WO2022013982A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2022013982A1
WO2022013982A1 PCT/JP2020/027550 JP2020027550W WO2022013982A1 WO 2022013982 A1 WO2022013982 A1 WO 2022013982A1 JP 2020027550 W JP2020027550 W JP 2020027550W WO 2022013982 A1 WO2022013982 A1 WO 2022013982A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
flow path
expansion valve
intermediate pressure
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2020/027550
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
智隆 石川
悠介 有井
素 早坂
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 EP20945603.7A priority Critical patent/EP4184077A4/en
Priority to PCT/JP2020/027550 priority patent/WO2022013982A1/ja
Priority to CN202080102936.9A priority patent/CN115867755A/zh
Priority to JP2022536049A priority patent/JP7367222B2/ja
Publication of WO2022013982A1 publication Critical patent/WO2022013982A1/ja
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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity 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
    • F25B1/00—Compression machines, plants or systems with non-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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for expansion valves or capillary tubes
    • 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—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/072—Intercoolers therefor
    • 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
    • F25B2600/2501—Bypass valves

Definitions

  • This disclosure relates to a refrigeration cycle device.
  • Patent Document 1 describes a refrigerant circuit in which a refrigerant circulates in a compressor, a condenser, a supercooler, an expansion valve, and an evaporator, and a refrigerant condensed by the condenser.
  • a refrigeration cycle apparatus including an injection circuit for returning to a compressor is disclosed. This injection circuit switches between gas injection, in which the refrigerant flowing through the injection circuit is evaporated by the supercooler and then returned to the compressor, and liquid injection, in which the refrigerant flowing through the injection circuit is returned to the compressor without passing through the supercooler. Includes flow path switching means.
  • the compressor includes a low pressure side compression part, an intermediate pressure chamber, and a high pressure side compression part.
  • the low-pressure side compression unit sucks and adiabatically compresses the refrigerant evaporated by the evaporator and discharges it to the intermediate pressure chamber.
  • the high-pressure side compression unit sucks and adiabatically compresses the refrigerant in the intermediate pressure chamber and discharges it to the condenser.
  • the pressure P of the refrigerant, the volume V of the refrigerant, the temperature T of the refrigerant, and the specific heat ratio ⁇ of the refrigerant satisfy the following relational expressions (1) and (2). ..
  • the specific heat ratio ⁇ is relative.
  • the temperature Td (discharge temperature) of the refrigerant when discharged from the compressor is likely to rise, and it is necessary to suppress the rise in the discharge temperature.
  • the flow rate of the refrigerant returned from the injection circuit to the compressor increases.
  • the refrigerant having a relatively low specific heat ratio ⁇ is filled in the refrigerating cycle apparatus.
  • the pressure (intermediate pressure) of the refrigerant returned from the injection circuit to the compressor is likely to rise, so the high-pressure refrigerant discharged from the compressor and the intermediate-pressure refrigerant returned from the injection circuit to the compressor The pressure difference becomes smaller. That is, in the former case, as compared with the latter case, it is difficult to obtain the injection flow rate required to suppress the increase in the discharge temperature, and it is difficult to reliably suppress the increase in the discharge temperature.
  • a main object of the present disclosure is to provide a refrigerating cycle apparatus capable of reliably suppressing an increase in discharge temperature even in a refrigerant having a high specific heat ratio.
  • the refrigeration cycle apparatus includes a compressor, a condenser, a first expansion valve, and an evaporator, and a first refrigerant circuit in which a refrigerant circulates in order through the compressor, the condenser, the first expansion valve, and the evaporator.
  • the compressor has a discharge port for discharging the refrigerant of the first pressure, a suction port for sucking the refrigerant of the second pressure lower than the first pressure, and a refrigerant having an intermediate pressure between the first pressure and the second pressure. It has an inflowing intermediate pressure port.
  • the refrigeration cycle apparatus has a first end connected between the condenser and the first expansion valve in the first refrigerant circuit and a second end connected to the intermediate pressure port of the compressor to condense. It is further provided with an intermediate pressure injection flow path that returns a part of the refrigerant flowing out of the vessel to the compressor.
  • the intermediate pressure injection flow path includes a second expansion valve, a bypass flow path that bypasses the second expansion valve, and a control valve that adjusts the flow rate of the refrigerant flowing through the bypass flow path.
  • FIG. 1 It is a block diagram which shows the refrigeration cycle apparatus which concerns on Embodiment 1.
  • FIG. 2 It is a block diagram which shows the 1st modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2 It is a block diagram which shows the 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. It is a block diagram which shows the 3rd modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. It is a block diagram which shows the refrigeration cycle apparatus which concerns on Embodiment 3.
  • FIG. 3 shows the 1st modification of the refrigerating cycle apparatus which concerns on Embodiment 3.
  • FIG. 1 shows the 1st modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • FIG. is a block diagram which shows the 3rd modification of the refrigerating cycle apparatus which concerns on Embodiment 4.
  • the refrigeration cycle device 100 includes a first refrigerant circuit and an intermediate pressure injection flow path 13.
  • the first refrigerant circuit and the intermediate pressure injection flow path 13 are filled with the first refrigerant (hereinafter, simply referred to as a refrigerant).
  • the refrigerant may be any refrigerant.
  • the refrigeration cycle device 100 is suitable for a refrigerant having a high specific heat ratio.
  • the specific heat ratio of the refrigerant is, for example, 1.16 or more.
  • the refrigerant comprises at least one selected from the group consisting of, for example, CO 2 , ammonia (NH 3 ), R32, R434A, R410A, and R407H.
  • the first refrigerant circuit includes a compressor 1, a condenser 2, a first expansion valve 3, and an evaporator 4.
  • the first refrigerant circulates through the compressor 1, the condenser 2, the first expansion valve 3, and the evaporator 4 in the order described.
  • the compressor 1 has a discharge port for discharging a refrigerant having a first pressure, a suction port for sucking a refrigerant having a second pressure lower than the first pressure, and an intermediate pressure between the first pressure and the second pressure. It has an intermediate pressure port into which the refrigerant of the above is injected.
  • the discharge port is connected to the refrigerant inflow portion of the condenser 2.
  • the suction port is connected to the refrigerant outflow portion of the evaporator 4.
  • the intermediate pressure port is connected to the second end of the intermediate pressure injection flow path 13, which will be described later.
  • the compressor 1 is, for example, a multi-stage compressor.
  • the compressor 1 connects a high-pressure side compression unit connected to the discharge port, a low-pressure side compression unit connected to the suction port, and a high-pressure side compression unit and a low-pressure side compression unit connected to the intermediate pressure port. Includes an intermediate pressure chamber.
  • the refrigerant of the second pressure sucked from the suction port is adiabatically compressed to be the refrigerant of the intermediate pressure, and is discharged to the intermediate pressure chamber.
  • the intermediate-pressure refrigerant sucked from the intermediate pressure chamber is adiabatically compressed to be the first-pressure refrigerant, and is discharged from the discharge port to the outside of the compressor 1.
  • the condenser 2 In the condenser 2, the refrigerant discharged from the discharge port of the compressor 1 is condensed.
  • the condenser 2 has a refrigerant inflow section into which the refrigerant flows, a heat exchange section in which the refrigerant exchanges heat with a heat medium such as air, and a refrigerant outflow section in which the refrigerant flows out.
  • the first expansion valve 3 the refrigerant condensed in the condenser 2 adiabatically expands.
  • the first expansion valve 3 is, for example, an electronic expansion valve.
  • the evaporator 4 the refrigerant decompressed by the first expansion valve 3 evaporates.
  • the evaporator 4 has a refrigerant inflow section into which the refrigerant flows, a heat exchange section in which the refrigerant exchanges heat with a heat medium such as air, and a refrigerant outflow section in which the refrigerant flows out. The refrigerant vaporized by the evaporator 4 is sucked into the suction port of the compressor 1.
  • the refrigerant flow path connecting the refrigerant outflow portion of the condenser 2 and the first expansion valve 3 is called the first flow path 10
  • the first expansion valve 3 and the refrigerant inflow portion of the evaporator 4 are referred to as a first flow path 10.
  • the connecting flow path is called the second flow path 11
  • the flow path connecting the refrigerant outflow portion of the evaporator 4 and the suction port of the compressor 1 is called the third flow path 12.
  • the condenser 2 is a heat source side heat exchanger and the evaporator 4 is a load side heat exchanger.
  • a part of each of the passage 11 and the third flow path 12 is arranged in the heat source side unit (outdoor unit).
  • the evaporator 4, and the other part of each of the second flow path 11 and the third flow path 12 are arranged in the load side unit (indoor unit).
  • the rest of each of the second flow path 11 and the third flow path 12 is arranged in the pipe connecting the heat source side unit and the load side unit.
  • the intermediate pressure injection flow path 13 includes a second expansion valve 5, a bypass flow path 14 that bypasses the second expansion valve, and a control valve 15 that adjusts the flow rate of the refrigerant flowing through the bypass flow path 14.
  • the first end of the intermediate pressure injection flow path 13 is connected to the first flow path 10 of the first refrigerant circuit.
  • the second end of the intermediate pressure injection flow path 13 is connected to the intermediate pressure port of the compressor.
  • the intermediate pressure injection flow path 13 returns a part of the refrigerant condensed by the condenser 2 to the compressor 1 when the opening degree of the second expansion valve 5 is larger than zero.
  • the refrigerant flowing through the intermediate pressure injection flow path 13 adiabatically expands.
  • the second expansion valve 5 is, for example, an electronic expansion valve.
  • the opening degree of the second expansion valve 5 is controlled by a control unit 210, which will be described later, to increase or decrease.
  • the flow rate of the refrigerant flowing through the intermediate pressure injection flow path 13 increases or decreases according to the opening degree of the second expansion valve 5.
  • the opening degree of the second expansion valve 5 is zero, that is, when the second expansion valve 5 is closed, all the refrigerant condensed by the condenser 2 flows into the first expansion valve 3, and the refrigerant has an intermediate pressure. It does not flow into the injection flow path 13.
  • the opening degree of the second expansion valve 5 is larger than zero, a part of the refrigerant condensed by the condenser 2 flows through the intermediate pressure injection flow path 13.
  • bypass flow path 14 One end of the bypass flow path 14 is connected to a portion of the intermediate pressure injection flow path 13 located on the upstream side of the second expansion valve 5.
  • the other end of the bypass flow path 14 is connected to a portion of the intermediate pressure injection flow path 13 located on the downstream side of the second expansion valve 5.
  • the adjusting valve 15 may have an arbitrary configuration as long as the flow rate of the refrigerant flowing through the bypass flow path 14 can be adjusted, but is, for example, an on-off valve, and a more specific example is a solenoid valve.
  • the opening degree of the adjusting valve 15 when the temperature of the high-pressure refrigerant discharged from the discharge port is higher than the determination value is the opening degree of the adjusting valve 15 when the temperature of the high-pressure refrigerant discharged from the discharge port is equal to or less than the determination value. It is high compared to the opening.
  • the refrigeration cycle device 100 includes a temperature sensor 200 that measures the temperature (discharge temperature) of the refrigerant discharged from the compressor 1, and a control unit that controls the opening degrees of the second expansion valve 5 and the adjustment valve 15 according to the discharge temperature. Further equipped with 210.
  • the temperature sensor 200 is, for example, a thermistor.
  • the control unit 210 includes a CPU (Central Processing Unit) (not shown), a memory (ROM (Read Only Memory) and RAM (Random Access Memory)) (not shown), an input / output buffer (not shown) for inputting / outputting various signals, and the like. Consists of including.
  • the CPU expands the program stored in the ROM into a RAM or the like and executes it.
  • the program stored in the ROM is a program in which the processing procedure of the control unit 210 is described.
  • the control unit 210 controls the second expansion valve 5 and the regulating valve 15 according to these programs.
  • the control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).
  • the control unit 210 determines whether or not the discharge temperature measured by the temperature sensor 200 is equal to or less than the determination value.
  • the control unit 210 keeps the second expansion valve 5 and the adjusting valve 15 closed while the discharge temperature is equal to or lower than the determination value.
  • the control unit 210 opens the second expansion valve 5 when the discharge temperature becomes higher than the determination value. If the discharge temperature is still higher than the determination value even when the second expansion valve 5 is fully opened, the control unit 210 opens the adjustment valve 15.
  • the control unit 210 keeps the second expansion valve 5 and the adjusting valve 15 open while the discharge temperature is higher than the determination value.
  • the control unit 210 closes the second expansion valve 5 when the discharge temperature falls below the determination value again.
  • the control unit 210 makes the above determination continuously or intermittently while the refrigeration cycle device 100 is operating.
  • control unit 210 may open at least one of the second expansion valve 5 and the adjustment valve 15, and opens the second expansion valve 5 and the adjustment valve 15 at the same time. You may.
  • the operation and effect of the refrigeration cycle device 100 will be described based on the comparison with the refrigeration cycle device according to the comparative example.
  • the refrigeration cycle apparatus according to Comparative Example 1 is different from the refrigeration cycle apparatus 100 only in that the injection flow path does not include the bypass flow path 14 and the regulating valve 15.
  • the refrigerating cycle device according to Comparative Example 2 is different from the refrigerating cycle device 100 in that it does not include an injection flow path and a second expansion valve, a bypass flow path 14 and a regulating valve 15 included therein.
  • the refrigerating cycle apparatus according to Comparative Example 1 when the refrigerant having a high specific heat ratio is filled, it is difficult to suppress the discharge temperature to the determination value or less even if the second expansion valve is fully opened.
  • the specific heat ratio of the refrigerant is 1.16 or more
  • the evaporation temperature may be ⁇ 10 ° C.
  • the condensation temperature may be 45 ° C.
  • the suction super heat may be 10K during the operation of the refrigeration cycle apparatus according to Comparative Example 1.
  • the discharge temperature exceeds 100 ° C. Therefore, when the determination value is 100 ° C. as described above, it is difficult to suppress the discharge temperature to the determination value or less even if the second expansion valve is fully opened.
  • the intermediate pressure injection flow path 13 includes the bypass flow path 14 and the adjusting valve 15. Therefore, when the refrigerating cycle device 100 having the same opening degree of the second expansion valve 5 and the refrigerating cycle device according to Comparative Example 1 are compared, the intermediate pressure of the refrigerating cycle device 100 when the adjusting valve 15 is further opened.
  • the flow rate of the refrigerant flowing through the injection flow path 13 is larger than the flow rate of the refrigerant flowing through the intermediate pressure injection flow path of the refrigeration cycle apparatus according to Comparative Example 1. Therefore, the refrigerating cycle apparatus 100 can surely suppress an increase in the discharge temperature even in a refrigerant having a high specific heat ratio as compared with the refrigerating cycle apparatus according to Comparative Example 1.
  • the time for flowing the refrigerant through the intermediate pressure injection flow path 13 in order to suppress an increase in the discharge temperature can be shortened. That is, in the refrigerating cycle device 100, the time from the detection of the increase in the discharge temperature to the restart of the normal operation can be shortened as compared with the refrigerating cycle device according to Comparative Example 1. Therefore, in the refrigerating cycle device 100, as compared with the refrigerating cycle device according to Comparative Example 1, the capacity decrease due to the process of suppressing the increase in the discharge temperature is suppressed.
  • the first refrigerant circuit may include a switching unit such as a four-way valve for switching the flow direction of the refrigerant.
  • a switching unit such as a four-way valve for switching the flow direction of the refrigerant.
  • the heat source side heat exchanger acts as a condenser and the load side heat exchanger acts as an evaporator, and the heat source side heat exchanger acts as an evaporator by the switching unit.
  • the heating operation in which the load side heat exchanger acts as a condenser is switched.
  • the refrigerating cycle apparatus 101 according to the second embodiment has basically the same configuration as the refrigerating cycle apparatus 100 according to the first embodiment, but the intermediate pressure injection flow path 13 is the first. It differs from the refrigeration cycle device 100 in that it further includes a cooling unit 6. In FIG. 2, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerant decompressed by the second expansion valve 5 is cooled.
  • the first cooling unit 6 is arranged between the second expansion valve 5 and the intermediate pressure port of the compressor 1 in the intermediate pressure injection flow path 13.
  • the first cooling unit 6 is arranged between the other end of the bypass flow path 14 and the intermediate pressure port of the compressor 1 in the intermediate pressure injection flow path 13.
  • the other end of the bypass flow path 14 is connected to a portion of the intermediate pressure injection flow path 13 located on the downstream side of the second expansion valve 5 and on the upstream side of the first cooling unit 6. ..
  • the other end of the bypass flow path 14 may be connected to a portion of the intermediate pressure injection flow path 13 located on the downstream side of the first cooling unit 6.
  • the first cooling unit 6 has a refrigerant inflow unit into which the refrigerant flows, a heat exchange unit in which the refrigerant exchanges heat with a cold heat source such as air, and a refrigerant outflow unit in which the refrigerant flows out. As the refrigerant is cooled in the first cooling unit 6, the dryness of the refrigerant decreases. The refrigerant cooled by the first cooling unit 6 is sucked from the intermediate pressure port of the compressor 1.
  • the refrigeration cycle device 101 also includes an intermediate pressure injection flow path 13 including a bypass flow path 14 and a regulating valve 15, the same effect as that of the refrigeration cycle device 100 can be obtained.
  • the intermediate pressure injection flow path 13 includes the first cooling unit 6. Also in the refrigeration cycle device 101, when the discharge temperature becomes higher than the determination value, the second expansion valve 5 is opened. As a result, a part of the refrigerant condensed in the condenser 2 flows into the intermediate pressure injection flow path 13. The refrigerant flowing into the intermediate pressure injection flow path 13 is adiabatically expanded by the second expansion valve 5 and depressurized to become an intermediate pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is cooled by a cold heat source in the first cooling unit 6 to become a low-temperature gas-liquid two-phase refrigerant. The low-temperature gas-liquid two-phase refrigerant is injected into the intermediate pressure chamber from the intermediate pressure port of the compressor 1.
  • the temperature of the refrigerant injected into the intermediate pressure chamber from the intermediate pressure port of the compressor 1 in the refrigeration cycle device 101 is higher than the temperature of the refrigerant injected into the intermediate pressure chamber from the intermediate pressure port of the compressor in the refrigeration cycle device 100. Also becomes low. Therefore, in the refrigerating cycle device 101, an increase in the discharge temperature can be suppressed even when the flow rate of the refrigerant in the intermediate pressure injection flow path 13 is smaller than that in the refrigerating cycle device 100. That is, in the refrigerating cycle device 101, even when the specific heat ratio of the filled refrigerant is high, the increase in the discharge temperature can be suppressed as compared with the refrigerating cycle device 100.
  • Modification example 3 to 5 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 101 shown in FIG. 2.
  • the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 102 shown in FIG. 3 has basically the same configuration as the refrigerating cycle device 101, but further includes a second refrigerant circuit 20 in which the second refrigerant circulates, and the first cooling unit 6 cools the refrigerant with respect to the refrigerant. It differs from the refrigeration cycle device 101 in that the source is a second refrigerant.
  • the second refrigerant may be any refrigerant.
  • the specific heat ratio of the second refrigerant is, for example, lower than the specific heat ratio of the first refrigerant.
  • the specific heat ratio of the second refrigerant may be, for example, equal to the specific heat ratio of the first refrigerant.
  • the second refrigerant circuit 20 includes a second compressor 21, a second condenser 22, a third expansion valve 23, and a first cooling unit 6.
  • the second refrigerant circulates in the second compressor 21, the second condenser 22, the third expansion valve 23, and the first cooling unit 6 in the order described.
  • the first cooling unit 6 the second refrigerant flowing through the second refrigerant circuit 20 absorbs heat of vaporization from the refrigerant flowing through the intermediate pressure injection flow path 13 and evaporates.
  • the first cooling unit 6 cools the refrigerant flowing through the intermediate pressure injection flow path 13 with the second refrigerant flowing through the second refrigerant circuit 20.
  • the operating conditions of the second compressor 21 and the third expansion valve 23 are set so that the second refrigerant flowing through the first cooling unit 6 can sufficiently cool the refrigerant flowing through the intermediate pressure injection flow path 13.
  • the refrigerating cycle device 102 also has an intermediate pressure injection flow path 13 including a bypass flow path 14, a regulating valve 15, and a first cooling unit 6, and thus has the same effect as the refrigerating cycle device 101. be able to.
  • the refrigerating cycle device 103 shown in FIG. 4 has basically the same configuration as the refrigerating cycle device 101, but the first cooling unit 6 is an internal heat exchanger, and the intermediate pressure injection flow in the first cooling unit 6. It differs from the refrigeration cycle device 101 in that the cooling heat source for the refrigerant flowing through the passage 13 is the refrigerant flowing between the first expansion valve 3 and the suction port of the compressor 1.
  • the refrigerant flowing through the intermediate pressure injection flow path 13 exchanges heat with the refrigerant flowing through the second flow path 11.
  • the second expansion valve 5 is opened.
  • the opening degree of the second expansion valve 5 is set so that the amount of decrease in the pressure of the refrigerant in the second expansion valve 5 is smaller than the amount of decrease in the pressure of the refrigerant in the first expansion valve 3.
  • the second expansion valve 5 is fully opened.
  • the flow rate of the refrigerant flowing through the second expansion valve 5 is maximized, and the temperature of the refrigerant adiabatically expanded by the second expansion valve 5 is higher than the temperature of the refrigerant adiabatically expanded by the first expansion valve 3.
  • the first cooling unit 6 a relatively large amount of the refrigerant flowing through the intermediate pressure injection flow path 13 is cooled by the refrigerant flowing through the second flow path 11.
  • the refrigerating cycle device 103 also has an intermediate pressure injection flow path 13 including a bypass flow path 14, a regulating valve 15, and a first cooling unit 6, and thus has the same effect as the refrigerating cycle device 101. be able to.
  • the refrigerating cycle device 104 shown in FIG. 5 has basically the same configuration as the refrigerating cycle device 103, but the cooling heat source for the refrigerant flowing through the intermediate pressure injection flow path 13 in the first cooling unit 6 is the evaporator 4. It differs from the refrigeration cycle device 103 in that it is a refrigerant that flows between the suction port of the compressor 1 and the suction port of the compressor 1.
  • the refrigerant flowing through the intermediate pressure injection flow path 13 exchanges heat with the refrigerant flowing through the third flow path 12.
  • the second expansion valve 5 is opened.
  • the second expansion valve 5 is fully opened.
  • the temperature of the refrigerant adiabatically expanded by the second expansion valve 5 is higher than the temperature of the refrigerant adiabatically expanded by the first expansion valve 3 and evaporated by the evaporator 4. Therefore, in the first cooling unit 6, a relatively large amount of the refrigerant flowing through the intermediate pressure injection flow path 13 is cooled by the refrigerant flowing through the third flow path 12.
  • the refrigerating cycle device 104 also has an intermediate pressure injection flow path 13 including a bypass flow path 14, a regulating valve 15, and a first cooling unit 6, and thus has the same effect as the refrigerating cycle device 101. be able to.
  • the refrigerating cycle apparatus 105 according to the third embodiment has basically the same configuration as the refrigerating cycle apparatus 100 according to the first embodiment, but the refrigerant circuit has a second cooling unit 7. It is different from the refrigeration cycle device 100 in that it further includes.
  • the second cooling unit 7 cools the refrigerant flowing between the condenser 2 and the first end of the intermediate pressure injection flow path 13 in the first flow path 10 by the second cooling heat source.
  • the refrigerant condensed by the condenser 2 is supercooled.
  • the second cooling unit 7 acts as a supercooler.
  • the second cooling unit 7 is arranged between the condenser 2 and the first end of the intermediate pressure injection flow path 13 in the refrigerant circuit.
  • the second cooling unit 7 has a refrigerant inflow unit into which the refrigerant flows, a heat exchange unit in which the refrigerant exchanges heat with a second cold heat source such as air, and a refrigerant outflow unit in which the refrigerant flows out.
  • the opening degree of the second expansion valve 5 When the opening degree of the second expansion valve 5 is zero, that is, when the second expansion valve 5 is closed, all the refrigerant condensed by the condenser 2 and supercooled by the second cooling unit 7 is the first. It flows into the expansion valve 3 and the refrigerant does not flow into the intermediate pressure injection flow path 13. When the opening degree of the second expansion valve 5 is larger than zero, a part of the refrigerant condensed by the condenser 2 and supercooled by the second cooling unit 7 flows through the intermediate pressure injection flow path 13.
  • the refrigerating cycle device 105 includes an intermediate pressure injection flow path 13 including a bypass flow path 14 and a regulating valve 15, the same effect as that of the refrigerating cycle device 100 can be obtained.
  • the refrigerating cycle device 105 since the refrigerant circuit includes the second cooling unit 7, the degree of supercooling of the refrigerant flowing into the first expansion valve 3 is higher than that of the refrigerating cycle device 100. As a result, the performance of the refrigerating cycle apparatus 105 is higher than the performance of the refrigerating cycle apparatus 100.
  • (Modification example) 7 to 9 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 105 shown in FIG. In FIGS. 7 to 9, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 106 shown in FIG. 7 has basically the same configuration as the refrigerating cycle device 105, but further includes a third refrigerant circuit 30 in which a third refrigerant circulates, and a first flow in the second cooling unit 7. It differs from the refrigeration cycle device 105 in that the cold heat source (second cold heat source) for the refrigerant flowing through the path 10 is the third refrigerant.
  • the third refrigerant circuit 30 includes a third compressor 31, a third condenser 32, a fourth expansion valve 33, and a second cooling unit 7.
  • the third refrigerant circulates through the third compressor 31, the third condenser 32, the fourth expansion valve 33, and the second cooling unit 7 in the order described.
  • the third refrigerant flowing through the third refrigerant circuit 30 absorbs heat of vaporization from the refrigerant flowing through the first flow path 10 and evaporates.
  • the second cooling unit 7 cools the refrigerant flowing through the first flow path 10 with the third refrigerant flowing through the third refrigerant circuit 30.
  • the operating conditions of the third compressor 31 and the fourth expansion valve 33 are set so that the third refrigerant flowing through the second cooling unit 7 can sufficiently cool the refrigerant flowing through the first flow path 10.
  • the third refrigerant may be any refrigerant.
  • the specific heat ratio of the third refrigerant is, for example, lower than the specific heat ratio of the first refrigerant.
  • the specific heat ratio of the third refrigerant may be, for example, equal to the specific heat ratio of the first refrigerant.
  • the refrigerating cycle device 107 shown in FIG. 8 has basically the same configuration as the refrigerating cycle device 105, but the cooling heat source for the refrigerant flowing through the first flow path 10 in the second cooling unit 7 is the first expansion valve 3. It differs from the refrigeration cycle device 105 in that it is a refrigerant that flows between the compressor 1 and the suction port of the compressor 1. In the second cooling unit 7, the refrigerant flowing through the first flow path 10 exchanges heat with the refrigerant flowing through the second flow path 11.
  • the refrigerating cycle device 108 shown in FIG. 9 has basically the same configuration as the refrigerating cycle device 105, but the cooling heat source for the refrigerant flowing through the first flow path 10 in the second cooling unit 7 is compressed with the evaporator 4. It differs from the refrigerating cycle device 103 in that it is a refrigerant flowing between the suction port of the machine 1. In the second cooling unit 7, the refrigerant flowing through the first flow path 10 exchanges heat with the refrigerant flowing through the third flow path 12.
  • the refrigerating cycle devices 106, 107, and 108 shown in FIGS. 7 to 9 can have the same effect as the refrigerating cycle device 105 because the refrigerant circuit further includes the second cooling unit 7.
  • the refrigerating cycle apparatus 109 according to the fourth embodiment has basically the same configuration as the refrigerating cycle apparatus 100 according to the first embodiment, but the intermediate pressure injection flow path 13 is the first. It differs from the refrigeration cycle device 100 in that it further includes a cooling unit 6 and the refrigerant circuit further includes a second cooling unit 7.
  • the first cooling unit 6 of the refrigeration cycle device 109 has the same configuration as the first cooling unit 6 of the refrigeration cycle device 101 shown in FIG.
  • the second cooling unit 7 of the refrigeration cycle device 109 has the same configuration as the second cooling unit 7 of the refrigeration cycle device 105 shown in FIG.
  • the refrigeration cycle device 109 includes an intermediate pressure injection flow path 13 including a bypass flow path 14 and a regulating valve 15, the same effect as that of the refrigeration cycle device 100 can be obtained.
  • the refrigerating cycle device 109 further includes the first cooling section 6 shown in FIG. 2 and the second cooling section 7 shown in FIG. 6, the effect of the refrigerating cycle device 101 and the effect of the refrigerating cycle device 104. Can be played at the same time.
  • Modification example 11 to 13 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 109 shown in FIG. In FIGS. 11 to 13, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 110 shown in FIG. 11 has basically the same configuration as the refrigerating cycle device 109, but the first cooling unit 6 has the same configuration as the first cooling unit 6 shown in FIG. In that respect, it differs from the refrigeration cycle device 109.
  • the refrigerating cycle apparatus 111 shown in FIG. 12 has basically the same configuration as the refrigerating cycle apparatus 109, but the first cooling unit 6 has the same configuration as the first cooling unit 6 shown in FIG.
  • the second cooling unit 7 differs from the refrigeration cycle device 109 in that the second cooling unit 7 has the same configuration as the second cooling unit 7 shown in FIG. 7.
  • the refrigerating cycle device 112 shown in FIG. 13 has basically the same configuration as the refrigerating cycle device 111, but the first cooling unit 6 has the same configuration as the first cooling unit 6 shown in FIG. In that respect, it differs from the refrigeration cycle device 109.
  • the refrigerating cycle devices 110, 111, 112 shown in FIGS. 11 to 13 include the first cooling unit 6 and the second cooling unit 7 at the same time, the same effect as that of the refrigerating cycle device 109 can be obtained. ..
  • the second cooling unit 7 of the refrigeration cycle apparatus 109, 110, 111, 112 may have the same configuration as any of the second cooling units 7 shown in FIGS. 6 to 9.
  • 1 Compressor 2 Condenser, 3 1st expansion valve, 4 Evaporator, 5 2nd expansion valve, 6 Cooling section, 7 2nd cooling section, 10 1st flow path, 11 2nd flow path, 12 3rd Flow path, 13 Intermediate pressure injection flow path, 14 Bypass flow path, 15 Adjustment valve, 20 Second refrigerant circuit, 21 Second compressor, 22 Second condenser, 23 Third expansion valve, 30 Third refrigerant circuit, 31 3rd compressor, 32nd 3rd condenser, 33rd 4th expansion valve, 100, 101, 102, 103, 104, 105, 106, 107, 108, 109, 110, 111, 112 Refrigerating cycle device, 200 temperature sensor, 210 Control unit.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Air-Conditioning For Vehicles (AREA)
PCT/JP2020/027550 2020-07-15 2020-07-15 冷凍サイクル装置 Ceased WO2022013982A1 (ja)

Priority Applications (4)

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EP20945603.7A EP4184077A4 (en) 2020-07-15 2020-07-15 Refrigeration cycle device
PCT/JP2020/027550 WO2022013982A1 (ja) 2020-07-15 2020-07-15 冷凍サイクル装置
CN202080102936.9A CN115867755A (zh) 2020-07-15 2020-07-15 制冷循环装置
JP2022536049A JP7367222B2 (ja) 2020-07-15 2020-07-15 冷凍サイクル装置

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JP7367222B2 (ja) 2023-10-23
CN115867755A (zh) 2023-03-28

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