity are in balance, so the flow control valve 32 is opened in step S20. Control is completed, and the process returns to the main routine in step S21.
　一方、流量調整弁３２の開度Ｌが下限開度Ｌｍｉｎであった場合（Ｓ１９でＹＥＳ）、これ以上冷媒を貯留させることができないので、制御装置２００は、ステップＳ２２において圧縮機１０を停止させ、室内温度が上昇しすぎるのを防ぐ。 On the other hand, when the opening degree L of the flow rate adjusting valve 32 is the lower limit opening degree Lmin (YES in S19), the refrigerant cannot be stored any more, so the control device 200 stops the compressor 10 in step S22. , Prevent the room temperature from rising too high.
　図１０は、本実施の形態の制御を行なった場合と通常の制御を行なった場合の下限能力を対比して示す図である。定格能力を１００％としたときに、圧縮機１０の周波数制御のみを実行した場合の下限能力は、１５％であるのに対して、圧縮機１０の周波数制御に加えて熱交換器内への冷媒貯留量を制御した場合の下限能力は、１０％となった。本実施の形態の空調機は、下限能力を通常機と比べて６６．７％まで下げることができる。 FIG. 10 is a diagram showing the lower limit capabilities of the case where the control of the present embodiment is performed and the case where the normal control is performed, in comparison. When the rated capacity is set to 100%, the lower limit capacity when only the frequency control of the compressor 10 is executed is 15%, whereas in addition to the frequency control of the compressor 10, the lower limit capacity The lower limit capacity when controlling the refrigerant storage amount was 10%. The lower limit capacity of the air conditioner of the present embodiment can be reduced to 66.7% compared to the normal machine.
　したがって、本実施の形態の空気調和装置によれば、高気密高断熱の住宅において、空調負荷が少ない場合に温度変動を従来よりも抑えることができる。 Therefore, according to the air conditioner of the present embodiment, in a highly airtight and highly insulated house, temperature fluctuations can be suppressed more than before when the air conditioning load is small.
　図１１は、流量調整弁を変形した変形例を示す図である。図１１に示す変形例は、図１における流量調整弁３２，３４をそれぞれ流量調整部３２Ａ、３４Ａに変更したものである。流量調整弁３２，３４は、具体的には流量調整機能を有する三方弁などを意図していた。 FIG. 11 is a diagram showing a modified example in which the flow rate adjusting valve is modified. In the modification shown in FIG. 11, the flow rate adjusting valves 32 and 34 in FIG. 1 are changed to flow rate adjusting units 32A and 34A, respectively. The flow rate adjusting valves 32 and 34 are specifically intended to be three-way valves having a flow rate adjusting function.
　流量調整弁として三方弁を使用する場合、三方弁を微開にすることで循環する冷媒量を調整できるので、圧縮機周波数と三方弁の調整により空調能力の変化幅を大きくすることができる（下限能力をさらに低下させることができる）。 When a three-way valve is used as the flow rate control valve, the amount of circulating refrigerant can be adjusted by slightly opening the three-way valve, so the adjustment range of the air-conditioning capacity can be increased by adjusting the compressor frequency and the three-way valve ( The lower limit capacity can be further reduced).
　しかし、流量調整弁３２，３４として、もっと簡単な構成を採用することも可能である。図１１に示すように冷媒を貯留させる第２熱交換部２０Ｂ，４０Ｂ側のみに流量調整弁を設けた構成としても、同様な制御が可能である。 However, it is also possible to adopt a simpler configuration as the flow rate adjusting valves 32, 34. Similar control is possible even if the flow rate adjusting valve is provided only on the second heat exchange section 20B, 40B side for storing the refrigerant as shown in FIG.
　最後に、本実施の形態について、再び図面を参照して総括する。
　本開示は、運転中に、冷媒が圧縮機１０、凝縮器（室外熱交換器４０／室内熱交換器２０）、膨張装置（膨張弁３０）および蒸発器（室内熱交換器２０／室外熱交換器４０）の順に循環する空気調和装置１に関する。凝縮器（室外熱交換器４０／室内熱交換器２０）は、冷媒が互いに並行して流れるように構成された第１熱交換部４０Ａ／２０Ａおよび第２熱交換部４０Ｂ／２０Ｂと、第１熱交換部４０Ａ／２０Ａを通過する冷媒の流量と第２熱交換部４０Ｂ／２０Ｂを通過する冷媒の流量とに流量差をつけることが可能に構成された流量制限部（流量調整弁３４／３２）とを含む。空気調和装置１は、圧縮機１０と流量制限部（流量調整弁３４／３２）とを制御する制御装置２００を備える。制御装置２００は、空気調和装置１の空調能力を変更する場合に、圧縮機１０の周波数と流量差とを組み合わせて使用する。 Finally, the present embodiment will be summarized again with reference to the drawings.
In the present disclosure, during operation, the refrigerant is a compressor 10, a condenser (outdoor heat exchanger 40/indoor heat exchanger 20), an expansion device (expansion valve 30), and an evaporator (indoor heat exchanger 20/outdoor heat exchange). The air conditioner 1 that circulates in the order of the device 40). The condenser (outdoor heat exchanger 40/indoor heat exchanger 20) includes a first heat exchange section 40A/20A and a second heat exchange section 40B/20B configured to allow the refrigerant to flow in parallel with each other. A flow rate restricting unit (flow rate adjusting valve 34/32) configured to be able to make a flow rate difference between the flow rate of the refrigerant passing through the heat exchange section 40A/20A and the flow rate of the refrigerant passing through the second heat exchange section 40B/20B. ) And. The air conditioner 1 includes a control device 200 that controls the compressor 10 and the flow rate limiting unit (flow rate adjusting valve 34/32). The control device 200 uses the frequency and the flow rate difference of the compressor 10 in combination when changing the air conditioning capacity of the air conditioner 1.
　なお、冷房時と暖房時で凝縮器、蒸発器に対応する熱交換器が異なり、流量制限部に対応する要素も異なるため、上記のように対応関係を示した。また膨張装置は、膨張弁３０が対応するが、必ずしも弁でなくても良く、たとえば、キャピラリーチューブのようなものであっても良い。 Note that the heat exchangers corresponding to the condenser and evaporator differ during cooling and heating, and the elements corresponding to the flow rate restriction unit also differ, so the correspondence relationship is shown above. The expansion device corresponds to the expansion valve 30, but is not necessarily a valve and may be, for example, a capillary tube.
　このような構成とすることによって、冷媒を貯留させる容器のように凝縮器の一部を使用することができるため、アキュムレータおよびレシーバ等の冷媒容器を用いずに冷媒循環量を増減させ、下限能力を小さく抑えることができる。また、アキュムレータおよびレシーバ等の冷媒容器を用いる場合であっても、小型のサイズで済む。 With such a configuration, since a part of the condenser can be used like a container for storing the refrigerant, the refrigerant circulation amount can be increased or decreased without using a refrigerant container such as an accumulator and a receiver, and the lower limit capacity can be used. Can be kept small. Further, even when using a refrigerant container such as an accumulator and a receiver, a small size is sufficient.
　好ましくは、制御装置２００は、（ａ）空調能力を第１能力から第１能力よりも小さい第２能力に変更する場合に、圧縮機１０の周波数ｆを低減させ、（ｂ）空調能力を第２能力から第２能力よりも小さい第３能力に変更する場合に、流量制限部（流量調整弁３４／３２）によって第２熱交換部４０Ｂ／２０Ｂを通過する冷媒の流量を第１熱交換部４０Ａ／２０Ａを通過する冷媒の流量よりも制限し、第２熱交換部４０Ｂ／２０Ｂに貯留する冷媒を増加させることにより、冷媒の循環量を低減させる。 Preferably, the control device 200 reduces the frequency f of the compressor 10 when changing (a) the air conditioning capacity from the first capacity to the second capacity that is smaller than the first capacity, and (b) sets the air conditioning capacity to the first capacity. When changing from the second capacity to the third capacity smaller than the second capacity, the flow rate of the refrigerant passing through the second heat exchange section 40B/20B is changed by the flow rate restriction section (flow rate adjusting valve 34/32) to the first heat exchange section. By limiting the flow rate of the refrigerant passing through 40A/20A and increasing the amount of refrigerant stored in the second heat exchange section 40B/20B, the circulation amount of the refrigerant is reduced.
　圧縮機１０の運転周波数を変化させて空調能力を下げる方が、流量制限部によって冷媒貯留量を増加させて空調能力を下げるよりも、応答性が良い。したがって、空調能力を下げる場合には、まず運転周波数を低下させ、それと同時またはその後に流量制限部によって冷媒貯留量を増加させて空調能力を下げるほうが応答性が良く、室温の変動も少なくて済む。 Changing the operating frequency of the compressor 10 to lower the air conditioning capacity has better response than lowering the air conditioning capacity by increasing the refrigerant storage amount by the flow rate limiting unit. Therefore, when lowering the air conditioning capacity, it is better to lower the air conditioning capacity by lowering the operating frequency first, and at the same time or after that, increasing the refrigerant storage amount by the flow rate limiting unit to lower the air conditioning capacity, and the fluctuation of room temperature can be small. ..
　好ましくは、空気調和装置１は、冷媒の循環方向を冷房運転時と暖房運転時とで切り換える四方弁９１をさらに備える。室内熱交換器２０と室外熱交換器４０は、ともに２つに分割されている。冷房運転時には室外熱交換器４０が凝縮器として働き、暖房運転時には室内熱交換器２０が凝縮器として働く。 Preferably, the air conditioner 1 further includes a four-way valve 91 that switches the circulation direction of the refrigerant between cooling operation and heating operation. The indoor heat exchanger 20 and the outdoor heat exchanger 40 are both divided into two. The outdoor heat exchanger 40 functions as a condenser during the cooling operation, and the indoor heat exchanger 20 functions as a condenser during the heating operation.
　冷房運転時には、室外熱交換器４０側に配置されている流量調整弁３４の流路の一方の流路を閉にする。室外熱交換器４０のファン４２が回っているため、閉止された側の熱交換器（図４の第２熱交換部４０Ｂ）に冷媒が貯留する。 During the cooling operation, one of the flow paths of the flow rate adjusting valve 34 arranged on the outdoor heat exchanger 40 side is closed. Since the fan 42 of the outdoor heat exchanger 40 is rotating, the refrigerant is stored in the heat exchanger on the closed side (the second heat exchange unit 40B in FIG. 4).
　一方、暖房運転時には、室内熱交換器２０側に配置されている流量調整弁３２の流路の一方を閉にする。室内熱交換器２０のファンが回っているため、閉止された側の熱交換器（図８の第２熱交換部２０Ｂ）に冷媒が貯留する。 On the other hand, during the heating operation, one of the flow paths of the flow rate adjusting valve 32 arranged on the indoor heat exchanger 20 side is closed. Since the fan of the indoor heat exchanger 20 is rotating, the refrigerant is stored in the heat exchanger on the closed side (the second heat exchange section 20B in FIG. 8).
　このような構成とすることによって、１台の空気調和装置において、冷房時、暖房時の両方において、下限の空調能力を引き下げることが可能となる。 With such a configuration, it is possible to lower the lower limit air conditioning capacity in one air conditioner both during cooling and during heating.
　なお、本実施の形態の空気調和装置１では、空調能力を低下させるために、積極的に冷媒を熱交換器に寝込ませるため、凝縮器のファンの回転を維持する点も特徴の一つである。室外熱交換器では、通常の構成では、凝縮器のファンは、分割された２つの熱交換部で共有される一つのファンである。室内熱交換器では、凝縮器のファンは、ラインフローファンだと共通な一つのファンであるが、左右にプロペラファンが２つある構成の場合は、ファンを２つとも回転させることになる。 In addition, in the air conditioner 1 of the present embodiment, one of the features is that the rotation of the condenser fan is maintained in order to positively let the refrigerant lie in the heat exchanger in order to reduce the air conditioning capacity. Is. In the outdoor heat exchanger, in the normal configuration, the fan of the condenser is one fan shared by the two divided heat exchange sections. In the indoor heat exchanger, the fan of the condenser is one fan that is common to the line flow fan, but in the case of a configuration having two propeller fans on the left and right, both fans will rotate.
　今回開示された実施の形態は、すべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は、上記した実施の形態の説明ではなくて請求の範囲によって示され、請求の範囲と均等の意味及び範囲内でのすべての変更が含まれることが意図される。 The embodiments disclosed this time are to be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the claims, and is intended to include meanings equivalent to the claims and all modifications within the scope.
　１　空気調和装置、２　室外機、３　室内機、１０　圧縮機、２０　室内熱交換器、２０Ａ，４０Ａ　第１熱交換部、２０Ｂ，４０Ｂ　第２熱交換部、２２，４２　ファン、２４　室温センサ、３０　膨張弁、３２，３４　流量調整弁、３２Ａ　流量調整部、４０　室外熱交換器、９０，９２，９４，９４Ａ，９４Ｂ，９６，９７Ａ，９７Ｂ，９８，９９，１０１，１０１Ａ，１０１Ｂ，１０２，１０２Ａ，１０２Ｂ　管、９１　四方弁、１００，１０３　延長配管、１１０，１１２　ストップバルブ、２００　制御装置、２０１　通信回路、２０２　プロセッサ、２０３　メモリ、Ｅ，Ｆ，Ｇ，Ｈ　ポート。 1 air conditioner, 2 outdoor unit, 3 indoor unit, 10 compressor, 20 indoor heat exchanger, 20A, 40A first heat exchange section, 20B, 40B second heat exchange section, 22, 42 fan, 24 room temperature sensor, 30 expansion valve, 32, 34 flow rate adjusting valve, 32A flow rate adjusting section, 40 outdoor heat exchanger, 90, 92, 94, 94A, 94B, 96, 97A, 97B, 98, 99, 101, 101A, 101B, 102, 102A, 102B pipe, 91 four-way valve, 100, 103 extension pipe, 110, 112 stop valve, 200 control device, 201 communication circuit, 202 processor, 203 memory, E, F, G, H port.

Claims (3)

  1. 　運転中に、冷媒が圧縮機、凝縮器、膨張装置および蒸発器の順に循環する空気調和装置であって、
    　前記凝縮器は、
    　前記冷媒が互いに並行して流れるように構成された第１熱交換部および第２熱交換部と、
    　前記第１熱交換部を通過する冷媒の流量と前記第２熱交換部を通過する冷媒の流量とに流量差をつけることが可能に構成された流量制限部とを含み、
    　前記空気調和装置は、前記圧縮機と前記流量制限部とを制御する制御装置を備え、
    　前記制御装置は、前記空気調和装置の空調能力を変更する場合に、前記圧縮機の周波数と前記流量差とを組み合わせて使用する、空気調和装置。     An air conditioner in which a refrigerant circulates in order of a compressor, a condenser, an expander, and an evaporator during operation,
    The condenser is
    A first heat exchange section and a second heat exchange section configured such that the refrigerant flows in parallel with each other;
    A flow rate limiting unit configured to be capable of providing a flow rate difference between the flow rate of the refrigerant passing through the first heat exchange section and the flow rate of the refrigerant passing through the second heat exchange section,
    The air conditioner includes a control device that controls the compressor and the flow rate limiter,
    The air conditioner, wherein the control device uses a combination of the frequency of the compressor and the flow rate difference when changing the air conditioning capacity of the air conditioner.
  2. 　前記制御装置は、（ａ）前記空調能力を第１能力から前記第１能力よりも小さい第２能力に変更する場合に、前記圧縮機の周波数を低減させ、（ｂ）前記空調能力を前記第２能力から前記第２能力よりも小さい第３能力に変更する場合に、前記流量制限部によって前記第２熱交換部を通過する冷媒の流量を前記第１熱交換部を通過する冷媒の流量よりも制限し、前記第２熱交換部に貯留する冷媒を増加させることにより、冷媒の循環量を低減させる、請求項１に記載の空気調和装置。 The control device (a) reduces the frequency of the compressor when changing the air conditioning capacity from a first capacity to a second capacity smaller than the first capacity, and (b) sets the air conditioning capacity to the second capacity. When changing from the second capacity to the third capacity that is smaller than the second capacity, the flow rate of the refrigerant that passes through the second heat exchange section by the flow rate limiting section is smaller than the flow rate of the refrigerant that passes through the first heat exchange section. The air conditioner according to claim 1, wherein the amount of circulation of the refrigerant is reduced by limiting the amount of refrigerant and increasing the amount of refrigerant stored in the second heat exchange unit.
  3. 　前記冷媒の循環方向を冷房運転時と暖房運転時とで切り換える四方弁をさらに備え、
    　室内熱交換器と室外熱交換器がともに２つに分割されており、
    　冷房運転時には前記室外熱交換器が前記凝縮器として働き、
    　暖房運転時には前記室内熱交換器が前記凝縮器として働く、請求項１または２に記載の空気調和装置。     Further comprising a four-way valve that switches the circulation direction of the refrigerant between cooling operation and heating operation,
    The indoor heat exchanger and the outdoor heat exchanger are both divided into two,
    During the cooling operation, the outdoor heat exchanger works as the condenser,
    The air conditioner according to claim 1, wherein the indoor heat exchanger functions as the condenser during heating operation.
PCT/JP2019/002650 2019-01-28 2019-01-28 Air conditioner WO2020157788A1 (en)

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