WO2022123736A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2022123736A1
WO2022123736A1 PCT/JP2020/046094 JP2020046094W WO2022123736A1 WO 2022123736 A1 WO2022123736 A1 WO 2022123736A1 JP 2020046094 W JP2020046094 W JP 2020046094W WO 2022123736 A1 WO2022123736 A1 WO 2022123736A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
pipe
control device
gas
solenoid valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/046094
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English (en)
Japanese (ja)
Inventor
素 早坂
悠介 有井
智隆 石川
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2020/046094 priority Critical patent/WO2022123736A1/fr
Priority to JP2022567979A priority patent/JP7433476B2/ja
Priority to EP20965118.1A priority patent/EP4261475A4/fr
Publication of WO2022123736A1 publication Critical patent/WO2022123736A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid
    • 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
    • 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
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B2600/05—Refrigerant levels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser

Definitions

  • This disclosure relates to a refrigeration cycle device.
  • an intermediate injection type refrigeration cycle device for the purpose of reducing power consumption and improving capacity of the refrigeration cycle.
  • This refrigeration cycle device divides a part of the refrigerant circulating in the main circuit into the injection circuit and injects it into the intermediate pressure portion of the compressor.
  • Patent Document 1 provides a gas-liquid separator in an injection circuit, and freezes a flow having a large amount of gas phase and a flow having a large amount of liquid phase in the first and second injection paths, respectively. Cycle devices are disclosed. As a result, the mass flow rate of the refrigerant flowing through the second injection path increases.
  • the amount of refrigerant in the main circuit is adjusted by storing excess liquid refrigerant in the receiver tank provided in the main circuit. Since a receiver tank is provided in addition to the gas-liquid separator as a member for storing the refrigerant, the refrigeration cycle device becomes large.
  • the present disclosure has been made to solve the above problems, and an object thereof is to provide an intermediate injection type refrigeration cycle apparatus capable of miniaturization.
  • the refrigerating cycle device of one aspect of the present disclosure is a main circuit in which the refrigerant circulates in the order of a compressor, a condenser, a decompression device, and an evaporator, and a part of the refrigerant flowing from the condenser to the decompression device is divided into a compressor. It is equipped with an injection circuit for inflow.
  • the injection circuit includes a gas-liquid separator that separates a part of the refrigerant into gas-liquid.
  • the injection circuit merges the first pipe that discharges the liquid refrigerant from the gas-liquid separator, the second pipe that discharges the gas refrigerant from the gas-liquid separator, and the refrigerant that flows through the first pipe and the refrigerant that flows through the second pipe. It includes a third pipe that is allowed to flow into the injection port of the compressor. Further, the injection circuit includes a flow rate adjusting valve provided in the first pipe and a first solenoid valve provided in the second pipe. The refrigeration cycle device further includes a control device that adjusts the amount of refrigerant in the main circuit by controlling the opening degree of the flow rate adjusting valve and the open / closed state of the first solenoid valve.
  • the amount of refrigerant in the main circuit is adjusted by using the gas-liquid separator provided in the injection circuit.
  • the gas-liquid separator provided in the injection circuit.
  • FIG. It is a figure which shows the internal structure of the refrigerating cycle apparatus which concerns on Embodiment 1.
  • FIG. It is a figure which shows the structure of the gas-liquid separator schematically. It is a flowchart which shows an example of the processing flow of the control apparatus which concerns on Embodiment 1.
  • FIG. It is a figure which shows the internal structure of the refrigerating cycle apparatus which concerns on Embodiment 2. It is a flowchart which shows an example of the processing flow of the control apparatus which concerns on Embodiment 2.
  • FIG. It is a figure which shows an example of the internal structure of the refrigerating cycle apparatus which concerns on Embodiment 3.
  • FIG. It is a flowchart which shows an example of the processing flow of the control apparatus which concerns on Embodiment 3.
  • FIG. It is a flowchart which shows an example of the processing flow of the control apparatus which concerns on Embodiment 3.
  • FIG. 1 It is a figure which shows an example of the internal structure of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. It is a figure which shows an example of the correspondence table stored in the control apparatus which concerns on Embodiment 4.
  • FIG. It is a figure which shows an example of the height range set with respect to the gas-liquid separator in Embodiment 4.
  • FIG. It is a figure which shows the state of a gas-liquid separator when a liquid level reaches a reference height.
  • It is a flowchart which shows the flow of steps S31 to S37 among the processing of the control apparatus which concerns on Embodiment 4.
  • FIG. It is a flowchart which shows the flow of steps S38-S44 among the processing of the control apparatus which concerns on Embodiment 4.
  • FIG. It is a flowchart which shows the flow of steps S45 to S47 in the process of the control apparatus which concerns on Embodiment 4.
  • FIG. It is a figure which shows an example of the internal structure of the refrigerating cycle apparatus which concerns on Embodiment 5. It is a figure which shows an example of the correspondence table stored in the control apparatus which concerns on Embodiment 5. It is a figure which shows an example of the height range set with respect to the gas-liquid separator in Embodiment 5. It is a flowchart which shows the flow of steps S51-S59 in the process of the control apparatus which concerns on Embodiment 5. It is a flowchart which shows the flow of steps S60 to S66 among the processing of the control apparatus which concerns on Embodiment 5.
  • FIG. 1 is a diagram showing an internal configuration of the refrigeration cycle apparatus 100 according to the first embodiment.
  • the refrigerating cycle device 100 shown in FIG. 1 cools a cooling target space such as a room, a warehouse, a showcase, or a refrigerator.
  • the refrigeration cycle device 100 includes a heat source side unit 80 and a user side unit 90.
  • the heat source side unit 80 and the user side unit 90 are connected by a liquid pipe 91 and a gas pipe 92.
  • a supercooled liquid refrigerant flows from the heat source side unit 80 toward the user side unit 90 in the liquid pipe 91.
  • a gas refrigerant flows from the user-side unit 90 toward the heat source-side unit 80 in the gas pipe 92.
  • the lengths of the liquid pipe 91 and the gas pipe 92 are adjusted according to the installation positions of the heat source side unit 80 and the user side unit 90. In the example shown in FIG. 1, one heat source side unit 80 and one user side unit 90 are shown, but the number of these units is not limited. At least one of the heat source side unit 80 and the user side unit 90 may be two or more.
  • the refrigeration cycle device 100 separates a part of the refrigerant flowing from the condenser 2 to the decompression device 3 and a main circuit 50 in which the refrigerant circulates in the order of the compressor 1, the condenser 2, the decompression devices 3 and 4, and the evaporator 5. It is provided with an injection circuit 60 for flowing into the compressor 1.
  • the compressor 1, the condenser 2, the decompression device 3, and the injection circuit 60 are provided in the heat source side unit 80.
  • the decompression device 4 and the evaporator 5 are provided in the user-side unit 90.
  • the refrigerant is, for example, a CO 2 refrigerant.
  • the compressor 1 is, for example, a scroll compressor, and has a suction port 1i and a discharge port 1o.
  • the compressor 1 compresses the refrigerant sucked from the suction port 1i and discharges it from the discharge port 1o.
  • the compressor 1 is a positive displacement compressor driven by a drive motor (not shown) controlled by an inverter, and has a variable operating capacity. Further, the compressor 1 has an injection port 1p leading to an intermediate pressure portion of the compression chamber.
  • the condenser 2 is connected to the discharge port 1o of the compressor 1 via a pipe, and condenses the refrigerant discharged from the compressor 1.
  • the condenser 2 exchanges heat between the refrigerant discharged from the compressor 1 and the outside air sent by the fan 17. As a result, the heat of the refrigerant is dissipated to the outside air, and the refrigerant is cooled.
  • the condenser 2 is, for example, a fin-and-tube heat exchanger having a heat transfer tube and a plurality of fins.
  • the pressure reducing devices 3 and 4 are composed of an electronic expansion valve, a temperature type expansion valve, and the like, and reduce the pressure of the refrigerant that has passed through the condenser 2. Specifically, the decompression devices 3 and 4 decompress and expand the refrigerant, and adjust the flow rate of the refrigerant flowing through the main circuit 50.
  • the evaporator 5 heat-exchanges the refrigerant decompressed and expanded by the depressurizing devices 3 and 4 with the air in the user-side unit 90 to evaporate the refrigerant.
  • the evaporator 5 is, for example, a fin-and-tube heat exchanger having a heat transfer tube and a plurality of fins.
  • the injection circuit 60 includes pipes 8, 9, 10 and 16, flow rate adjusting valves 6 and 13, a gas-liquid separator 7, and a solenoid valve 14.
  • the pipe 16 connects the branch point 15 between the condenser 2 and the decompression device 3 in the main circuit 50 and the gas-liquid separator 7.
  • the pipe 16 divides a part of the refrigerant flowing from the condenser 2 to the decompression device 3 and flows it into the gas-liquid separator 7.
  • the flow rate adjusting valve 6 is provided in the pipe 16 and adjusts the amount of the refrigerant flowing through the injection circuit 60.
  • the flow rate adjusting valve 6 is, for example, an electronic expansion valve, and the opening degree is controlled by a control device 70 described later to adjust the flow rate of the refrigerant branched to the injection circuit 60.
  • the opening degree of the flow rate adjusting valve 6 is controlled to increase as the discharge temperature, which is the temperature of the refrigerant discharged from the compressor 1, increases, and decreases as the discharge temperature decreases.
  • the gas-liquid separator 7 separates the refrigerant that has passed through the flow rate adjusting valve 6 into a liquid refrigerant (hereinafter referred to as “liquid refrigerant”) and a gaseous refrigerant (hereinafter referred to as “gas refrigerant”). ..
  • the pipe 8 is provided to discharge the liquid refrigerant from the gas / liquid separator 7.
  • the pipe 9 is provided to discharge the gas refrigerant from the gas-liquid separator 7.
  • the pipe 10 merges the refrigerant flowing through the pipe 8 and the refrigerant flowing through the pipe 9 and flows them into the injection port 1p of the compressor 1. That is, the pipe 10 connects the confluence 11 of the pipes 8 and 9 with the injection port 1p.
  • the pipe 8 connects the liquid refrigerant discharge port of the gas-liquid separator 7 and the confluence point 11.
  • the pipe 9 connects the gas refrigerant discharge port of the gas-liquid separator 7 and the confluence point 11.
  • the flow rate adjusting valve 13 is provided in the pipe 8 and adjusts the flow rate of the refrigerant in the pipe 8.
  • the opening degree of the flow rate adjusting valve 13 can be changed and is controlled to a designated opening degree among a plurality of stages.
  • the minimum opening is the closed state.
  • the solenoid valve 14 is provided in the pipe 9 and is controlled to either an open state or a closed state.
  • the refrigeration cycle device 100 includes an economizer 12, a pressure sensor 31, a temperature sensor 32, and a control device 70.
  • the economizer 12 exchanges heat between the refrigerant flowing through the pipe 10 and the refrigerant flowing out of the condenser 2, and supercools the refrigerant flowing out of the condenser 2.
  • the economizer 12 is, for example, a double tube heat exchanger or a plate heat exchanger. In the example shown in FIG. 1, the economizer 12 is arranged between the branch point 15 and the decompression device 3. However, the economizer 12 may be arranged between the condenser 2 and the branch point 15.
  • the pressure sensor 31 measures the discharge pressure P1 which is the pressure of the refrigerant discharged from the compressor 1. The pressure sensor 31 outputs the measurement result to the control device 70.
  • the temperature sensor 32 measures the temperature T of the refrigerant that has passed through the condenser 2. The temperature sensor 32 outputs the measurement result to the control device 70.
  • the control device 70 controls the operation of each part provided in the refrigeration cycle device 100.
  • the control device 70 adjusts the amount of refrigerant in the main circuit 50 by controlling the opening degree of the flow rate adjusting valve 13 and the open / closed state of the solenoid valve 14. That is, the amount of the refrigerant in the main circuit 50 is adjusted by using the gas-liquid separator 7 provided in the injection circuit 60. Therefore, it is not necessary to provide a receiver tank or the like in addition to the gas-liquid separator 7, and the refrigeration cycle device 100 can be downsized.
  • the gas-liquid separator 7 stores the refrigerant separated from the main circuit 50.
  • the gas refrigerant is not discharged from the gas-liquid separator 7, and the gas refrigerant is stored in the gas-liquid separator 7.
  • the discharge of the liquid refrigerant from the gas-liquid separator 7 to the pipe 8 is promoted, and the amount of the refrigerant in the main circuit 50 increases.
  • the control device 70 opens the solenoid valve 14 when the amount of the refrigerant in the main circuit 50 is excessive.
  • the gas refrigerant is discharged from the gas-liquid separator 7, and the liquid refrigerant is likely to be stored in the gas-liquid separator 7.
  • the amount of the liquid refrigerant stored in the gas-liquid separator 7 increases, and the amount of the refrigerant in the main circuit 50 decreases.
  • the control device 70 may determine the excess or deficiency of the amount of the refrigerant in the main circuit 50 based on, for example, the discharge pressure P1 measured by the pressure sensor 31 and the temperature T measured by the temperature sensor 32. The details of this determination method will be described later.
  • the control device 70 further controls the opening degrees of the pressure reducing devices 3 and 4 and the flow rate adjusting valve 6.
  • a known method can be adopted as a method for controlling the opening degree of the pressure reducing devices 3 and 4 and the flow rate adjusting valve 6. Therefore, detailed description of the method of controlling the opening degree of the pressure reducing devices 3 and 4 and the flow rate adjusting valve 6 will be omitted.
  • the control device 70 is composed of hardware such as a circuit device that realizes its function.
  • the control device 70 may also be configured by an arithmetic unit such as a CPU (Central Processing Unit) and a memory in which software executed by the arithmetic unit is stored.
  • an arithmetic unit such as a CPU (Central Processing Unit) and a memory in which software executed by the arithmetic unit is stored.
  • FIG. 2 is a diagram schematically showing the configuration of the gas-liquid separator 7.
  • the refrigerant is stored in the internal space of the gas-liquid separator 7.
  • One end of the pipe 16 penetrates the upper wall of the gas-liquid separator 7 and is located in the internal space.
  • the refrigerant that has passed through the pipe 16 is temporarily stored in the internal space of the gas-liquid separator 7.
  • one end of the pipe 8 penetrates the lower wall of the gas-liquid separator 7 and is located at the lower part of the internal space.
  • the liquid refrigerant accumulates in the lower part of the internal space. Therefore, the liquid refrigerant is discharged from the pipe 8.
  • One end of the pipe 9 penetrates the upper wall of the gas-liquid separator 7 and is located at the upper part of the internal space.
  • the gas refrigerant accumulates in the upper part of the internal space. Therefore, the gas refrigerant is discharged from the pipe 9.
  • FIG. 3 is a flowchart showing an example of the processing flow of the control device 70 according to the first embodiment.
  • the control device 70 can determine the excess or deficiency of the amount of the refrigerant in the main circuit 50 based on the degree of supercooling of the refrigerant at the outlet of the condenser 2.
  • the control device 70 calculates the degree of supercooling SC of the refrigerant at the outlet of the condenser 2 based on the discharge pressure P1 measured by the pressure sensor 31 and the temperature T measured by the temperature sensor 32. Specifically, the control device 70 specifies the saturation temperature CT of the refrigerant discharged from the compressor 1 based on the discharge pressure P1 of.
  • control device 70 may define the temperature on the enthalpy of the critical point as the saturation temperature CT, and calculate the supercooling degree SC according to the above equation (1). That is, when the discharge pressure P1 exceeds the pressure at the critical point, the control device 70 determines the temperature at the critical point as the saturation temperature CT.
  • the control device 70 compares the supercooling degree SC with the predetermined threshold value Th1 and determines whether or not SC ⁇ Th1 is satisfied (step S1).
  • the threshold value Th1 for example, a value of the degree of supercooling when the compression ratio of the compressor 1 is near the lower limit of the allowable range can be adopted.
  • the compression ratio is represented by a value obtained by dividing the pressure of the refrigerant at the discharge port 1o (that is, the discharge pressure P1) by the suction pressure which is the pressure of the refrigerant at the suction port 1i.
  • the control device 70 compares the supercooling degree SC with the predetermined threshold value Th2, and determines whether or not SC> Th2 is satisfied (step S2).
  • the threshold Th2 is larger than the threshold Th1.
  • the threshold value Th2 is set so that supercooling can be ensured even with a pressure loss at the assumed maximum length of the liquid pipe 91 shown in FIG.
  • step S2 When SC> Th2 is not satisfied (NO in step S2), that is, when Th2 ⁇ SC ⁇ Th1, the control device 70 determines that the amount of the refrigerant in the main circuit 50 is appropriate, and determines that the amount of the refrigerant in the main circuit 50 is appropriate, and the flow rate adjusting valve 13 and the electromagnetic wave. The valve 14 is maintained as it is and the process returns to step S1.
  • step S2 the control device 70 determines that the amount of the refrigerant in the main circuit 50 is excessive, and steps S3 to S6 as a process for reducing the amount of the refrigerant in the main circuit 50. To execute.
  • step S3 the control device 70 determines whether or not the opening degree of the flow rate adjusting valve 13 is the minimum, that is, whether or not the flow rate adjusting valve 13 is in the closed state.
  • step S4 the control device 70 reduces the opening degree of the flow rate adjusting valve 13 by one step (step S4). As a result, the amount of the refrigerant flowing through the pipe 8 is reduced, and the liquid refrigerant is likely to accumulate in the gas-liquid separator 7. As a result, the amount of refrigerant in the main circuit 50 is reduced. After step S4, the control device 70 returns the process to step S1.
  • the control device 70 determines whether or not the time T1 has elapsed since the opening degree of the flow rate adjusting valve 13 became the minimum (step S5). ).
  • the time T1 is predetermined and is, for example, 10 minutes.
  • the control device 70 has an internal timer for executing step S5, and counts the internal timer when it is determined that the opening degree of the flow rate adjusting valve 13 is the minimum in a state where the internal timer is reset. To start.
  • the control device 70 may determine that the time T1 has elapsed since the opening degree of the flow rate adjusting valve 13 became the minimum because the count value of the internal timer reached the time T1.
  • control device 70 When the time T1 has not elapsed since the opening degree of the flow rate adjusting valve 13 became the minimum (NO in step S5), the control device 70 returns the process to step S1 while maintaining the opening degree of the flow rate adjusting valve 13. ..
  • step S5 When the time T1 has elapsed since the opening degree of the flow rate adjusting valve 13 became the minimum (YES in step S5), the control device 70 resets the internal timer for executing step S5 and opens the solenoid valve 14 (YES in step S5). Step S6). Even if the opening degree of the flow rate adjusting valve 13 is the minimum for the time T1, if SC> Th2 is still satisfied, the control response is poor with the flow rate adjusting valve 13 alone, and the liquid refrigerant is stored in the gas-liquid separator 7. Need to be promoted. By opening the solenoid valve 14, the gas refrigerant stored in the gas-liquid separator 7 is discharged to the pipe 9. As a result, the storage of the liquid refrigerant in the gas-liquid separator 7 is promoted, and the amount of the refrigerant in the main circuit 50 can be reduced. After step S6, the control device 70 returns the process to step S1.
  • step S1 When SC ⁇ Th1 is not satisfied (NO in step S1), the control device 70 determines that the amount of refrigerant in the main circuit 50 is insufficient, and steps S7 to increase the amount of refrigerant in the main circuit 50. Execute S10.
  • step S7 the control device 70 determines whether or not the opening degree of the flow rate adjusting valve 13 is the maximum.
  • step S8 When the opening degree of the flow rate adjusting valve 13 is not the maximum (NO in step S7), the control device 70 raises the opening degree of the flow rate adjusting valve 13 by one step (step S8). As a result, the amount of the refrigerant flowing through the pipe 8 increases, and the liquid refrigerant is easily discharged from the gas-liquid separator 7. As a result, the amount of refrigerant in the main circuit 50 increases. After step S8, the control device 70 returns the process to step S1.
  • the control device 70 determines whether or not the time T2 has elapsed since the opening degree of the flow rate adjusting valve 13 became the maximum (step S9). ).
  • the time T2 is predetermined and is, for example, 10 minutes.
  • the control device 70 has an internal timer for executing step S9, and counts the internal timer when it is determined that the opening degree of the flow rate adjusting valve 13 is the maximum in a state where the internal timer is reset. To start.
  • the control device 70 may determine that the time T2 has elapsed since the opening degree of the flow rate adjusting valve 13 became maximum because the count value of the internal timer reached the time T2.
  • step S9 If the time T2 has not elapsed since the opening of the flow rate adjusting valve 13 became maximum (NO in step S9), the control device 70 returns the process to step S1 while maintaining the opening of the flow rate adjusting valve 13. ..
  • step S10 When the time T2 has elapsed from the maximum opening of the flow rate adjusting valve 13 (YES in step S9), the control device 70 resets the internal timer for executing step S9 and closes the solenoid valve 14 (YES in step S9). Step S10). Even if the opening degree of the flow rate adjusting valve 13 is maximum for the time T2, if SC ⁇ Th1, the control response is poor with the flow rate adjusting valve 13 alone, and the liquid refrigerant is discharged from the gas / liquid separator 7. Need to promote. By closing the solenoid valve 14, the gas refrigerant is stored in the gas-liquid separator 7, and the discharge of the liquid refrigerant is promoted. As a result, the rate of increase in the amount of refrigerant in the main circuit 50 can be increased. After step S10, the control device 70 returns the process to step S1.
  • the control device 70 closes the solenoid valve 14 according to the degree of supercooling being less than the threshold value Th1 and the opening degree of the flow rate adjusting valve 13 being the maximum.
  • the control device 70 opens the solenoid valve 14 according to the supercooling degree SC of the refrigerant flowing through the outlet of the condenser 2 exceeding the threshold value Th2 and the opening degree of the flow rate adjusting valve 13 being the minimum.
  • the threshold Th2 is larger than the threshold Th1. That is, in the case of SC ⁇ Th1 or SC> Th2, first, the amount of refrigerant in the main circuit 50 is adjusted by controlling the opening degree of the flow rate adjusting valve 13.
  • the opening degree of the flow rate adjusting valve 13 is controlled to the limit value, if the control response is poor, the open / closed state of the solenoid valve 14 is controlled.
  • a refrigerant that can take a supercritical state such as a CO 2 refrigerant
  • the pressure range that the refrigerant can take becomes wide, and the range that the amount of the refrigerant of the main circuit 50 should take becomes wide. Even in such a case, according to the refrigeration cycle apparatus 100 according to the first embodiment, the amount of the refrigerant in the main circuit 50 can be appropriately adjusted.
  • Embodiment 2 In the transient operation until the stable state is reached, the discharge pressure P1 of the compressor 1 may rise sharply. Transient operation typically includes operation immediately after startup.
  • the refrigerating cycle apparatus according to the second embodiment appropriately adjusts the amount of the refrigerant in the main circuit 50 in order to avoid such an increase in the discharge pressure P1.
  • FIG. 4 is a diagram showing an internal configuration of the refrigeration cycle device 100A according to the second embodiment. As shown in FIG. 4, the refrigeration cycle device 100A differs from the refrigeration cycle device 100 shown in FIG. 1 in that it includes a pressure sensor 33.
  • the pressure sensor 33 measures the intermediate pressure P2, which is the pressure of the injection port 1p of the compressor 1, and outputs the measurement result to the control device 70.
  • FIG. 5 is a flowchart showing an example of the processing flow of the control device 70 according to the second embodiment.
  • the control device 70 executes the flow shown in FIG. 5 in parallel with the flow shown in FIG.
  • control device 70 determines whether or not the solenoid valve 14 is in the closed state (step S11). When the solenoid valve 14 is in the open state (NO in step S11), the control device 70 returns the process to step S11.
  • the control device 70 compares the discharge pressure P1 of the compressor 1 with the threshold value Th3, and also compares the intermediate pressure P2 of the compressor 1 with the threshold value Th4. do.
  • the control device 70 determines whether or not at least one of the following conditions (1) and (2) is satisfied (step S12).
  • the threshold values Th3 and Th4 are set in advance according to the type of the refrigerant used and the like.
  • the threshold Th3 is, for example, 10 MPa.
  • the threshold Th4 is smaller than the threshold Th3, for example, 8.5 MPa.
  • control device 70 If neither the condition (1) nor the condition (2) is satisfied (NO in step S12), the control device 70 returns the process to step S11.
  • the control device 70 opens the solenoid valve 14 (step S13).
  • the solenoid valve 14 By opening the solenoid valve 14, the gas refrigerant is discharged from the gas-liquid separator 7, and the storage of the liquid refrigerant in the gas-liquid separator 7 is promoted.
  • the amount of refrigerant in the main circuit 50 decreases, and the discharge pressure P1 and the intermediate pressure P2 decrease.
  • Embodiment 3 When the outside air temperature becomes low, the discharge pressure P1 of the compressor 1 decreases. When the discharge pressure P1 decreases, a compressed state (hereinafter, referred to as “overcompression”) in which the intermediate pressure P2 at the injection port 1p becomes higher than the discharge pressure P1 may occur in the compressor 1.
  • overcompression a compressed state in which the intermediate pressure P2 at the injection port 1p becomes higher than the discharge pressure P1 may occur in the compressor 1.
  • FIG. 6 is a diagram showing an example of the internal configuration of the refrigeration cycle apparatus 100B according to the third embodiment.
  • the refrigerating cycle device 100B has a pipe 18, a solenoid valve 19, 20, a capillary tube 22, a pressure sensor 34, and a temperature sensor as compared with the refrigerating cycle device 100 shown in FIG. It differs from 35 in that it is provided.
  • the pipe 18, the solenoid valves 19, 20 and the capillary tube 22 are included in the injection circuit 60.
  • the pipe 18 connects the branch point 21 of the pipe 10 and the suction port 1i of the compressor 1 in the main circuit 50. That is, the pipe 18 causes a part of the refrigerant flowing through the pipe 10 to flow to the suction side of the compressor 1.
  • the branch point 21 is located between the economizer 12 and the injection port 1p.
  • the solenoid valve 19 is provided between the branch point 21 and the injection port 1p in the pipe 10.
  • the solenoid valve 20 is provided in the pipe 18.
  • the solenoid valves 19 and 20 take either an open state or a closed state.
  • the capillary tube 22 is provided between the branch point 21 and the solenoid valve 20 in the pipe 18.
  • the capillary tube 22 decompresses the refrigerant separated from the pipe 10.
  • the pressure sensor 34 measures the suction pressure P3, which is the pressure of the refrigerant on the suction side of the compressor 1, and outputs the measurement result to the control device 70.
  • the temperature sensor 35 measures the outside air temperature AT and outputs the measurement result to the control device 70.
  • FIG. 7 is a flowchart showing an example of the processing flow of the control device 70 according to the third embodiment.
  • the control device 70 executes the flow shown in FIG. 7 in parallel with the flow shown in FIG.
  • control device 70 determines whether or not the solenoid valve 14 is in the open state (step S21).
  • the control device 70 determines whether or not the outside air temperature AT is less than the threshold value Th5 (step S22).
  • the threshold Th5 is, for example, 0 ° C.
  • the control device 70 compares the compression ratio P1 / P3, which is the value obtained by dividing the discharge pressure P1 by the suction pressure P3, with the threshold value Th6, and sets P1 / P3 ⁇ Th6. It is determined whether or not the condition is satisfied (step S23).
  • the threshold Th6 is predetermined to be slightly larger than the compression ratio when overcompression occurs, and is, for example, 1.4. If AT ⁇ Th5 is not satisfied (NO in step S22) or P1 / P3 ⁇ Th6 is not satisfied (NO in step S23), the control device 70 returns the process to step S21.
  • the control device 70 closes the solenoid valves 14 and 19 and opens the solenoid valve 20 (step S24).
  • the solenoid valve 14 By closing the solenoid valve 14, the gas refrigerant is not discharged from the gas-liquid separator 7, and the discharge of the liquid refrigerant from the gas-liquid separator 7 is promoted.
  • the solenoid valve 19 even if overcompression occurs due to the low outside air temperature AT, it is possible to prevent the backflow of the refrigerant from the injection port 1p to the gas-liquid separator 7.
  • the solenoid valve 20 is opened, the refrigerant discharged from the gas-liquid separator 7 is returned to the main circuit 50 through the pipe 18. As a result, the amount of refrigerant in the main circuit 50 increases, and the occurrence of overcompression can be suppressed.
  • the refrigerant passing through the pipe 18 is depressurized by the capillary tube 22. Therefore, the pressure difference of the refrigerant at the confluence of the pipe 18 and the pipe constituting the main circuit 50 can be reduced.
  • the solenoid valve 20 is opened to open the main circuit 50 from the pipe 18. Refrigerant flows rapidly into the pipe. When such a rapid inflow of the refrigerant occurs, foaming may occur in the liquid refrigerant stored in the gas-liquid separator 7.
  • the liquid refrigerant may be discharged from the pipe 9 provided in the upper part of the gas-liquid separator 7.
  • the capillary tube 22 By providing the capillary tube 22, such bubbling and discharge of the liquid refrigerant from the pipe 9 are suppressed. If the difference between the pressure of the refrigerant at the branch point 21 and the suction pressure P3 of the compressor 1 is within the allowable range, the capillary tube 22 may be omitted.
  • step S21 When the solenoid valve 14 is in the closed state (NO in step S21), the control device 70 determines whether or not the solenoid valve 20 is in the open state (step S25). When the solenoid valve 20 is in the closed state (NO in step S25), the control device 70 returns the process to step S21.
  • the control device 70 determines whether or not the outside air temperature AT is less than the threshold value Th5 (step S26). When AT ⁇ Th5 is satisfied (YES in step S26), the control device 70 compares the compression ratio P1 / P3 with the threshold value Th6, and determines whether or not P1 / P3 ⁇ Th6 is satisfied (step S27). When P1 / P3 ⁇ Th6 is satisfied (YES in step S27), the control device 70 returns the process to step S21.
  • the control device 70 opens the solenoid valves 14 and 19 and closes the solenoid valve 20 (step). S28). If NO in step S26 or NO in step S27, it is unlikely that overcompression due to the low outside air temperature AT will occur. Therefore, when the solenoid valve 14 is opened, the gas refrigerant is discharged from the gas-liquid separator 7. When the solenoid valve 19 is opened and the solenoid valve 20 is closed, the refrigerant flows into the injection port 1p, the power consumption is reduced, and the capacity is improved.
  • Embodiment 4 The refrigeration cycle apparatus according to the first embodiment determines the excess or deficiency of the amount of the refrigerant in the main circuit 50 by using the supercooling degree SC of the refrigerant that has passed through the condenser 2.
  • the evaporation temperature ET of the refrigerant sucked into the compressor 1 and the liquid level of the gas-liquid separator 7 are used to exceed the amount of the refrigerant in the main circuit 50. Judge the shortage.
  • FIG. 8 is a diagram showing an example of the internal configuration of the refrigeration cycle apparatus 100C according to the fourth embodiment.
  • the refrigerating cycle apparatus 100C includes a pressure sensor 34 and a liquid level sensor 36 instead of the pressure sensor 31 and the temperature sensor 32 as compared with the refrigerating cycle apparatus 100 shown in FIG. It's different.
  • the pressure sensor 34 measures the suction pressure P3 of the compressor 1 as described in the third embodiment, and outputs the measurement result to the control device 70.
  • the liquid level sensor 36 is a sensor that detects the liquid level (the height of the liquid level) of the gas-liquid separator 7.
  • the liquid level sensor 36 outputs the detection result to the control device 70.
  • the control device 70 calculates the evaporation temperature ET of the refrigerant sucked into the compressor 1 based on the suction pressure P3.
  • the control device 70 stores in advance a correspondence table in which a plurality of evaporation temperature zones and a plurality of height ranges are associated with each other.
  • the control device 70 specifies the evaporation temperature zone to which the evaporation temperature ET belongs among the plurality of evaporation temperature zones, and determines the height range corresponding to the specified evaporation temperature zone among the plurality of height ranges as the target height range. ..
  • the control device 70 controls the opening degree of the flow rate adjusting valve 13 and the open / closed state of the solenoid valve 14 so that the liquid level of the gas-liquid separator 7 falls within the target height range.
  • FIG. 9 is a diagram showing an example of a corresponding table 45 stored in the control device 70 according to the fourth embodiment.
  • the corresponding table 45 associates the evaporation temperature zone below ⁇ 30 ° C. with the height range Rc, and sets the evaporation temperature zone below ⁇ 30 ° C. and below ⁇ 10 ° C. and the height range Rb.
  • the evaporation temperature zone of -10 ° C or higher and the height range Ra are associated.
  • FIG. 10 is a diagram showing an example of a height range set for the gas-liquid separator 7 in the fourth embodiment.
  • the height range Rb corresponding to the evaporation temperature zone of ⁇ 30 ° C. or higher and lower than ⁇ 10 ° C. is set higher than the height range Ra corresponding to the evaporation temperature zone of ⁇ 10 ° C. or higher.
  • the height range corresponding to the lower temperature evaporation temperature zone of any two evaporation temperature zones selected from the plurality of evaporation temperature zones is the higher temperature evaporation temperature zone of the two evaporation temperature zones. It is set higher than the height range corresponding to.
  • the amount of refrigerant in the main circuit 50 is an appropriate amount. Is adjusted to.
  • the refrigerant discharged from the compressor 1 includes the refrigerating machine oil of the compressor 1. Therefore, the refrigerating machine oil is also contained in the liquid refrigerant stored in the gas-liquid separator 7. It is preferable that the refrigerating machine oil discharged from the compressor 1 is recovered by the compressor 1. When the refrigerating machine oil is dissolved in the refrigerant, the liquid refrigerant is discharged from the gas-liquid separator 7 through the pipe 8, and the refrigerating machine oil is recovered in the compressor 1.
  • the refrigerating machine oil is stored in the lower part of the gas-liquid separator 7.
  • the refrigerating machine oil stationed in the lower part of the gas-liquid separator 7 is discharged through the pipe 8 and collected in the compressor 1.
  • the refrigerating machine oil is accumulated in a layer on the liquid refrigerant in the gas-liquid separator 7. In this case, the liquid refrigerant is mainly discharged from the pipe 8, and the refrigerating machine oil is not easily discharged. Therefore, the refrigerating machine oil in the gas-liquid separator 7 is difficult to be recovered by the compressor 1.
  • the control device 70 pipes the liquid level of the gas-liquid separator 7 to the compressor 1 at predetermined intervals in order to allow the compressor 1 to recover the refrigerating machine oil that is insoluble in the refrigerant and has a lighter specific density than the refrigerant.
  • the reference height LV (see FIG. 10) higher than one end 9a of the above is reached.
  • FIG. 11 is a diagram showing the state of the gas-liquid separator 7 when the liquid level reaches the reference height LV.
  • one end 9a of the pipe 9 is located in the gas-liquid separator 7. Since the liquid level reaches the reference height LV higher than the one end 9a of the pipe 9, the one end 9a of the pipe 9 is located in the layer 40 of the refrigerating machine oil stored above the liquid refrigerant. As a result, the refrigerating machine oil can be recovered in the compressor 1 through the pipe 9.
  • FIG. 12 is a flowchart showing the flow of steps S31 to S37 in the processing of the control device 70 according to the fourth embodiment.
  • FIG. 13 is a flowchart showing the flow of steps S38 to S44 in the processing of the control device 70 according to the fourth embodiment.
  • FIG. 14 is a flowchart showing the flow of steps S45 to S47 in the processing of the control device 70 according to the fourth embodiment.
  • the control device 70 determines whether or not the time T3 has elapsed since the control device 70 was started or the liquid level level reached the reference height LV last time (step S31).
  • the time T3 is a predetermined cycle, for example, 60 minutes.
  • the control device 70 has an internal timer for executing step S31, resets the internal timer when the refrigeration cycle device 100C is started, and starts counting the internal timer.
  • the control device 70 may determine YES in step S31 according to the fact that the count value of the internal timer has reached the time T3.
  • the control device 70 calculates the evaporation temperature ET based on the suction pressure P3 and determines whether or not ET ⁇ -30 ° C. is satisfied (step S32). ). When ET ⁇ -30 ° C. is not satisfied (NO in step S32), the control device 70 determines whether or not ⁇ 30 ° C. ⁇ ET ⁇ -10 ° C. is satisfied (step S33).
  • the control device 70 covers the height range Rc corresponding to the evaporation temperature zone below -30 ° C from the corresponding table 45 shown in FIG. Read as.
  • the control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S34).
  • the control device 70 When ⁇ 30 ° C. ⁇ ET ⁇ -10 ° C. is satisfied (YES in step S33), the control device 70 indicates the height corresponding to the evaporation temperature zone of ⁇ 30 ° C. or higher and lower than ⁇ 10 ° C. from the corresponding table 45 shown in FIG.
  • the range Rb is read out as the target height range.
  • the control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S35).
  • the control device 70 sets the height range Ra corresponding to the evaporation temperature zone of ⁇ 10 ° C. or higher from the corresponding table 45 shown in FIG. Read as the target height range.
  • the control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S36).
  • step S37 the control device 70 maintains the opening degree of the flow rate adjusting valve 13 as it is (step S37). After step S37, the control device 70 returns the process to step S31.
  • control device 70 determines whether or not the liquid level level exceeds the upper limit of the target height range (step S38).
  • step S39 the control device 70 determines whether or not the opening degree of the flow rate adjusting valve 13 is the maximum (step S39).
  • step S40 the control device 70 increases the opening degree of the flow rate adjusting valve 13 by one step (step S40).
  • step S41 When the opening degree of the flow rate adjusting valve 13 is maximum (YES in step S39), the control device 70 closes the solenoid valve 14 (step S41). By closing the solenoid valve 14, the gas refrigerant is stored in the gas-liquid separator 7, and the discharge of the liquid refrigerant is promoted. As a result, as the liquid level approaches the target height range, the amount of refrigerant in the main circuit 50 increases. After step S41, the control device 70 returns the process to step S31.
  • step S38 When the liquid level does not exceed the upper limit of the target height range (NO in step S38), that is, when the liquid level level is less than the lower limit of the target height range, the control device 70 controls the opening degree of the flow rate adjusting valve 13. Is the minimum (step S42). When the opening degree of the flow rate adjusting valve 13 is not the minimum (NO in step S42), the control device 70 reduces the opening degree of the flow rate adjusting valve 13 by one step (step S43). As a result, the amount of the refrigerant flowing through the pipe 8 is reduced, and the liquid refrigerant is likely to be stored in the gas-liquid separator 7. As a result, the liquid level approaches the target height range, and the amount of the refrigerant in the main circuit 50 decreases. After step S43, the control device 70 returns the process to step S31.
  • step S43 the control device 70 opens the solenoid valve 14 (step S43).
  • the solenoid valve 14 By opening the solenoid valve 14, the gas refrigerant is discharged from the gas-liquid separator 7, and the liquid refrigerant is more likely to be stored in the gas-liquid separator 7.
  • the control device 70 returns the process to step S31.
  • the control device 70 opens the solenoid valve 14 and adjusts the flow rate until the liquid level reaches the reference height LV.
  • the opening degree of the valve 13 is set to the minimum (that is, closed) (step S45).
  • the flow rate adjusting valve 13 is closed, so that the discharge of the liquid refrigerant from the gas-liquid separator 7 is stopped.
  • the solenoid valve 14 is opened, the gas refrigerant is discharged from the gas-liquid separator 7, and the storage of the liquid refrigerant in the gas-liquid separator 7 is promoted.
  • the reference height LV is higher than one end of the pipe 9.
  • the layer 40 of the refrigerating machine oil is discharged from the pipe 9 and the refrigerating machine oil is recovered in the compressor 1 between the time when the liquid level reaches one end of the pipe 9 and the time when the liquid level reaches the reference height LV.
  • the control device 70 may wait for a certain period of time after the liquid level reaches the reference height LV. As a result, the refrigerating machine oil in the gas-liquid separator 7 is more reliably recovered in the compressor 1.
  • step S46 the control device 70 returns the opening / closing state of the flow rate adjusting valve 13 and the open / closed state of the solenoid valve 14 to the states before the start of step S45 (step S46).
  • step S47 the control device 70 resets the internal timer used for executing step S31 (step S47).
  • step S45 is executed each time the time T3 elapses, and the refrigerating machine oil in the gas-liquid separator 7 is periodically collected in the compressor 1.
  • Embodiment 5 The refrigerating cycle apparatus 100C according to the fourth embodiment determines the excess or deficiency of the amount of the refrigerant in the main circuit 50 by using the evaporation temperature ET of the refrigerant sucked into the compressor 1 and the liquid level height of the gas-liquid separator 7. do.
  • the excess or deficiency of the amount of the refrigerant in the main circuit 50 is determined by using the outside air temperature, the evaporation temperature ET, and the liquid level height of the gas-liquid separator 7.
  • control device 70 determines the target height range according to the outside air temperature AT and the evaporation temperature ET, and adjusts the flow rate so that the liquid level of the gas-liquid separator 7 falls within the target height range.
  • the opening degree of the valve 13 and the open / closed state of the solenoid valve 14 are controlled.
  • FIG. 15 is a diagram showing an example of the internal configuration of the refrigeration cycle apparatus 100D according to the fifth embodiment.
  • the refrigeration cycle device 100D differs from the refrigeration cycle device 100C shown in FIG. 8 in that it further includes a temperature sensor 35.
  • the temperature sensor 35 measures the outside air temperature AT as described in the third embodiment, and outputs the measurement result to the control device 70.
  • the control device 70 stores in advance a correspondence table in which a plurality of evaporation temperature zones and a plurality of height ranges are associated with each of the plurality of outside air temperature zones.
  • FIG. 16 is a diagram showing an example of a corresponding table 46 stored in the control device 70 according to the fifth embodiment.
  • the corresponding table 46 includes a record 46a corresponding to an outside air temperature zone of 10 ° C. or higher and a record 46b corresponding to an outside air temperature zone of less than 10 ° C.
  • Each of the records 46a and 46b associates the evaporation temperature zone of less than -30 ° C, the evaporation temperature zone of -30 ° C or more and less than -10 ° C, and the evaporation temperature zone of -10 ° C or more with the height range. That is, each of the records 46a and 46b is correspondence information in which a plurality of evaporation temperature zones and a plurality of height ranges are associated with each other.
  • the record 46a associates the evaporation temperature zone of less than -30 ° C with the height range Rf, associates the evaporation temperature zone of -30 ° C or more and less than -10 ° C with the height range Re, and evaporates at -10 ° C or more.
  • the record 46b associates the evaporation temperature zone of less than -30 ° C with the height range Ri, associates the evaporation temperature zone of -30 ° C or more and less than -10 ° C with the height range Rh, and evaporates at -10 ° C or more.
  • FIG. 17 is a diagram showing an example of a height range set for the gas-liquid separator 7 in the fifth embodiment.
  • the height range Re Corresponding to the evaporation temperature zone of -30 ° C or higher and lower than -10 ° C.
  • Rh is set higher than the height ranges Rd and Rg corresponding to the evaporation temperature zone of ⁇ 10 ° C. or higher, respectively.
  • the height ranges Rf, Re, and Rd corresponding to the outside air temperature zone of 10 ° C. or higher are set lower than the height ranges Ri, Rh, Rg corresponding to the outside air temperature zone of less than 10 ° C.
  • the plurality of height ranges included in the record corresponding to the high temperature outside air temperature zone among any two outside air temperature zones selected from the plurality of outside air temperature zones are the two outside air temperature zones. It is set lower than the height range contained in the record corresponding to the cold outside air temperature zone.
  • the amount of refrigerant in the main circuit 50 is controlled by controlling the opening degree of the flow rate adjusting valve 13 and the open / closed state of the solenoid valve 14 so that the liquid level level falls within the target height range corresponding to the outside air temperature AT and the evaporation temperature ET. Is adjusted to the appropriate amount.
  • FIG. 18 is a flowchart showing the flow of steps S51 to S59 in the processing of the control device 70 according to the fifth embodiment.
  • step S51 the control device 70 determines whether or not the time T3 has elapsed since the control device 70 was started or the liquid level level reached the reference height LV last time (step S51).
  • the details of step S51 are the same as those of step S31 shown in FIG.
  • control device 70 determines whether or not the outside air temperature AT received from the temperature sensor 35 satisfies AT ⁇ 10 ° C. (step S52).
  • control device 70 When AT ⁇ 10 ° C. is not satisfied (NO in step S52), that is, when AT ⁇ 10 ° C. is satisfied, the control device 70 corresponds to the outside air temperature zone of less than 10 ° C. in the corresponding table 46 shown in FIG. Read the record 46b (S53).
  • control device 70 calculates the evaporation temperature ET based on the suction pressure P3, and determines whether or not ET ⁇ -30 ° C. is satisfied (step S54). When ET ⁇ -30 ° C. is not satisfied (NO in step S54), the control device 70 determines whether or not ⁇ 30 ° C. ⁇ ET ⁇ -10 ° C. is satisfied (step S55).
  • the control device 70 covers the height range Ri corresponding to the evaporation temperature zone below -30 ° C from the record 46b read in step S53. Read as. The control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S56).
  • the control device 70 When -30 ° C ⁇ ET ⁇ -10 ° C is satisfied (YES in step S55), the control device 70 has a height corresponding to the evaporation temperature zone of ⁇ 30 ° C. or higher and lower than ⁇ 10 ° C. from the record 46b read in step S53. The range Rh is read out as the target height range. The control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S57).
  • the control device 70 obtains a height range Rg corresponding to the evaporation temperature zone of ⁇ 10 ° C. or higher from the record 46b read in step S53. Read as the target height range. The control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S58).
  • step S59 the control device 70 returns the process to step S51.
  • FIG. 19 is a flowchart showing the flow of steps S60 to S66 in the processing of the control device 70 according to the fifth embodiment.
  • control device 70 corresponds to the outside air temperature zone of 10 ° C. or higher in the corresponding table 46 shown in FIG. Read the record 46a (S60).
  • control device 70 calculates the evaporation temperature ET based on the suction pressure P3, and determines whether or not ET ⁇ -30 ° C. is satisfied (step S61). When ET ⁇ -30 ° C. is not satisfied (NO in step S61), the control device 70 determines whether or not ⁇ 30 ° C. ⁇ ET ⁇ -10 ° C. is satisfied (step S62).
  • the control device 70 covers the height range Rf corresponding to the evaporation temperature zone below -30 ° C from the record 46a read in step S60. Read as. The control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S63).
  • the control device 70 When ⁇ 30 ° C. ⁇ ET ⁇ -10 ° C. is satisfied (YES in step S62), the control device 70 indicates the height corresponding to the evaporation temperature zone of ⁇ 30 ° C. or higher and lower than ⁇ 10 ° C. from the record 46a read in step S59. Read the range Re as the target height range. The control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S64).
  • the control device 70 sets the height range Rd corresponding to the evaporation temperature zone of ⁇ 10 ° C. or higher from the record 46a read in step S59. Read as the target height range.
  • the control device 70 determines whether or not the liquid level level detected by the liquid level sensor 36 belongs to the target height range (step S65).
  • step S66 the control device 70 returns the process to step S51.
  • control device 70 executes steps S38 to S44 shown in FIG. 13 and then returns the process to step S51, as in the fourth embodiment.
  • step S51 If YES in step S51, the process is returned to step S51 after executing steps S45 to S47 shown in FIG. 14 as in the fourth embodiment.
  • Embodiment 6 In the above embodiments 1 to 5, the economizer 12 exchanges heat between the refrigerant flowing through the pipe 10 and the refrigerant flowing out of the condenser 2. On the other hand, in the refrigerating cycle apparatus according to the sixth embodiment, the economizer 12 exchanges heat between the refrigerant flowing through the pipe 9 and the refrigerant flowing out of the condenser 2.
  • FIG. 20 is a diagram showing an internal configuration of the refrigeration cycle apparatus 100E according to the sixth embodiment.
  • the economizer 12 is arranged between the solenoid valve 14 and the confluence point 11 in the pipe 9.
  • the pipe 8 joins the pipe 9 at the confluence 11 without passing through the economizer 12.
  • the wetness of the refrigerant in the gas-liquid two-phase state flowing into the injection port 1p of the compressor 1 increases, and the ability to lower the temperature of the refrigerant discharged from the compressor 1 can be enhanced. ..
  • the wetness of the refrigerant in the gas-liquid two-phase state is adjusted by the opening degree of the flow rate adjusting valve 13 provided in the pipe 8.
  • Embodiment 7 In the refrigeration cycle apparatus according to the seventh embodiment, the economizer 12 exchanges heat between the refrigerant flowing through the pipe 8 and the refrigerant flowing out of the condenser 2.
  • FIG. 21 is a diagram showing an internal configuration of the refrigeration cycle device 100F according to the seventh embodiment.
  • the economizer 12 is arranged between the flow rate adjusting valve 13 and the confluence point 11 in the pipe 8.
  • the pipe 9 joins the pipe 8 at the confluence 11 without passing through the economizer 12.
  • the economizer 12 can improve the efficiency of heat exchange by utilizing the latent heat of vaporization of the liquid refrigerant flowing through the pipe 8.
  • Embodiment 8 The refrigeration cycle apparatus according to the eighth embodiment can switch the path of the injection circuit 60 shown in FIGS. 1, 20 and 21.
  • FIG. 22 is a diagram showing an internal configuration of the refrigeration cycle device 100G according to the eighth embodiment. As shown in FIG. 22, the refrigerating cycle device 100G differs from the refrigerating cycle device 100 shown in FIG. 1 in that it includes pipes 23 to 30 and three-way valves 47 and 48.
  • the three-way valve 47 has three ports 47a, 47b, 47c, and switches between a state in which the port 47a and the port 47b communicate with each other and a state in which the port 47a and the port 47c communicate with each other.
  • the three-way valve 48 has three ports 48a, 48b, and 48c, and switches between a state in which the port 48a and the port 48b communicate with each other and a state in which the port 48a and the port 48c communicate with each other.
  • the pipe 23 is provided to discharge the liquid refrigerant from the gas / liquid separator 7.
  • the pipe 23 connects the gas-liquid separator 7 and the port 47a of the three-way valve 47.
  • the flow rate adjusting valve 13 is provided in the pipe 23.
  • One end of the pipe 24 is connected to the port 47b of the three-way valve 47.
  • One end of the pipe 25 is connected to the port 47c of the three-way valve 47.
  • the pipe 26 is provided to discharge the gas refrigerant from the gas-liquid separator 7.
  • the pipe 26 connects the gas-liquid separator 7 and the port 48a of the three-way valve 48.
  • the solenoid valve 14 is provided in the pipe 26.
  • One end of the pipe 27 is connected to the port 48b of the three-way valve 48.
  • One end of the pipe 28 is connected to the port 48c of the three-way valve 48.
  • the other end of the pipe 24 is connected to the other end of the pipe 27.
  • the other end of the pipe 25 is connected to the other end of the pipe 28.
  • the pipe 29 connects the connection point 11a of the pipes 24 and 27 and the connection point 11b of the pipes 25 and 28.
  • the pipe 29 passes through the economizer 12. Therefore, heat exchange is performed between the refrigerant flowing through the pipe 29 and the refrigerant passing through the condenser 2.
  • the pipe 30 connects the connection points 11b of the pipes 25 and 28 and the injection port 1p of the compressor 1.
  • the control device 70 switches the three-way valves 47 and 48 to one of the following first to third states.
  • First state A state in which the port 47a and the port 47b of the three-way valve 47 are communicated with each other, and the port 48a and the port 48b of the three-way valve 48 are communicated with each other.
  • Second state A state in which the port 47a and the port 47c of the three-way valve 47 are communicated with each other, and the port 48a and the port 48b of the three-way valve 48 are communicated with each other.
  • Third state A state in which the port 47a and the port 47b of the three-way valve 47 are communicated with each other, and the port 48a and the port 48c of the three-way valve 48 are communicated with each other.
  • connection point 11a When the three-way valves 47 and 48 are switched to the first state, the refrigerant that has passed through the flow rate adjusting valve 13 is flowed to the connection point 11a, and the refrigerant that has passed through the solenoid valve 14 is flowed to the connection point 11a.
  • the refrigerant merged at the connection point 11a flows through the pipes 29 and 30 to the compressor 1 after heat exchange with the refrigerant passing through the condenser 2 by the economizer 12.
  • the path of the injection circuit 60 of the first embodiment is realized. That is, the pipes 23 and 24 constitute the pipe 8 of FIG. 1, the pipes 26 and 27 form the pipe 9 of FIG. 1, and the pipes 29 and 30 form the pipe 10 of FIG.
  • the connection point 11a corresponds to the confluence point 11 in FIG.
  • the refrigerant that has passed through the flow rate adjusting valve 13 is flowed to the connection point 11b.
  • the refrigerant that has passed through the solenoid valve 14 flows through the pipes 27 and 29 to the connection point 11b. That is, the refrigerant that has passed through the solenoid valve 14 exchanges heat with the refrigerant that has passed through the condenser 2 in the economizer 12, and then merges with the refrigerant that has passed through the flow rate adjusting valve 13 at the connection point 11b.
  • the refrigerant that has passed through the flow rate adjusting valve 13 does not pass through the economizer 12.
  • connection point 11b The refrigerant merged at the connection point 11b flows to the compressor 1 through the pipe 30.
  • the path of the injection circuit 60 of the sixth embodiment is realized. That is, the pipes 23 and 25 constitute the pipe 8 of FIG. 20, the pipes 26, 27 and 29 form the pipe 9 of FIG. 20, and the pipe 30 constitutes the pipe 10 of FIG. 20.
  • the connection point 11b corresponds to the confluence point 11 in FIG.
  • the refrigerant that has passed through the solenoid valve 14 is flowed to the connection point 11b.
  • the refrigerant that has passed through the flow rate adjusting valve 13 flows through the pipes 24 and 29 to the connection point 11b. That is, the refrigerant that has passed through the flow control valve 13 exchanges heat with the refrigerant that has passed through the condenser 2 in the economizer 12, and then merges with the refrigerant that has passed through the solenoid valve 14 at the connection point 11b.
  • the refrigerant that has passed through the solenoid valve 14 does not pass through the economizer 12.
  • the refrigerant merged at the connection point 11b flows to the compressor 1 through the pipe 30.
  • the path of the injection circuit 60 of the seventh embodiment is realized. That is, the pipes 23, 24, and 29 constitute the pipe 8 in FIG. 21, the pipes 26 and 28 form the pipe 9 in FIG. 21, and the pipe 30 constitutes the pipe 10 in FIG.
  • the connection point 11b corresponds to the confluence point 11 in FIG.
  • the three-way valves 47 and 48 switch the pipe passing through the economizer 12 to any of the pipe 8, the pipe 9, and the pipe 10.
  • the three-way valves 47 and 48 When the three-way valves 47 and 48 are in the first state, the refrigerant flowing through the main circuit 50 is efficiently supercooled, and the performance of the refrigeration cycle device 100G is enhanced.
  • the liquid refrigerant that has passed through the flow rate adjusting valve 13 is directly sent to the compressor 1 without passing through the economizer 12. Therefore, it becomes easy to lower the discharge temperature of the compressor 1.
  • the three-way valves 47 and 48 are in the third state, only the liquid refrigerant that has passed through the flow rate adjusting valve 13 passes through the economizer 12, so that the gas refrigerant is sent to the compressor 1. Therefore, it becomes easy to raise the discharge temperature of the compressor 1.
  • the control device 70 may set the three-way valves 47 and 48 to the first state except when the discharge temperature of the compressor 1 changes transiently. Then, the control device 70 may switch the three-way valves 47 and 48 to the second state when the discharge temperature of the compressor 1 rises sharply (for example, when the temperature reaches 115 ° C. or higher). Further, if the discharge temperature drops and the degree of superheat of the discharged refrigerant cannot be secured (for example, when the degree of superheat is 20 K or less), the control device 70 can switch the three-way valves 47 and 48 to the third state. good.
  • the injection circuit 60 may be provided with the pipe 18, the solenoid valves 19, 20 and the capillary tube 22 as in the third embodiment.
  • the liquid level sensor 36 detects the liquid level of the gas-liquid separator 7. Therefore, in order to accurately detect the liquid level, it is preferable that the liquid level is stable in the gas-liquid separator 7.
  • the capillary tube 22 is provided between the branch point 21 and the solenoid valve 20 in the pipe 18.

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

Abstract

Selon la présente invention, un circuit d'injection (60) comprend : un séparateur gaz-liquide (7) pour séparer une partie d'un fluide frigorigène en gaz et en liquide ; un premier tuyau (8) pour évacuer un fluide frigorigène liquide du séparateur gaz-liquide (7) ; un deuxième tuyau (9) pour évacuer un fluide frigorigène gazeux du séparateur gaz-liquide (7) ; un troisième tuyau (10) pour amener les fluides frigorigènes s'écoulant à travers le premier tuyau (8) et le deuxième tuyau (9) à fusionner et à s'écouler dans un orifice d'injection (1p) d'un compresseur (1) ; une vanne de réglage de débit (13) disposée dans le premier tuyau (8) ; et une électrovanne (14) disposée dans le deuxième tuyau (9). Un dispositif à cycle de réfrigération (100) est pourvu d'un dispositif de commande (70) pour régler la quantité de fluide frigorigène dans un circuit principal (50) en réglant le degré d'ouverture de la vanne de réglage de débit (13) et de l'état d'ouverture/fermeture de l'électrovanne (14).
PCT/JP2020/046094 2020-12-10 2020-12-10 Dispositif à cycle de réfrigération Ceased WO2022123736A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
PCT/JP2020/046094 WO2022123736A1 (fr) 2020-12-10 2020-12-10 Dispositif à cycle de réfrigération
JP2022567979A JP7433476B2 (ja) 2020-12-10 2020-12-10 冷凍サイクル装置
EP20965118.1A EP4261475A4 (fr) 2020-12-10 2020-12-10 Dispositif à cycle de réfrigération

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CN115264643A (zh) * 2022-07-18 2022-11-01 青岛海信日立空调系统有限公司 一种空调系统及其控制方法
WO2024204176A1 (fr) * 2023-03-31 2024-10-03 ダイキン工業株式会社 Dispositif de réfrigération
CN119778898A (zh) * 2024-12-30 2025-04-08 哈尔滨工业大学 一种蒸气压缩式热泵系统控制及蒸气压缩式热泵系统

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JP2010127531A (ja) * 2008-11-27 2010-06-10 Mitsubishi Electric Corp 冷凍空調装置
JP2016156557A (ja) 2015-02-24 2016-09-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置
WO2017037788A1 (fr) * 2015-08-28 2017-03-09 三菱電機株式会社 Dispositif à cycle de réfrigération

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US8671703B2 (en) * 2007-05-14 2014-03-18 Carrier Corporation Refrigerant vapor compression system with flash tank economizer
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JP2010127531A (ja) * 2008-11-27 2010-06-10 Mitsubishi Electric Corp 冷凍空調装置
JP2016156557A (ja) 2015-02-24 2016-09-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 冷凍サイクル装置
WO2017037788A1 (fr) * 2015-08-28 2017-03-09 三菱電機株式会社 Dispositif à cycle de réfrigération

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN115264643A (zh) * 2022-07-18 2022-11-01 青岛海信日立空调系统有限公司 一种空调系统及其控制方法
WO2024204176A1 (fr) * 2023-03-31 2024-10-03 ダイキン工業株式会社 Dispositif de réfrigération
JP2024145993A (ja) * 2023-03-31 2024-10-15 ダイキン工業株式会社 冷凍装置
JP7670996B2 (ja) 2023-03-31 2025-05-01 ダイキン工業株式会社 冷凍装置
CN119778898A (zh) * 2024-12-30 2025-04-08 哈尔滨工业大学 一种蒸气压缩式热泵系统控制及蒸气压缩式热泵系统

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EP4261475A4 (fr) 2023-12-27
JPWO2022123736A1 (fr) 2022-06-16
EP4261475A1 (fr) 2023-10-18

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