WO2022013981A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2022013981A1
WO2022013981A1 PCT/JP2020/027549 JP2020027549W WO2022013981A1 WO 2022013981 A1 WO2022013981 A1 WO 2022013981A1 JP 2020027549 W JP2020027549 W JP 2020027549W WO 2022013981 A1 WO2022013981 A1 WO 2022013981A1
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WIPO (PCT)
Prior art keywords
refrigerant
flow path
intermediate pressure
expansion valve
compressor
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PCT/JP2020/027549
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English (en)
Japanese (ja)
Inventor
智隆 石川
悠介 有井
素 早坂
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2022536048A priority Critical patent/JP7466645B2/ja
Priority to PCT/JP2020/027549 priority patent/WO2022013981A1/fr
Publication of WO2022013981A1 publication Critical patent/WO2022013981A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

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 cooling unit that cools the refrigerant flowing through the intermediate pressure injection flow path by a cold heat source.
  • FIG. 1 shows the refrigeration cycle apparatus which concerns on Embodiment 1.
  • FIG. 2 shows the 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 1.
  • FIG. 2 is a block diagram which shows the 3rd modification of the refrigerating cycle apparatus which concerns on Embodiment 1.
  • FIG. 2 is a block diagram which shows the refrigeration cycle apparatus which concerns on Embodiment 2.
  • FIG. 2 is a block diagram which shows the 1st modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2 shows the 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 1.
  • FIG. is a block diagram which shows the 3rd modification of the refrigerating cycle apparatus which concerns on Embodiment 1.
  • FIG. It is a block diagram which shows the refrigeration cycle apparatus which concerns on Embodiment 2.
  • It is a block diagram which shows the 1st modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 2.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 3.
  • FIG. 2nd modification of the refrigerating cycle apparatus which concerns on Embodiment 3.
  • 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.
  • Each part of each of the flow paths 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 and a cooling unit 6.
  • 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.
  • the refrigerant decompressed by the second expansion valve 5 is cooled.
  • the 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 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.
  • 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
  • a refrigerant outflow unit in which the refrigerant flows out.
  • the refrigeration cycle device 100 further includes a temperature sensor 200 that measures the temperature (discharge temperature) of the refrigerant discharged from the compressor 1, and a control unit 210 that controls the opening degree of the second expansion valve 5 according to the discharge temperature. ..
  • 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 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 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.
  • the control unit 210 keeps the second expansion valve 5 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 becomes equal to or lower than the determination value again.
  • the control unit 210 makes the above determination continuously or intermittently while the refrigeration cycle device 100 is operating.
  • the determination value can be arbitrarily set according to the specifications of the compressor 1 and the operating conditions of the refrigeration cycle device 100, and is, for example, 100 ° C.
  • 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 refrigerating cycle apparatus according to Comparative Example 1 is different from the refrigerating cycle apparatus 100 only in that the injection flow path does not include the cooling unit 6.
  • 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 and a cooling unit 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 cooling unit 6. Also in the refrigeration cycle device 100, 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 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 apparatus 100 is the temperature of the refrigerant injected into the intermediate pressure chamber from the intermediate pressure port of the compressor in the refrigeration cycle apparatus according to Comparative Example 1. It will be lower than the temperature. Therefore, in the refrigerating cycle device 100, the 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 according to Comparative Example 1. That is, in the refrigerating cycle device 100, 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 according to Comparative Example 1.
  • 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.
  • Modification example 2 to 4 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 100 shown in FIG. In FIGS. 2 to 4, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 101 shown in FIG. 2 has basically the same configuration as the refrigerating cycle device 100, but further includes a second refrigerant circuit 20 in which a second refrigerant circulates, and a cooling heat source for the refrigerant is provided in the cooling unit 6. It differs from the refrigeration cycle device 100 in that it 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 cooling unit 6.
  • the second refrigerant circulates in the second compressor 21, the second condenser 22, the third expansion valve 23, and the cooling unit 6 in the order described.
  • the 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 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 cooling unit 6 can sufficiently cool the refrigerant flowing through the intermediate pressure injection flow path 13.
  • the refrigerating cycle device 101 also includes the intermediate pressure injection flow path 13 including the cooling unit 6, it is possible to obtain the same effect as the refrigerating cycle device 100.
  • the refrigerating cycle device 102 shown in FIG. 3 has basically the same configuration as the refrigerating cycle device 100, but the cooling unit 6 is an internal heat exchanger and flows through the intermediate pressure injection flow path 13 in the cooling unit 6. It differs from the refrigeration cycle device 100 in that the cooling heat source for the refrigerant 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. For example, 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 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 102 also includes the intermediate pressure injection flow path 13 including the cooling unit 6, it is possible to obtain the same effect as the refrigerating cycle device 100.
  • the refrigerating cycle device 103 shown in FIG. 4 has basically the same configuration as the refrigerating cycle device 102, but the cooling heat source for the refrigerant flowing through the intermediate pressure injection flow path 13 in the cooling unit 6 is the evaporator 4 and the compressor. It differs from the refrigeration cycle device 102 in that it is a refrigerant flowing between the suction port of 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 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 103 also includes the intermediate pressure injection flow path 13 including the cooling unit 6, it is possible to obtain the same effect as the refrigerating cycle device 100.
  • the refrigerating cycle apparatus 104 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 has two expansion valves 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. ..
  • 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 other end of the bypass flow path 14 is connected to a portion of the intermediate pressure injection flow path 13 located upstream of the 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 cooling unit 6.
  • 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 control unit 210 of the refrigerating cycle device 104 performs basically the same control as the control unit 210 of the refrigerating cycle device 100, but refrigerates in that it controls the opening degree of the adjusting valve 15 in addition to the second expansion valve 5. It is different from the control unit 210 of the cycle device 100.
  • 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 refrigerating cycle device 104 includes an intermediate pressure injection flow path 13 including a cooling unit 6, the same effect as that of the refrigerating cycle device 100 can be obtained.
  • the intermediate pressure injection flow path 13 includes the bypass flow path 14 and the adjusting valve 15. Therefore, comparing the refrigeration cycle device 104 and the refrigeration cycle device 100 in which the opening degrees of the second expansion valve 5 are the same, the intermediate pressure injection flow path 13 of the refrigeration cycle device 104 when the regulating valve 15 is further opened.
  • the flow rate of the refrigerant flowing through the refrigerating cycle device 100 is larger than the flow rate of the refrigerant flowing through the intermediate pressure injection flow path 13 of the refrigeration cycle device 100.
  • the refrigerant flowing through each of the second expansion valve 5 and the bypass flow path 14 is cooled by the cooling unit 6. Therefore, the refrigerating cycle device 104 can surely suppress an increase in the discharge temperature even in a refrigerant having a higher specific heat ratio than the refrigerating cycle device 100.
  • 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 104, 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 100. Therefore, in the refrigerating cycle device 104, as compared with the refrigerating cycle device 100, the decrease in capacity due to the process of suppressing the increase in the discharge temperature is suppressed.
  • Modification example 6 to 8 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 104 shown in FIG. In FIGS. 6 to 8, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 105 shown in FIG. 6 has basically the same configuration as the refrigerating cycle device 104, but further includes a second refrigerant circuit 20 in which a second refrigerant circulates, and a cooling heat source for the refrigerant is provided in the cooling unit 6. It differs from the refrigeration cycle device 104 in that it is a second refrigerant.
  • the cooling unit 6 of the refrigerating cycle device 105 has the same configuration as the cooling unit 6 of the refrigerating cycle device 101 shown in FIG. 2 described above.
  • the refrigerating cycle device 106 shown in FIG. 7 has basically the same configuration as the refrigerating cycle device 104, but the cooling unit 6 is an internal heat exchanger and flows through the intermediate pressure injection flow path 13 in the cooling unit 6. It differs from the refrigeration cycle device 104 in that the cooling heat source for the refrigerant is the refrigerant flowing between the first expansion valve 3 and the suction port of the compressor 1.
  • the cooling unit 6 of the refrigerating cycle device 106 has the same configuration as the cooling unit 6 of the refrigerating cycle device 102 shown in FIG. 3 described above.
  • the refrigerating cycle device 107 shown in FIG. 8 has basically the same configuration as the refrigerating cycle device 106, but the cooling heat source for the refrigerant flowing through the intermediate pressure injection flow path 13 in the cooling unit 6 is the evaporator 4 and the compressor. It differs from the refrigeration cycle device 106 in that it is a refrigerant flowing between the suction port of 1.
  • the cooling unit 6 of the refrigerating cycle device 107 has the same configuration as the cooling unit 6 of the refrigerating cycle device 103 shown in FIG. 4 described above.
  • the refrigerating cycle devices 105, 106, and 107 shown in FIGS. 6 to 8 have an intermediate pressure injection flow path 13 including a bypass flow path 14 and a regulating valve 15, and thus have the same effect as the refrigerating cycle device 104. Can be played.
  • the refrigerating cycle device 108 according to the third embodiment has basically the same configuration as the refrigerating cycle device 100 according to the first embodiment, but the refrigerant circuit is the second cooling unit 7. It is different from the refrigerating cycle apparatus 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 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 second. 1 It flows into the expansion valve 3 and the refrigerant does not flow into the intermediate pressure 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 and supercooled by the second cooling unit 7 flows through the intermediate pressure injection flow path 13.
  • the refrigerating cycle device 108 includes the intermediate pressure injection flow path 13 including the cooling unit 6, it is possible to obtain the same effect as the refrigerating cycle device 100.
  • the refrigerating cycle device 108 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 refrigeration cycle apparatus 108 is higher than that of the refrigeration cycle apparatus 100.
  • Modification example 10 to 12 are block diagrams showing first modification to third modification of the refrigeration cycle apparatus 108 shown in FIG. In FIGS. 10 to 12, the temperature sensor 200 and the control unit 210 are not shown.
  • the refrigerating cycle device 109 shown in FIG. 10 has basically the same configuration as the refrigerating cycle device 108, but further includes a second refrigerant circuit 20 in which a second refrigerant circulates, and a cooling heat source for the refrigerant is provided in the cooling unit 6. It differs from the refrigeration cycle device 108 in that it is a second refrigerant.
  • the cooling unit 6 of the refrigerating cycle device 109 has the same configuration as the cooling unit 6 of the refrigerating cycle device 101 shown in FIG. 2 described above.
  • the refrigerating cycle device 110 shown in FIG. 11 has basically the same configuration as the refrigerating cycle device 108, but the cooling unit 6 is an internal heat exchanger and flows through the intermediate pressure injection flow path 13 in the cooling unit 6. It differs from the refrigeration cycle device 108 in that the cooling heat source for the refrigerant is the refrigerant flowing between the first expansion valve 3 and the suction port of the compressor 1.
  • the cooling unit 6 of the refrigerating cycle device 110 has the same configuration as the cooling unit 6 of the refrigerating cycle device 102 shown in FIG. 3 described above.
  • the refrigerating cycle device 110 further includes a third refrigerant circuit 30 in which the third refrigerant circulates, and the cooling heat source for the refrigerant flowing through the first flow path 10 in the second cooling unit 7 is the third refrigerant. It is different from the refrigeration cycle device 108.
  • 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 111 shown in FIG. 12 has basically the same configuration as the refrigerating cycle device 110, but the cooling heat source for the refrigerant flowing through the intermediate pressure injection flow path 13 in the cooling unit 6 is the evaporator 4 and the compressor. It differs from the refrigeration cycle device 110 in that it is a refrigerant flowing between the suction port of 1.
  • the cooling unit 6 of the refrigerating cycle device 111 has the same configuration as the cooling unit 6 of the refrigerating cycle device 103 shown in FIG. 4 described above.
  • the refrigerating cycle device 110 further includes a third refrigerant circuit 30 in which the third refrigerant circulates, and the cooling heat source for the refrigerant flowing through the first flow path 10 in the second cooling unit 7 is the third refrigerant. It is different from the refrigeration cycle device 108.
  • the second cooling unit 7 of the refrigeration cycle device 111 has the same configuration as the second cooling unit 7 of the refrigeration cycle device 110 shown in FIG. 11 described above.
  • the refrigerating cycle devices 109, 110, and 111 shown in FIGS. 10 to 12 can have the same effect as the refrigerating cycle device 109 because the refrigerant circuit further includes the second cooling unit 7.
  • the second cooling unit 7 of the refrigeration cycle devices 108 and 109 may have the same configuration as the second cooling unit 7 of the refrigeration cycle devices 110 and 111, and the second cooling unit 7 of the refrigeration cycle devices 110 and 111 may have the same configuration.
  • the cooling unit 7 of the above may have the same configuration as the second cooling unit 7 of the refrigeration cycle devices 108 and 109.
  • 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, 100, 101, 102, 103 , 104, 105, 106, 107, 108, 109, 110, 111 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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif à cycle frigorifique (100) qui comprend un circuit de fluide frigorigène (10) comportant un compresseur (1), un condenseur (2), un détendeur (3) et un évaporateur (4), et dans lequel un fluide frigorigène circule dans l'ordre à travers le compresseur, le condenseur, le détendeur et l'évaporateur. Le compresseur comporte un orifice de refoulement qui refoule le fluide frigorigène à une première pression, un orifice d'admission qui aspire le fluide frigorigène à une seconde pression inférieure à la première pression, et un orifice de pression intermédiaire dans lequel le fluide frigorigène s'écoule à une pression intermédiaire entre la première pression et la seconde pression. Le dispositif à cycle frigorifique comprend en outre un trajet d'écoulement d'injection à pression intermédiaire (13) qui présente une première extrémité reliée entre le condenseur et le premier détendeur dans le premier circuit de fluide frigorigène, et une seconde extrémité reliée à l'orifice de pression intermédiaire du compresseur, et qui renvoie, au compresseur, une partie du fluide frigorigène qui s'est écoulée depuis le côté arrière du condenseur. Le trajet d'écoulement d'injection de pression intermédiaire comprend une unité de refroidissement (6) qui refroidit le fluide frigorigène s'écoulant à travers le trajet d'écoulement d'injection de pression intermédiaire au moyen d'une source froide/chaleur.
PCT/JP2020/027549 2020-07-15 2020-07-15 Dispositif à cycle frigorifique WO2022013981A1 (fr)

Priority Applications (2)

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JP2022536048A JP7466645B2 (ja) 2020-07-15 2020-07-15 冷凍サイクル装置
PCT/JP2020/027549 WO2022013981A1 (fr) 2020-07-15 2020-07-15 Dispositif à cycle frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/027549 WO2022013981A1 (fr) 2020-07-15 2020-07-15 Dispositif à cycle frigorifique

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WO2022013981A1 true WO2022013981A1 (fr) 2022-01-20

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WO (1) WO2022013981A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08271062A (ja) * 1995-03-31 1996-10-18 Sanyo Electric Co Ltd 冷凍装置
JP2001091064A (ja) * 1999-09-20 2001-04-06 Mitsubishi Electric Corp 冷凍装置
JP2007085705A (ja) * 2005-09-26 2007-04-05 Sanyo Electric Co Ltd 冷凍装置
WO2014203354A1 (fr) * 2013-06-19 2014-12-24 三菱電機株式会社 Dispositif à cycle de réfrigération

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08271062A (ja) * 1995-03-31 1996-10-18 Sanyo Electric Co Ltd 冷凍装置
JP2001091064A (ja) * 1999-09-20 2001-04-06 Mitsubishi Electric Corp 冷凍装置
JP2007085705A (ja) * 2005-09-26 2007-04-05 Sanyo Electric Co Ltd 冷凍装置
WO2014203354A1 (fr) * 2013-06-19 2014-12-24 三菱電機株式会社 Dispositif à cycle de réfrigération

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JP7466645B2 (ja) 2024-04-12

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