WO2024009351A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2024009351A1
WO2024009351A1 PCT/JP2022/026588 JP2022026588W WO2024009351A1 WO 2024009351 A1 WO2024009351 A1 WO 2024009351A1 JP 2022026588 W JP2022026588 W JP 2022026588W WO 2024009351 A1 WO2024009351 A1 WO 2024009351A1
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Prior art keywords
degree
refrigerant
expansion valve
superheat
compressor
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PCT/JP2022/026588
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English (en)
Japanese (ja)
Inventor
健太 村田
謙作 畑中
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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 PCT/JP2022/026588 priority Critical patent/WO2024009351A1/fr
Publication of WO2024009351A1 publication Critical patent/WO2024009351A1/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

  • the present disclosure relates to a refrigeration cycle device.
  • Patent Document 1 discloses an example of an air conditioner that performs such injection.
  • an object of the present disclosure is to provide a refrigeration cycle device that can suppress an increase in discharge temperature and suppress a decrease in compressor efficiency.
  • the present disclosure relates to a refrigeration cycle device.
  • the refrigeration cycle device includes a refrigerant circuit and an injection flow path.
  • the refrigerant circuit includes a compressor having a suction port and a discharge port, a condenser, a first expansion valve, a receiver, a second expansion valve, and an evaporator.
  • the refrigerant circuit is configured such that refrigerant circulates in the order of the discharge port of the compressor, the condenser, the first expansion valve, the receiver, the second expansion valve, the evaporator, and the suction port of the compressor.
  • the compressor further has an injection port.
  • the injection flow path includes a third expansion valve, and is configured to send the refrigerant whose pressure has been reduced by the first expansion valve to the injection port via the third expansion valve.
  • the refrigeration cycle device further includes a control device configured to control the second expansion valve so that the dryness of the refrigerant at the suction port is less than 1.
  • the refrigeration cycle device of the present disclosure it is possible to suppress a decrease in compressor efficiency while suppressing an increase in discharge temperature.
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle device 1 according to a first embodiment.
  • 2 is a schematic diagram showing a cross section of a scroll portion of the compressor 10.
  • FIG. FIG. 2 is a schematic diagram showing a vertical cross section of a scroll portion of the compressor 10.
  • FIG. 2 is a PV diagram showing a variation in the amount of work of the compressor depending on the amount of intermediate pressure refrigerant injected.
  • 7 is a flowchart for explaining control of the first expansion valve LEV1 in the first embodiment.
  • 7 is a flowchart for explaining control of the second expansion valve LEV2 in the first embodiment.
  • 7 is a flowchart for explaining control of the third expansion valve LEV3 in the first embodiment.
  • It is a figure showing the composition of refrigeration cycle device 201 of Embodiment 2.
  • FIG. 2 is a ph diagram of the refrigeration cycle device 201.
  • FIG. 5 is a diagram showing the temperature distribution inside the heat exchanger 50.
  • FIG. 7 is a flowchart for explaining control of the first expansion valve LEV1 in Embodiment 2.
  • FIG. 7 is a flowchart for explaining control of the second expansion valve LEV2 in Embodiment 2.
  • FIG. 7 is a flowchart for explaining control of the third expansion valve LEV3 in the second embodiment. It is a figure showing the composition of refrigeration cycle device 211 of Embodiment 3.
  • 3 is a ph diagram of the refrigeration cycle device 211.
  • FIG. 1 is a diagram showing the configuration of a refrigeration cycle device 1 according to the first embodiment.
  • the refrigeration cycle device 1 includes a refrigerant circuit C1 and an injection flow path F1.
  • the refrigeration cycle device 1 is used, for example, in an air conditioner.
  • the refrigerant circuit C1 includes a compressor 10, a condenser 20, a first expansion valve LEV1, a receiver 30, a second expansion valve LEV2, and an evaporator 40.
  • the refrigerant circuit C1 is configured such that refrigerant circulates in the order of the discharge port PD of the compressor 10, the condenser 20, the first expansion valve LEV1, the receiver 30, the second expansion valve LEV2, the evaporator 40, and the suction port PS of the compressor 10. It is composed of
  • the receiver 30 is an example of a liquid receiver that stores refrigerant.
  • the compressor 10 further includes an injection port PM.
  • the injection flow path F1 includes a third expansion valve LEV3, and is configured to send the refrigerant depressurized by the first expansion valve LEV1 to the injection port PM via the third expansion valve LEV3.
  • the third expansion valve LEV3 may be a flow rate adjustment valve or the like as long as the opening degree can be changed.
  • the refrigeration cycle device 1 further includes a control device 100.
  • the control device 100 includes a CPU (Central Processing Unit) 101, a memory 102 (ROM (Read Only Memory) and RAM (Random Access Memory)), an input/output buffer (not shown), and the like.
  • the CPU 101 expands a program stored in the ROM into a RAM or the like and executes the program.
  • the program stored in the ROM is a program in which the processing procedure of the control device 100 is written.
  • Control device 100 executes control of each element in refrigeration cycle device 1 according to these programs. This control is not limited to processing by software, but can also be performed by dedicated hardware (electronic circuit).
  • the compressor 10 is controlled by an inverter and its operating frequency can be changed.
  • the control device 100 controls the operating frequency of the compressor 10 so that the compressor 10 is controlled in units so that the indoor temperature obtained by a temperature sensor (not shown) becomes a desired temperature (for example, the temperature set by the user). Controls the amount of refrigerant discharged per hour.
  • the control device 100 is configured to control the amount of air per unit time of the fan 22 that blows air to the condenser 20 and the fan 42 that blows air to the evaporator 40.
  • the control device 100 detects the degree of subcooling SC of the refrigerant at the outlet of the condenser 20 based on the outputs of a temperature sensor, a pressure sensor, etc. (not shown).
  • the control device 100 controls the opening degree of the first expansion valve LEV1 so that the degree of subcooling SC of the refrigerant at the outlet of the condenser 20 approaches a target value.
  • the control device 100 By opening the third expansion valve LEV3, the control device 100 injects the low-temperature refrigerant stored in the receiver 30 into the compressor 10, thereby cooling the compressor 10. Thereby, the discharge temperature Td of the compressor 10 can be lowered.
  • the control device 100 acquires the discharge temperature Td of the refrigerant discharged from the compressor 10 from a discharge temperature sensor (not shown).
  • the control device 100 detects the degree of superheating SH of the refrigerant discharged from the compressor 10 based on the outputs of a temperature sensor, a pressure sensor, etc. (not shown).
  • the control device 100 is configured to control the opening degree of the third expansion valve LEV3 so that the degree of superheating SH of the refrigerant discharged from the compressor 10 approaches a target value.
  • the discharge temperature Td is determined by the injection flow rate, so the following control method is adopted as the control method for the second expansion valve LEV2.
  • the refrigeration cycle device 1 further includes a capacitive sensor 111 that detects the dryness of the refrigerant in the suction port PS.
  • the control device 100 is configured to control the second expansion valve LEV2 so that the degree of dryness of the refrigerant in the suction port PS is less than 1.
  • the capacitive sensor 111 is configured to sense the degree of dryness (void ratio of the refrigerant).
  • the sensor 111 is a dryness sensor that uses the fact that the capacitance changes when the dielectric constant between the electrodes of a flat capacitor filled with refrigerant changes with the content of air bubbles in the refrigerant (void ratio). It is a sensor.
  • the control device 100 controls the opening degree of the second expansion valve LEV2 so that the degree of dryness of the refrigerant detected by the sensor 111 becomes a predetermined value of 1 or less.
  • the control device 100 is configured to control the second expansion valve LEV2 so that the output of the sensor 111 approaches the target value.
  • the compressor 10 is configured so that intermediate pressure refrigerant is injected during compression. In other words, it is not a two-stage compressor with two stages of compression sections.
  • the structure of the compressor 10 will be explained below.
  • Compressor 10 is a scroll compressor.
  • FIG. 2 is a schematic diagram showing a cross section of the scroll portion of the compressor 10.
  • FIG. 3 is a schematic diagram showing a longitudinal section of the scroll portion of the compressor 10.
  • the scroll roll section includes a fixed scroll 12 fixed to the lid 15 of the compressor 10, and an orbiting scroll 11 fixed to a pedestal 14 that is arranged so as to partially contact the fixed scroll 12 and rotates by a motor or the like.
  • the compressor 10 is provided with an injection port PM.
  • a check valve 18 is arranged at the injection port PM. Refrigerant is injected from the injection port PM into the crescent-shaped gap during compression. When the refrigerant pressure inside the receiver 30 is higher than the pressure in the crescent-shaped gap during compression, the refrigerant passes through the check valve 18 and flows into the compressor 10 .
  • FIG. 4 is a PV diagram showing variations in the amount of work of the compressor depending on the amount of intermediate pressure refrigerant injected.
  • Waveform W1 shows a case where the amount of injected refrigerant is large
  • waveform W2 shows a case where the amount of injected refrigerant is less by ⁇ INJ. Since the area surrounded by the waveform W2 on the PV diagram is smaller, it can be said that the waveform W2 is energy saving.
  • the first expansion valve LEV1 controls the degree of subcooling SC of the refrigerant at the outlet of the condenser to a target value
  • the second expansion valve LEV2 controls the subcooling degree SC of the refrigerant at the outlet of the condenser to a target value.
  • the discharge temperature Td of No. 10 is controlled to be the target value.
  • the third expansion valve LEV3 is controlled so that the discharge temperature Td of the compressor 10 is set to the target value.
  • the second expansion valve LEV2 is also controlled to bring the discharge temperature Td to the target value, the control will conflict and will not work.
  • the second expansion valve LEV2 controls the superheat degree SH of the suction refrigerant of the compressor 10 to the target value, in order to ensure the superheat degree SH of 0 or more (approximately 3 to 5 K in an actual unit).
  • the opening degree of the second expansion valve LEV2 is controlled to be smaller. If the heating capacity is not changed at this time, the injection flow rate will increase in order to keep the same amount of refrigerant flowing into the condenser.
  • the injection method is port injection and the injection flow rate increases, compressor efficiency deteriorates due to the following factors.
  • the refrigerant which has reached an intermediate pressure in the first stage compression, joins the injection refrigerant and is then compressed in the second stage compressor.
  • the compressor 10 shown in FIGS. 2 and 3 the refrigerant injected from the injection port PM and the refrigerant in the compression chamber mix, and the pressure in the compression chamber increases, resulting in two-stage compression.
  • the compression power corresponding to the first stage increases. In other words, compressor efficiency deteriorates.
  • the capacity is determined by the flow rate of refrigerant passing through the condenser, so if the amount of refrigerant is throttled with the second expansion valve LEV2, the lack of capacity must be made up from the third expansion valve LEV3. No. In that case, as shown by the waveform W1 in FIG. 4, the input to the compressor 10 increases, and energy saving is no longer achieved.
  • a check valve 18 is installed within the compressor to prevent backflow when the pressure inside the compression chamber exceeds the injection pressure.
  • the volume between the check valve 18 and the injection port PM becomes a dead volume in which refrigerant that is not discharged is compressed. If the diameter of the flow path in which the check valve 18 is provided is increased in order to increase the injection flow rate, the dead volume will increase, so the loss of compressing the dead volume will increase.
  • the problem with compressors that inject refrigerant through the injection port is that compressor efficiency deteriorates and power consumption increases due to an increase in the injection flow rate.
  • the control device 100 shown in FIG. 1 controls the opening degree of the first expansion valve LEV1 so that the degree of subcooling SC of the refrigerant at the outlet of the condenser 20 approaches the target degree of supercooling SC*, and the The opening degree of the third expansion valve LEV3 is controlled so that the degree of superheat SH2 of the refrigerant to be heated approaches the target degree of superheat SH2*.
  • FIG. 5 is a flowchart for explaining control of the first expansion valve LEV1 in the first embodiment.
  • the control device 100 detects the degree of subcooling SC of the refrigerant at the outlet of the condenser 20.
  • the degree of supercooling SC can be detected by various known methods. For example, the saturation temperature corresponding to the high pressure detected by the pressure sensor provided between the discharge side of the compressor 10 and the first expansion valve LEV1 and the detection temperature of the temperature sensor that detects the temperature of the refrigerant at the outlet of the condenser 20.
  • the degree of supercooling SC may be determined by the difference between the two. Note that the saturation temperature may be detected by a temperature sensor provided in the two-phase region of the condenser 20.
  • step S12 the current degree of supercooling SC and the target degree of supercooling SC* are compared. If SC>SC* holds true (YES in S12), the control device 100 increases the opening degree of the first expansion valve LEV1 by a certain degree in step S13. On the other hand, if SC>SC* does not hold (NO in S12), the control device 100 decreases the opening degree of the first expansion valve LEV1 by a certain degree in step S14.
  • the degree of supercooling SC at the outlet of the condenser 20 is maintained near the target value SC*.
  • FIG. 6 is a flowchart for explaining control of the second expansion valve LEV2 in the first embodiment.
  • the control device 100 detects the degree of dryness D of the refrigerant sucked into the compressor 10.
  • the capacitive sensor 111 shown in FIG. 1 can detect the degree of dryness D by capturing a change in the void ratio of the refrigerant as a change in capacitance.
  • step S22 the current degree of dryness D and the target degree of dryness D* are compared.
  • the target dryness is set to a value that does not damage the compressor 10 due to liquid compression, that is, a value slightly smaller than 1. Thereby, an increase in the injection flow rate can be suppressed.
  • control device 100 decreases the opening degree of the second expansion valve LEV2 by a certain degree in step S23. On the other hand, if D>D* does not hold (NO in S22), the control device 100 increases the opening degree of the second expansion valve LEV2 by a certain degree in step S24.
  • the dryness D of the refrigerant sucked into the compressor 10 is maintained near the target value D*.
  • FIG. 7 is a flowchart for explaining control of the third expansion valve LEV3 in the first embodiment.
  • the control device 100 detects the degree of superheat SH2 of the refrigerant discharged from the compressor 10.
  • the degree of superheating SH2 is calculated from the difference between the saturation temperature corresponding to the high pressure detected by a pressure sensor provided on the discharge side of the compressor 10 and the temperature detected by a temperature sensor that detects the temperature of the refrigerant discharged from the compressor 10. It's okay.
  • the saturation temperature may be detected by a temperature sensor provided in the two-phase region of the condenser 20.
  • step S32 the current degree of superheat SH2 and the target degree of superheat SH2* are compared. If SH2>SH2* holds true (YES in S32), the control device 100 increases the opening degree of the third expansion valve LEV3 by a constant opening degree in step S33. On the other hand, if SH2>SH2* does not hold (NO in S32), the control device 100 decreases the opening degree of the third expansion valve LEV3 by a certain degree in step S34.
  • the degree of superheating SH2 is maintained near the target value SH2* of the degree of superheating.
  • the injection flow rate can be reduced by controlling the suction dryness D to a target dryness D* smaller than 1 using the second expansion valve LEV2. Therefore, the amount of work required by the compressor to achieve the same capacity (circulation amount) on the condenser side is reduced. In other words, the efficiency of the refrigeration cycle device is improved.
  • FIG. 8 is a diagram showing the configuration of a refrigeration cycle device 201 according to the second embodiment.
  • Embodiment 2 a configuration that is effective when a non-azeotropic mixed refrigerant is employed will be described.
  • the refrigerant flowing through the refrigerant circuit C2 and the injection flow path F1 shown in FIG. 8 is a non-azeotropic mixed refrigerant.
  • the refrigerant circuit C2 includes the discharge port PD of the compressor 10, the condenser 20, the first expansion valve LEV1, the receiver 30, the second expansion valve LEV2, the first flow path of the heat exchanger 50, the evaporator 40, and the heat exchanger 50.
  • the refrigerant is configured to circulate in this order through the second flow path of the compressor 10 and the suction port PS of the compressor 10.
  • the refrigeration cycle device 201 further includes a temperature sensor 112 that measures the saturation temperature of the low-pressure refrigerant flowing through the evaporator 40 and a temperature sensor 113 that measures the refrigerant temperature at the outlet of the evaporator 40.
  • the configuration of other parts of the refrigeration cycle device 201 is the same as that of the refrigeration cycle device 1 shown in FIG. 1, so the description will not be repeated.
  • control device 100 controls the second expansion valve LEV2 so that the degree of superheat SH1 of the refrigerant passing through the evaporator 40 and flowing toward the heat exchanger 50 approaches the target degree of superheat SH1*. configured to do so.
  • the degree of superheat is imparted to the refrigerant anywhere from the outlet of the evaporator 40 to the inlet of the heat exchanger 50. Therefore, the second expansion valve LEV2 can be controlled so that the degree of superheat matches the target value at the location where the degree of superheat is applied.
  • the degree of superheat is given and the degree of dryness of the refrigerant is 1, but since the refrigerant is then cooled by the heat exchanger 50, the degree of dryness of the refrigerant sucked into the compressor 10 increases. degree can be less than 1.
  • FIG. 9 is a ph diagram of the refrigeration cycle device 201.
  • the states of the refrigerant at points A1 to A8 in FIG. 8 are indicated by points A1 to A8 in FIG. 9, respectively.
  • the isotherm line is parallel to the horizontal axis in the two-phase region, but in the case of a non-azeotropic mixed refrigerant, the isotherm line is downward-sloping in the two-phase region.
  • the temperature of the heat exchanger 50 is around temperatures T1 and T2.
  • FIG. 10 is a diagram showing the temperature distribution inside the heat exchanger 50. Since the non-azeotropic refrigerant mixture has a temperature gradient, points A1 and A8 at the evaporator outlet are higher in temperature than points A6 and A7 at the evaporator inlet, respectively.
  • the temperature at point A8 is higher than temperature T2, and points A1, A7, and A6 move away from the isothermal line indicating temperature T2 in the order of temperature T1.
  • This state is as shown in FIG. 10, where the vertical axis is the temperature and the horizontal axis is the position of the flow path of the heat exchanger.
  • the enthalpy decreases from point A8 to point A1, so the refrigerant sucked into the compressor 10 becomes a wet refrigerant with a degree of dryness smaller than 1.
  • the refrigerant sucked into the compressor 10 can be a wet refrigerant.
  • the superheat degree SH1 at the outlet of the evaporator 40 is fed back in the control of the second expansion valve LEV2, a dryness sensor is not required even when the suction dryness is controlled to be wet.
  • FIG. 11 is a flowchart for explaining control of the first expansion valve LEV1 in the second embodiment.
  • the control device 100 detects the degree of subcooling SC of the refrigerant at the outlet of the condenser 20.
  • the degree of supercooling SC can be detected by various known methods. For example, the saturation temperature corresponding to the high pressure detected by the pressure sensor provided between the discharge side of the compressor 10 and the first expansion valve LEV1 and the detection temperature of the temperature sensor that detects the temperature of the refrigerant at the outlet of the condenser 20. You can also find it by the difference between Further, the saturation temperature may be detected by a temperature sensor provided in the two-phase region of the condenser 20.
  • step S112 the current degree of supercooling SC and the target degree of supercooling SC* are compared. If SC>SC* holds true (YES in S112), the control device 100 increases the opening degree of the first expansion valve LEV1 by a constant opening degree in step S113. On the other hand, if SC>SC* does not hold (NO in S112), the control device 100 decreases the opening degree of the first expansion valve LEV1 by a certain degree in step S114.
  • the degree of supercooling SC at the outlet of the condenser 20 is maintained near the target value SC*.
  • FIG. 12 is a flowchart for explaining control of the second expansion valve LEV2 in the second embodiment.
  • the control device 100 detects the degree of superheat SH1 of the refrigerant discharged from the evaporator 40.
  • the degree of superheat SH1 can be determined, for example, by the difference between the saturation temperature corresponding to the low pressure detected by the sensor 112 and the temperature detected by the temperature sensor 113 that detects the temperature of the refrigerant at the outlet of the evaporator 40.
  • step S122 the current degree of superheat SH1 and the target degree of superheat SH1* are compared. If SH1>SH1* holds true (YES in S122), the control device 100 increases the opening degree of the second expansion valve LEV2 by a certain opening degree in step S123. On the other hand, if SH1>SH1* does not hold (NO in S122), the control device 100 decreases the opening degree of the second expansion valve LEV2 by a certain degree in step S124.
  • the degree of superheat SH1 of the refrigerant at the outlet of the evaporator 40 is maintained near the target degree of superheat SH1*.
  • FIG. 13 is a flowchart for explaining control of the third expansion valve LEV3 in the second embodiment.
  • the control device 100 detects the degree of superheat SH2 of the refrigerant discharged from the compressor 10.
  • the degree of superheating SH2 is calculated from the difference between the saturation temperature corresponding to the high pressure detected by a pressure sensor provided on the discharge side of the compressor 10 and the temperature detected by a temperature sensor that detects the temperature of the refrigerant discharged from the compressor 10. It's okay.
  • the saturation temperature may be detected by a temperature sensor provided in the two-phase region of the condenser 20.
  • step S132 the current degree of superheat SH2 and the target degree of superheat SH2* are compared. If SH2>SH2* holds true (YES in S132), the control device 100 increases the opening degree of the third expansion valve LEV3 by a constant opening degree in step S133. On the other hand, if SH2>SH2* does not hold (NO in S132), the control device 100 decreases the opening degree of the third expansion valve LEV3 by a certain degree in step S134.
  • the degree of superheat SH2 is maintained near the target degree of superheat SH2*.
  • the heat exchanger 50 can reduce the enthalpy of the suction refrigerant.
  • the opening degree of the second expansion valve LEV2 is controlled so that the degree of superheating of the refrigerant at the outlet of the evaporator 40 reaches the target value, the degree of dryness of the sucked refrigerant cannot be made smaller than 1 by the heat exchanger 50. It becomes possible.
  • FIG. 14 is a diagram showing the configuration of a refrigeration cycle device 211 according to the third embodiment.
  • the refrigerant piping was provided so as not to pass through the inside of the receiver 30, but the refrigerant piping may be made to pass inside the receiver 30 for heat exchange.
  • the refrigerant flowing through the refrigerant circuit C3 and the injection flow path F1 shown in FIG. 14 is a non-azeotropic mixed refrigerant.
  • It further includes a heat exchanger 50 that exchanges heat with the refrigerant, and includes a receiver 30A instead of the receiver 30.
  • the receiver 30A is configured such that the refrigerant passing through the evaporator 40 and heading toward the heat exchanger 50 and the refrigerant stored in the receiver 30A exchange heat.
  • the refrigerant circuit C3 includes the discharge port PD of the compressor 10, the condenser 20, the first expansion valve LEV1, the reservoir of the receiver 30A, the second expansion valve LEV2, the first flow path of the heat exchanger 50, the evaporator 40, and the receiver.
  • the refrigerant is configured to circulate in the order of the heat exchange channel 30A, the second channel of the heat exchanger 50, and the suction port PS of the compressor 10.
  • the control device 100 shown in FIG. 14 is configured to control the second expansion valve LEV2 so that the degree of superheat of the refrigerant passing through the evaporator 40 and the receiver 30A and flowing toward the heat exchanger 50 approaches a target value. be done.
  • the same control as in FIGS. 11, 12, and 13 is performed in the third embodiment as well.
  • FIG. 15 is a ph diagram of the refrigeration cycle device 211.
  • point A8 is in the gas phase region, but in FIG. 15, it can be seen that point A8 is in the two-phase region.
  • the refrigerant near the exit of the evaporator 40 is a gas refrigerant, but in the third embodiment, the refrigerant up to the exit of the evaporator 40 is a two-phase refrigerant. Since the evaporator generally has better heat exchange performance in the two-phase region than in the gas region, the third embodiment can improve the performance of the evaporator 40 more than the second embodiment.
  • point A8 at the outlet of the evaporator 40 is wet refrigerant, but by exchanging heat with the intermediate pressure refrigerant by the receiver 30A, the refrigerant is heated and given a degree of superheat as shown at point A9. Therefore, the degree of superheat SH1 of the refrigerant at point A9 can be controlled to a target value.
  • the degree of superheat is imparted somewhere from the outlet of the evaporator 40 to the low-pressure side inlet of the heat exchanger 50, and the heat exchanger 50 causes the refrigerant sucked into the compressor 10 to become wet refrigerant.
  • Any refrigerant circuit may be used.
  • the inlet temperature of the evaporator 40 becomes lower than the outlet temperature of the evaporator 40 due to the temperature gradient. Therefore, the enthalpy of the refrigerant sucked into the compressor 10 can be reduced by the heat exchanger 50.
  • the gas phase in the evaporator 40 can be reduced.
  • the performance of the evaporator 40 can be improved.
  • the present disclosure relates to a refrigeration cycle device 1.
  • the refrigeration cycle device 1 shown in FIG. 1 includes a refrigerant circuit C1, an injection flow path F1, and a control device 100.
  • Refrigerant circuit C1 includes a compressor 10 having a suction port PS and a discharge port PD, a condenser 20, a first expansion valve LEV1, a receiver 30, a second expansion valve LEV2, and an evaporator 40.
  • the refrigerant circuit C1 is configured such that refrigerant circulates in the order of the discharge port PD of the compressor 10, the condenser 20, the first expansion valve LEV1, the receiver 30, the second expansion valve LEV2, the evaporator 40, and the suction port PS of the compressor 10.
  • Compressor 10 further includes an injection port PM.
  • the injection flow path F1 includes a third expansion valve LEV3, and is configured to send the refrigerant depressurized by the first expansion valve LEV1 to the injection port PM via the third expansion valve LEV3.
  • the control device 100 is configured to control the second expansion valve LEV2 so that the degree of dryness of the refrigerant in the suction port PS is less than 1.
  • the refrigeration cycle device 1 further includes a capacitive sensor 111 that detects the dryness of the refrigerant in the suction port PS.
  • the control device 100 is configured to control the second expansion valve LEV2 so that the degree of dryness D indicated by the output of the sensor 111 approaches the target degree of dryness D*.
  • the refrigerant flowing through the refrigerant circuits C2 and C3 and the injection flow path F1 shown in FIGS. 8 and 14 is a non-azeotropic mixed refrigerant.
  • the refrigeration cycle devices 201 and 211 include a heat exchanger 50 that exchanges heat between the refrigerant that passes through the second expansion valve LEV2 and goes to the evaporator 40, and the refrigerant that passes through the evaporator 40 and goes to the suction port PS of the compressor 10. Be prepared for more.
  • control device 100 shown in FIGS. 8 and 14 sets the degree of superheat SH1 of the refrigerant passing through the evaporator 40 and flowing toward the heat exchanger 50 as a first target.
  • the second expansion valve LEV2 is configured to be controlled so as to approach the degree of superheat SH1*.
  • the refrigerant flowing through the refrigerant circuit C3 and the injection flow path F1 shown in FIG. 14 is a non-azeotropic mixed refrigerant.
  • the refrigeration cycle device 211 further includes a heat exchanger 50 that exchanges heat between the refrigerant that passes through the second expansion valve LEV2 and heads toward the evaporator 40 and the refrigerant that passes through the evaporator 40 and heads toward the suction port PS of the compressor 10.
  • the receiver 30A is configured such that the refrigerant passing through the evaporator 40 and heading toward the heat exchanger 50 exchanges heat with the refrigerant stored in the receiver 30A.
  • the second expansion valve LEV2 is configured to be controlled so as to approach the degree of superheat SH1*.
  • the control device 100 controls the degree of superheat SH1 of the refrigerant passing through the evaporator 40 and the receiver 30A and flowing toward the heat exchanger 50, as shown in FIG.
  • the degree of superheat is larger than the first target degree of superheat SH1*
  • the opening degree of the second expansion valve LEV2 is increased, and the degree of superheat SH1 of the refrigerant flowing toward the heat exchanger 50 is smaller than the first target degree of superheat SH1*. In this case, the opening degree of the second expansion valve LEV2 is reduced.
  • the control device 100 shown in FIGS. 1, 8, and 14 controls the degree of subcooling of the refrigerant at the outlet of the condenser 20.
  • the opening degree of the first expansion valve LEV1 is controlled so as to approach the target supercooling degree
  • the opening degree of the third expansion valve LEV3 is controlled so that the degree of superheating of the refrigerant discharged by the compressor 10 approaches the second target superheating degree. configured to control.
  • the opening degree of the first expansion valve LEV1 is increased. configured to reduce the degree of As shown in FIG. 7 or 13, when the degree of superheat SH2 of the refrigerant discharged by the compressor 10 is larger than the second target degree of superheat SH2*, the control device 100 controls the opening degree of the third expansion valve LEV3.
  • the opening degree of the third expansion valve LEV3 is decreased.
  • Refrigeration cycle device 10 Compressor, 11 Orbiting scroll, 12 Fixed scroll, 14 Pedestal, 15 Lid, 18 Check valve, 20 Condenser, 22, 42 Fan, 30, 30A receiver, 40 Evaporator, 50 Heat exchanger, 100 Control device, 101 CPU, 102 Memory, 112, 113 Temperature sensor, C1, C2, C3 Refrigerant circuit, F1 Injection flow path, LEV1 First expansion valve, LEV2 Second expansion valve, LEV3 Third expansion Valve, PD discharge port, PM injection port, PS suction port.

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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)

Abstract

Un dispositif à cycle frigorifique (1) comprend un circuit de fluide frigorigène (C1) et un chemin d'écoulement d'injection (F1). Le circuit de fluide frigorigène (C1) est conçu de telle sorte qu'un fluide frigorigène circule, dans l'ordre, à travers un orifice de décharge (PD) d'un compresseur (10), un condenseur (20), un premier détendeur (LEV1), un récepteur (30), un deuxième détendeur (LEV2), un évaporateur (40) et un orifice d'aspiration (PS) du compresseur (10). Le chemin d'écoulement d'injection (F1) est conçu de façon à fournir, par l'intermédiaire d'un troisième détendeur (LEV3), le fluide frigorigène dépressurisé par le premier détendeur (LEV1) vers un orifice d'injection (PM). Le dispositif à cycle frigorifique (1) comprend en outre un dispositif de commande (100) qui est configuré pour commander le deuxième détendeur (LEV2) de telle sorte que la siccité du fluide frigorigène au niveau de l'orifice d'aspiration (PS) est inférieure à un.
PCT/JP2022/026588 2022-07-04 2022-07-04 Dispositif à cycle frigorifique WO2024009351A1 (fr)

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0210061A (ja) * 1988-06-29 1990-01-12 Hitachi Ltd 空気調和機
JPH0495277U (fr) * 1991-01-08 1992-08-18
JPH10325622A (ja) * 1997-03-26 1998-12-08 Mitsubishi Electric Corp 冷凍サイクル装置
JP2002081767A (ja) * 2000-09-07 2002-03-22 Hitachi Ltd 空気調和装置
JP2012026610A (ja) * 2010-07-21 2012-02-09 Mitsubishi Electric Corp 冷媒回路システム
WO2013179803A1 (fr) * 2012-05-28 2013-12-05 ダイキン工業株式会社 Dispositif de réfrigération
JP2014167381A (ja) * 2013-01-29 2014-09-11 Daikin Ind Ltd 空気調和装置
JP2016196975A (ja) * 2015-04-03 2016-11-24 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 冷凍サイクル装置及び膨張弁
JP2021156563A (ja) * 2020-03-27 2021-10-07 株式会社富士通ゼネラル 空気調和装置

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0210061A (ja) * 1988-06-29 1990-01-12 Hitachi Ltd 空気調和機
JPH0495277U (fr) * 1991-01-08 1992-08-18
JPH10325622A (ja) * 1997-03-26 1998-12-08 Mitsubishi Electric Corp 冷凍サイクル装置
JP2002081767A (ja) * 2000-09-07 2002-03-22 Hitachi Ltd 空気調和装置
JP2012026610A (ja) * 2010-07-21 2012-02-09 Mitsubishi Electric Corp 冷媒回路システム
WO2013179803A1 (fr) * 2012-05-28 2013-12-05 ダイキン工業株式会社 Dispositif de réfrigération
JP2014167381A (ja) * 2013-01-29 2014-09-11 Daikin Ind Ltd 空気調和装置
JP2016196975A (ja) * 2015-04-03 2016-11-24 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 冷凍サイクル装置及び膨張弁
JP2021156563A (ja) * 2020-03-27 2021-10-07 株式会社富士通ゼネラル 空気調和装置

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