WO2021024443A1 - 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
WO2021024443A1
WO2021024443A1 PCT/JP2019/031273 JP2019031273W WO2021024443A1 WO 2021024443 A1 WO2021024443 A1 WO 2021024443A1 JP 2019031273 W JP2019031273 W JP 2019031273W WO 2021024443 A1 WO2021024443 A1 WO 2021024443A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
compressor
control device
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/031273
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
健太 村田
拓未 西山
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2019/031273 priority Critical patent/WO2021024443A1/ja
Priority to EP19940618.2A priority patent/EP4012293B1/en
Priority to JP2021538641A priority patent/JP7361777B2/ja
Publication of WO2021024443A1 publication Critical patent/WO2021024443A1/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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for the condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2600/00—Control issues
    • F25B2600/01—Timing
    • 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
    • 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
    • F25B2600/2519—On-off valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator

Definitions

  • the present invention relates to a refrigeration cycle device.
  • Patent Document 1 discloses a heat pump system in which an HFO (Hydro Fluoro Olefin) refrigerant is filled and a control valve is connected between the discharge port and the suction port of the compressor. Has been done.
  • HFO Hydro Fluoro Olefin
  • the pressure may drop sharply when the compressor starts. Therefore, depending on the refrigerant, the pressure of the refrigerant sucked into the compressor is smaller than the atmospheric pressure (negative pressure) while determining whether the pressure of the refrigerant sucked into the compressor is equal to or lower than the set pressure. ).
  • a refrigerant other than the HFO refrigerant is not considered.
  • the present invention has been made to solve the above-mentioned problems, and an object of the present invention is to reduce the pressure of the refrigerant sucked into the compressor at the start of operation of the refrigeration cycle apparatus regardless of the type of the refrigerant. It is to suppress.
  • the refrigerant circulates.
  • the refrigeration cycle device includes a compressor, a first heat exchanger, a second heat exchanger, an expansion valve, a flow rate adjusting unit, and a control device.
  • the flow rate adjusting unit adjusts the amount of refrigerant passing through at least one of the first heat exchanger and the expansion valve per unit time.
  • the control device switches the operation mode of the refrigeration cycle device.
  • the operation mode includes a start mode and a normal mode.
  • the boot mode is executed when the compressor is booted. Normal mode is executed after boot mode.
  • the refrigerant circulates in the first circulation direction of the compressor, the first heat exchanger, the expansion valve, and the second heat exchanger.
  • the control device controls the compressor and the flow rate adjusting unit to reduce the amount of refrigerant passing through at least one of the first heat exchanger and the expansion valve in the start mode than the amount of the refrigerant in the normal mode. ..
  • the amount of refrigerant passing through at least one of the first heat exchanger and the expansion valve per unit time in the start-up mode is smaller than the amount of the refrigerant in the normal mode, regardless of the type of refrigerant. , Suppress the pressure drop of the refrigerant sucked into the compressor at the start of operation of the refrigeration cycle device.
  • FIG. 6 It is a flowchart which shows the flow of the operation mode switching process performed by the control device of FIG. 1 and FIG. 6 is a flowchart showing another example of the operation mode switching process performed by the control devices of FIGS. 1 and 5.
  • It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on the modification of Embodiment 1, and the flow of a refrigerant in a start mode.
  • It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on Embodiment 2 and the flow of a refrigerant in a normal mode.
  • Embodiment 2 It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on Embodiment 2 and the flow of the refrigerant in the start mode.
  • FIG. 9 is a flowchart showing a flow of operation mode switching processing performed by the control devices of FIGS. 9 and 10. It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on Embodiment 3 and the flow of a refrigerant in a normal mode. It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on Embodiment 3 and the flow of a refrigerant in a start mode. It is a flowchart which shows the flow of the operation mode switching process performed by the control device of FIG. 12 and FIG. It is a functional block diagram which also shows the structure of the refrigerating cycle apparatus which concerns on Embodiment 4, and the flow of a refrigerant in a cooling operation.
  • FIG. 1 is a functional block diagram showing the configuration of the refrigeration cycle device 100 according to the first embodiment and the flow of the refrigerant in the normal mode.
  • the valves that are closed in FIG. 1 are hatched. The same applies to FIGS. 5, 8 to 10, 12, and 13 which will be described later.
  • the refrigeration cycle device 100 includes an outdoor unit 110 and an indoor unit 120.
  • the indoor unit 120 is arranged in the indoor space.
  • the outdoor unit 110 is arranged outside the indoor space (outdoor).
  • a refrigerant containing R290 is sealed in the refrigeration cycle device 100.
  • the indoor unit 120 includes a condenser 2 (first heat exchanger).
  • the outdoor unit 110 includes a compressor 1, an expansion valve 3, an evaporator 4 (second heat exchanger), a gas-liquid separator 5, a flow rate adjusting unit 130, a temperature sensor TS1, and a control device 10.
  • the flow rate adjusting unit 130 has a solenoid valve 6 (first valve) and a solenoid valve 7 (second valve).
  • the control device 10 may be included in the indoor unit 120, or may be provided separately from the outdoor unit 110 and the indoor unit 120.
  • the operation mode of the refrigeration cycle device 100 includes a start mode and a normal mode.
  • the start mode is executed when the compressor 1 is started.
  • Normal mode is executed following boot mode.
  • the normal mode may be executed after the start mode, and other operation modes may be executed between the start mode and the normal mode.
  • the refrigerant circulates in the circulation direction (first circulation direction) of the compressor 1, the condenser 2, the expansion valve 3, and the evaporator 4.
  • the solenoid valve 6 is connected between the discharge port of the compressor 1 and the condenser 2.
  • the solenoid valve 7 is connected between the discharge port of the compressor 1 and the flow path between the expansion valve 3 and the evaporator 4.
  • the gas-liquid separator 5 receives the refrigerant from the evaporator 4, separates the gaseous refrigerant (gas refrigerant) and the liquid refrigerant (liquid refrigerant), stores the liquid refrigerant, and transfers the gas refrigerant to the compressor 1. Guide.
  • the gas-liquid separator 5 prevents the liquid refrigerant from being sucked into the compressor 1.
  • the gas-liquid separator 5 includes an accumulator or a suction muffler.
  • the control device 10 switches the operation mode of the refrigeration cycle device 100.
  • the control device 10 opens the solenoid valve 6 and closes the solenoid valve 7 in the normal mode.
  • the control device 10 acquires the temperature T1 of the refrigerant flowing out of the evaporator 4 from the temperature sensor TS1.
  • Controller 10, the driving frequency F c of the compressor 1, for example, 50Hz By controlling the range of ⁇ 60 Hz, temperature of the indoor space (temperature set by for example a user) target temperature to become like the compressor 1 controls the amount of refrigerant discharged per unit time.
  • the control device 10 has an expansion valve 3 so that the pressure difference between the refrigerant before being discharged from the compressor 1 and being decompressed and the refrigerant before being depressurized and sucked into the compressor 1 is within a desired range. Control the opening.
  • the expansion valve 3 may be controlled so that the degree of superheating and the degree of supercooling of the refrigerant become target values.
  • FIG. 2 is a functional block diagram showing the configuration of the control device 10 of FIG.
  • the control device 10 includes a processing circuit 11, a memory 12, and an input / output unit 13.
  • the processing circuit 11 may be dedicated hardware or a CPU (Central Processing Unit) that executes a program stored in the memory 12.
  • the processing circuit 11 may be, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), or an FPGA (Field). Programmable Gate Array) or a combination of these is applicable.
  • the processing circuit 11 is a CPU, the function of the control device 10 is realized by software, firmware, or a combination of software and firmware.
  • the software or firmware is described as a program and stored in the memory 12.
  • the processing circuit 11 reads and executes the program stored in the memory.
  • the memory 12 includes a non-volatile or volatile semiconductor memory (for example, RAM (Random Access Memory), ROM (Read Only Memory), flash memory, EPROM (Erasable Programmable Read Only Memory), or EEPROM (Electrically Erasable Programmable Read Only Memory). )), Magnetic disc, flexible disc, optical disc, compact disc, mini disc, or DVD (Digital Versatile Disc) is included.
  • the CPU is also called a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, a processor, or a DSP (Digital Signal Processor).
  • the GWP total amount value T gwp is expressed by the following equation (1) using the GWP value R gwp , which is a physical property value peculiar to the refrigerant, and the refrigerant amount M chg sealed in the refrigeration cycle apparatus 100.
  • the total amount of GWP T gwp can be reduced by reducing the amount of refrigerant M chg sealed in the refrigeration cycle apparatus.
  • the refrigerant include low-pressure refrigerants having a low operating pressure.
  • the low pressure refrigerant includes, for example, R290 (propane) or R454a.
  • the heating capacity of the refrigeration cycle apparatus is as shown in the following equation (2) by using the refrigerant circulation amount Gr discharged by the compressor 1 per unit time and the enthalpy difference ⁇ h representing the change in the latent heat of the refrigerant in the condensation process. expressed.
  • the refrigerant circulation amount Gr is the stroke volume V st which is the amount of refrigerant discharged per rotation by the compression mechanism of the compressor 1, the density of the refrigerant sucked into the compressor 1 is ⁇ s , and the drive frequency F of the compressor 1. It is expressed by the following equation (3) using c .
  • the enthalpy difference ⁇ h of the formula (2) is different for each refrigerant. Therefore, in order to change the refrigerant to a low-pressure refrigerant and maintain the heating capacity of the refrigeration cycle apparatus, it is necessary to change the refrigerant circulation amount Gr.
  • the density ⁇ s of the refrigerant is a physical property value peculiar to the refrigerant.
  • FIG. 3 is a functional block diagram showing the configuration of the refrigeration cycle device 900 according to the comparative example.
  • the structure of the refrigeration cycle device 900 is such that the solenoid valves 6 and 7 are removed from the refrigeration cycle device 100 of FIG. 1 and the control device 10 is replaced with 90.
  • the problem that occurs when the refrigerant circulating in the refrigeration cycle device 900 is changed from R32 to R290 while maintaining the heating capacity of the refrigeration cycle device 900 will be described.
  • Table 1 below shows that when the refrigerant circulating in the refrigeration cycle apparatus 900 of FIG. 3 is changed from R32 to R290, it is necessary to maintain the heating capacity with respect to each value of the refrigerant amount, the refrigerant circulation amount, and the stroke volume. , The simulation result of the ratio of the value when R290 is used to the value when R32 is used is shown.
  • R32 is an example of a refrigerant conventionally used in a refrigeration cycle device.
  • the amount of refrigerant of R290 is 52% of the amount of refrigerant of R32.
  • the refrigerant circulation amount of R290 needs to be 88% of the refrigerant circulation amount of R32.
  • the stroke volume when R290 is used needs to be 210% of the stroke volume when R32 is used.
  • the amount of refrigerant distributed in the evaporator 4 may sharply decrease when the compressor 1 is started. It takes a certain amount of time for the refrigerant discharged from the compressor 1 to reach the evaporator 4 via the condenser 2 and the expansion valve 3. Therefore, when the compressor 1 is started, there may be a time zone in which the pressure of the refrigerant flowing between the evaporator 4 and the compressor 1 sharply decreases.
  • FIG. 4 is a graph showing the relationship between the elapsed time since the compressor 1 of FIG. 3 was started and the saturation temperature of the refrigerant sucked into the compressor 1.
  • graphs C10 and C11 are graphs when R32 and R290 are used as the refrigerants, respectively. The lower the saturation temperature, the smaller the pressure of the refrigerant sucked into the compressor 1.
  • Tm10 when the saturation temperature of graph C10 and the saturation temperature of C11 are compared in the time zone from the start of the compressor 1 to the elapsed time Tm10, the minimum temperature of R290 is higher than the minimum temperature Ts10 of R32. Ts11 is lower.
  • the pressure of R290 sucked into the compressor 1 decreases sharply.
  • the pressure of the refrigerant sucked into the compressor 1 becomes negative when the compressor 1 is started, and the refrigerating cycle device 900 may fail.
  • the operation mode of the refrigeration cycle device 100 when the compressor 1 is started, the operation mode of the refrigeration cycle device 100 is set as the start mode. In the start-up mode, the circulation flow path of the refrigerant is changed so as to suppress the decrease in the amount of the refrigerant distributed in the evaporator 4.
  • the operation mode in the order of the start mode and the normal mode when starting the operation of the refrigeration cycle device 100, the refrigerant sucked into the compressor 1 at the start of the operation of the refrigeration cycle device 100 regardless of the type of the refrigerant. It is possible to suppress the pressure drop of.
  • FIG. 5 is a functional block diagram showing the configuration of the refrigeration cycle device 100 according to the first embodiment and the flow of the refrigerant in the start mode.
  • the control device 10 activates the compressor 1 in the activation mode.
  • the control device 10 closes the solenoid valve 6 in the start mode, opens the solenoid valve 7, and opens the expansion valve 3 fully.
  • the control device 10 forms a circulation flow path so that the refrigerant discharged from the compressor 1 bypasses the condenser 2.
  • the refrigerant discharged from the compressor 1 is guided to the evaporator 4 without going through the condenser 2 by closing the solenoid valve 6 and opening the solenoid valve 7.
  • the control device 10 controls the compressor 1 and the flow rate adjusting unit 130 to reduce the amount of refrigerant passing through the condenser 2 per unit time in the start mode than the amount of the refrigerant in the normal mode.
  • the control device 10 promotes the movement of the refrigerant stored in the condenser 2 to the evaporator 4 by fully opening the expansion valve 3.
  • the distribution of the refrigerant is biased toward the evaporator 4 rather than the condenser 2, so that it is possible to prevent the amount of the refrigerant distributed in the evaporator 4 from being sharply reduced when the compressor 1 is started.
  • FIG. 6 is a flowchart showing the flow of the operation mode switching process performed by the control device 10 of FIGS. 1 and 5.
  • the process shown in FIG. 6 is called at the start of operation of the refrigeration cycle device 100 by the main routine that integrally controls the refrigeration cycle device 100. In the following, the step is simply referred to as S.
  • the control device 10 starts the activation mode from S101.
  • the control device 10 closes the solenoid valve 6 in S101 and proceeds to the process in S102.
  • the control device 10 opens the solenoid valve 7 in S102 and proceeds to the process in S103.
  • the control device 10 fully opens the expansion valve 3 in S103 and advances the process to S104.
  • the control device 10 starts the compressor 1 in S104 and advances the process to S105.
  • the control device 10 determines in S105 whether or not the reference time Tm1 has elapsed from the start of the compressor 1.
  • the reference time Tm1 is appropriately determined by an actual machine experiment or a simulation.
  • the control device 10 waits for a certain period of time in S106 and then returns the process to S105.
  • the control device 10 determines in S107 whether or not the temperature T1 is higher than the reference temperature Trf1.
  • the reference temperature Trf1 is appropriately determined by an actual experiment or a simulation.
  • the control device 10 waits for a certain period of time in S108 and then returns the process to S107.
  • the control device 10 advances the process to S109 and switches the operation mode from the start mode to the normal mode.
  • the start mode ends and the normal mode starts.
  • the control device 10 opens the solenoid valve 6 in S109 and proceeds to the process in S110.
  • the control device 10 closes the solenoid valve 7 in S110 and returns the process to the main routine.
  • the end of the start mode was determined using the temperature T1 after the reference elapsed from the start of the compressor 1.
  • the end of the activation mode may be determined by the elapsed time from the activation of the compressor 1.
  • FIG. 7 is a flowchart showing another example of the operation mode switching process performed by the control device 10 of FIGS. 1 and 5.
  • the process shown in FIG. 7 is a process in which S105 in FIG. 6 is replaced with S115 and S107 and S108 are removed.
  • the control device 10 determines whether or not the reference time Tm11 (> Tm1) has elapsed from the start of the compressor 1 in S115 after performing S101 to S104.
  • the reference time Tm11 is appropriately determined by an actual machine experiment or a simulation.
  • the control device 10 waits for a certain period of time in S106 and then returns the process to S115.
  • the control device 10 performs S109 and S110 and returns the process to the main routine.
  • the start mode ends and the normal mode starts.
  • the configuration in which the refrigerant discharged from the compressor 1 in the start-up mode is guided to the flow path between the expansion valve 3 and the evaporator 4 has been described.
  • the refrigerant discharged from the compressor 1 in the start-up mode is guided to the flow path between the condenser 2 and the expansion valve 3 as in the refrigeration cycle device 100A according to the modification of the first embodiment shown in FIG. You may be asked.
  • the refrigerating cycle apparatus As described above, according to the refrigerating cycle apparatus according to the first embodiment and the modified example, it is possible to suppress the pressure drop of the refrigerant sucked into the compressor at the start of the operation of the refrigerating cycle apparatus regardless of the type of the refrigerant.
  • Embodiment 2 In the first embodiment, a configuration in which a circulation flow path is formed so that the refrigerant discharged from the compressor bypasses the condenser has been described. In the second embodiment, the circulation flow path is formed so that the refrigerant discharged from the compressor bypasses the condenser in the start mode, and the refrigerant flowing out of the evaporator is heated by the refrigerant discharged from the compressor. A configuration in which the density of the refrigerant sucked into the compressor is reduced by the above-described structure will be described.
  • FIG. 9 is a functional block diagram showing the configuration of the refrigeration cycle device 200 according to the second embodiment and the flow of the refrigerant in the normal mode.
  • the refrigeration cycle device 200 includes an outdoor unit 210 and an indoor unit 220.
  • the indoor unit 220 is arranged in the indoor space.
  • the outdoor unit 210 is arranged outdoors.
  • a refrigerant containing R290 is sealed in the refrigeration cycle device 200.
  • the indoor unit 220 includes a condenser 22 (first heat exchanger).
  • the outdoor unit 210 includes a compressor 21, an expansion valve 23, an evaporator 24 (second heat exchanger), a gas-liquid separator 25, a check valve 28, and an internal heat exchanger 29 (third heat exchanger).
  • the device ), the flow rate adjusting unit 230, the temperature sensor TS2, and the control device 20.
  • the flow rate adjusting unit 230 has a solenoid valve 26 (first valve) and a solenoid valve 27 (second valve).
  • the control device 20 may be included in the indoor unit 220, or may be provided separately from the outdoor unit 210 and the indoor unit 220.
  • the operation mode of the refrigeration cycle device 200 includes a start mode and a normal mode.
  • the activation mode is executed when the compressor 21 is activated.
  • Normal mode is executed following boot mode.
  • the refrigerant circulates in the circulation direction (first circulation direction) of the compressor 21, the condenser 22, the expansion valve 23, and the evaporator 24.
  • the gas-liquid separator 25 receives the refrigerant from the evaporator 24, separates the gas refrigerant and the liquid refrigerant, stores the liquid refrigerant, and guides the gas refrigerant to the compressor 21.
  • the gas-liquid separator 25 prevents the liquid refrigerant from being sucked into the compressor 21.
  • the gas-liquid separator 25 includes an accumulator or a suction muffler.
  • a heat exchanger is performed between the refrigerant from the condenser 22 and the refrigerant from the evaporator 24.
  • the check valve 28 is connected between the condenser 22 and the internal heat exchanger 29. The forward direction of the check valve 28 is from the condenser 22 toward the internal heat exchanger 29.
  • the solenoid valve 26 is connected between the discharge port of the compressor 21 and the condenser 22.
  • the solenoid valve 27 is connected between the discharge port of the compressor 21 and the flow path between the check valve 28 and the internal heat exchanger 29.
  • the control device 20 switches the operation mode of the refrigeration cycle device 200.
  • the control device 20 opens the solenoid valve 26 and closes the solenoid valve 27 in the normal mode.
  • the control device 20 acquires the temperature T2 of the refrigerant flowing between the internal heat exchanger 29 and the gas-liquid separator 25 from the temperature sensor TS2.
  • the control device 20 controls the compressor 21 and the expansion valve 23 as in the first embodiment.
  • FIG. 10 is a functional block diagram showing the configuration of the refrigeration cycle device 200 according to the second embodiment and the flow of the refrigerant in the start mode.
  • the control device 20 activates the compressor 21 in the activation mode.
  • the control device 20 closes the solenoid valve 26 in the start mode, opens the solenoid valve 27, and fully opens the expansion valve 23.
  • the control device 20 forms a circulation flow path so that the refrigerant discharged from the compressor 21 bypasses the condenser 22.
  • the refrigerant discharged from the compressor 21 is between the check valve 28 and the internal heat exchanger 29 without the intervention of the condenser 22 by closing the solenoid valve 26 and opening the solenoid valve 27. Guided to the flow path.
  • the check valve 28 prevents the refrigerant from flowing from the flow path to the condenser 22.
  • the refrigerant that has passed through the internal heat exchanger 29 passes through the expansion valve 23 and reaches the evaporator 24.
  • the refrigerant flowing out of the evaporator 24 is heated by the refrigerant discharged from the compressor 21 in the internal heat exchanger 29, and then sucked into the compressor 21.
  • the control device 20 controls the compressor 21 and the flow rate adjusting unit 230 to reduce the amount of refrigerant passing through the condenser 22 per unit time in the start mode than the amount of the refrigerant in the normal mode.
  • the control device 20 promotes the movement of the refrigerant stored in the condenser 22 to the evaporator 24 by fully opening the expansion valve 23. In the start-up mode, the distribution of the refrigerant is biased toward the evaporator 24 rather than the condenser 22, so that it is possible to prevent the amount of the refrigerant distributed in the evaporator 24 from suddenly decreasing when the compressor 21 is started.
  • the refrigerant flowing out of the evaporator 24 is heated by the refrigerant discharged from the compressor 21 in the internal heat exchanger 29, so that the density of the refrigerant sucked into the compressor 21 becomes small. .. Since the amount of the refrigerant sucked into the compressor 21 per unit time decreases, the amount of the refrigerant remaining in the evaporator 24 increases. As a result, it is possible to prevent the refrigerant sucked into the compressor 21 from becoming a negative pressure when the compressor 21 is started.
  • FIG. 11 is a flowchart showing the flow of the operation mode switching process performed by the control device 20 of FIGS. 9 and 10. The process shown in FIG. 11 is called at the start of operation of the refrigeration cycle device 200 by the main routine that integrally controls the refrigeration cycle device 200.
  • the control device 20 starts the activation mode from S201.
  • the control device 20 closes the solenoid valve 26 in S201 and proceeds to the process in S202.
  • the control device 20 opens the solenoid valve 27 in S202 and proceeds to the process in S203.
  • the control device 20 advances the process to S204 with the expansion valve 23 fully opened in S203.
  • the control device 20 activates the compressor 21 in S204 and advances the process to S205.
  • the control device 20 determines in S205 whether or not the reference time Tm2 has elapsed from the start of the compressor 21.
  • the reference time Tm2 is appropriately determined by an actual machine experiment or a simulation.
  • the control device 20 waits for a certain period of time in S206 and then returns the process to S205.
  • the control device 20 determines whether or not the temperature T2 is higher than the reference temperature Trf2 in S207.
  • the reference temperature Trf2 is appropriately determined by an actual experiment or a simulation.
  • the control device 20 waits for a certain period of time in S208 and then returns the process to S207.
  • the control device 20 advances the process to S209 and switches the operation mode from the start mode to the normal mode.
  • the start mode ends and the normal mode starts.
  • the control device 20 opens the solenoid valve 26 in S209 and proceeds to the process in S210.
  • the control device 20 closes the solenoid valve 27 in S210 and returns the process to the main routine.
  • the refrigerating cycle apparatus According to the refrigerating cycle apparatus according to the second embodiment, it is possible to suppress a pressure drop of the refrigerant sucked into the compressor at the start of operation of the refrigerating cycle apparatus regardless of the type of the refrigerant.
  • Embodiment 3 In the first and second embodiments, the configuration in which the circulation flow path is formed so that the refrigerant discharged from the compressor bypasses the condenser has been described. In the third embodiment, a configuration in which a circulation flow path is formed so that the refrigerant discharged from the compressor bypasses a part of the evaporator in the start mode will be described.
  • FIG. 12 is a functional block diagram showing the configuration of the refrigeration cycle device 300 according to the third embodiment and the flow of the refrigerant in the normal mode.
  • the refrigeration cycle device 300 includes an outdoor unit 310 and an indoor unit 320.
  • the indoor unit 320 is arranged in the indoor space.
  • the outdoor unit 310 is arranged outdoors.
  • a refrigerant containing R290 is sealed in the refrigeration cycle device 300.
  • the indoor unit 320 includes a condenser 32 (first heat exchanger).
  • the outdoor unit 310 includes a compressor 31, an expansion valve 33, an evaporator 34 (second heat exchanger), a gas-liquid separator 35, a flow rate adjusting unit 330, a temperature sensor TS3, and a control device 30.
  • the evaporator 34 includes a heat exchange unit 341 (first heat exchange unit) and a heat exchange unit 342 (second heat exchange unit).
  • the flow rate adjusting unit 330 has a solenoid valve 36.
  • the control device 30 may be included in the indoor unit 320, or may be provided separately from the outdoor unit 310 and the indoor unit 320.
  • the operation mode of the refrigeration cycle device 300 includes a start mode and a normal mode.
  • the activation mode is executed when the compressor 31 is activated.
  • Normal mode is executed following boot mode.
  • the refrigerant circulates in the circulation direction (first circulation direction) of the compressor 31, the condenser 32, the expansion valve 33, the heat exchange unit 341, and the heat exchange unit 342.
  • the solenoid valve 36 is connected between the flow path between the condenser 32 and the expansion valve 33 and the flow path between the heat exchange section 341 and the heat exchange section 342.
  • the gas-liquid separator 35 receives the refrigerant from the evaporator 34, separates the gas refrigerant and the liquid refrigerant, stores the liquid refrigerant, and guides the gas refrigerant to the compressor 31.
  • the gas-liquid separator 35 prevents the liquid refrigerant from being sucked into the compressor 31.
  • the gas-liquid separator 35 includes an accumulator or a suction muffler.
  • the control device 30 switches the operation mode of the refrigeration cycle device 300.
  • the control device 30 opens the expansion valve 33 and closes the solenoid valve 36 in the normal mode.
  • the control device 30 acquires the temperature T3 of the refrigerant flowing out of the evaporator 34 from the temperature sensor TS3.
  • the control device 30 controls the compressor 31 and the expansion valve 33 as in the first embodiment.
  • FIG. 13 is a functional block diagram showing the configuration of the refrigeration cycle device 300 according to the third embodiment and the flow of the refrigerant in the start mode.
  • the control device 30 activates the compressor 31 in the activation mode.
  • the control device 30 closes the expansion valve 33 and opens the solenoid valve 36 in the start mode.
  • the control device 30 forms a circulation flow path so that the refrigerant discharged from the compressor 31 bypasses the heat exchange unit 341.
  • the refrigerant discharged from the compressor 31 is guided to the heat exchange section 342 without going through the heat exchange section 341 by closing the expansion valve 33 and opening the solenoid valve 36.
  • the control device 30 controls the compressor 31 and the flow rate adjusting unit 330 to reduce the amount of refrigerant passing through the expansion valve 33 per unit time in the start mode from the amount of the refrigerant in the normal mode.
  • the refrigerant stored in the heat exchange unit 341 moves to the heat exchange unit 342. Since the distribution of the refrigerant is biased toward the heat exchange unit 342 rather than the heat exchange unit 341, it is possible to prevent the amount of refrigerant flowing between the evaporator 34 and the compressor 31 from being sharply reduced when the compressor 31 is started. As a result, it is possible to prevent the refrigerant sucked into the compressor 31 from becoming a negative pressure when the compressor 31 is started.
  • FIG. 14 is a flowchart showing the flow of the operation mode switching process performed by the control device 30 of FIGS. 12 and 13. The process shown in FIG. 14 is called at the start of operation of the refrigeration cycle device 300 by the main routine that integrally controls the refrigeration cycle device 300.
  • control device 30 starts the activation mode from S301.
  • the control device 30 closes the expansion valve 33 in S301 and proceeds to the process in S302.
  • the control device 30 opens the solenoid valve 36 in S302 and proceeds to the process in S304.
  • the control device 30 activates the compressor 31 in S304 and advances the process to S305.
  • the control device 30 determines in S305 whether or not the reference time Tm3 has elapsed from the start of the compressor 31.
  • the reference time Tm3 is appropriately determined by an actual machine experiment or a simulation. If the reference time Tm3 has not elapsed since the compressor 31 was started (NO in S305), the control device 30 waits for a certain period of time in S306 and then returns the process to S305. When the reference time Tm3 has elapsed from the start of the compressor 31 (YES in S305), the control device 30 determines whether or not the temperature T3 is higher than the reference temperature Trf3 in S307. The reference temperature Trf3 is appropriately determined by an actual experiment or a simulation.
  • the control device 30 waits for a certain period of time in S308 and then returns the process to S307.
  • the control device 30 advances the process to S309 and switches the operation mode from the start mode to the normal mode.
  • the condition shown in S307 is satisfied, the start mode ends and the normal mode starts.
  • the control device 30 opens the expansion valve 33 in S309 and advances the process to S310.
  • the control device 30 closes the solenoid valve 36 in S310 and returns the process to the main routine.
  • the refrigerating cycle apparatus According to the refrigerating cycle apparatus according to the third embodiment, it is possible to suppress a pressure drop of the refrigerant sucked into the compressor at the start of operation of the refrigerating cycle apparatus regardless of the type of the refrigerant.
  • Embodiment 4 In the first to third embodiments, the configuration in which the compressor has one suction port has been described. In the fourth embodiment, a configuration in which the compressor has two compression mechanisms and has two suction ports corresponding to each of the compressors will be described.
  • FIG. 15 is a functional block diagram showing the configuration of the refrigeration cycle device 400 according to the fourth embodiment and the flow of the refrigerant in the cooling operation.
  • the refrigeration cycle device 400 includes an outdoor unit 410 and an indoor unit 420.
  • the indoor unit 420 is arranged in the indoor space.
  • the outdoor unit 410 is arranged outdoors.
  • the refrigerating cycle device 400 is filled with a refrigerant containing R290.
  • the indoor unit 420 includes a heat exchanger 42 (first heat exchanger).
  • the outdoor unit 410 includes a compressor 41, an expansion valve 43, a heat exchanger 44 (second heat exchanger), a gas-liquid separator 45, a four-way valve 46, a flow rate adjusting unit 430, and a temperature sensor TS4. , And the control device 40.
  • the flow rate adjusting unit 430 has a three-way valve 47.
  • the control device 40 may be included in the indoor unit 420, or may be provided separately from the outdoor unit 410 and the indoor unit 420.
  • the compressor 41 includes a suction port Ps1 (first suction port), a suction port Ps2 (second suction port), a discharge port Pd, a compression mechanism 411 (first compression mechanism), and a compression mechanism 412 (second compression). Mechanism) and included.
  • the compression mechanism 411 is connected between the suction port Ps1 and the discharge port Pd, compresses the refrigerant from the suction port Ps1, and discharges the refrigerant from the discharge port Pd.
  • the compression mechanism 412 is connected between the suction port Ps2 and the discharge port Pd, compresses the refrigerant from the suction port Ps2, and discharges the refrigerant from the discharge port Pd.
  • the compressor 41 is a twin rotary type compressor.
  • the three-way valve 47 includes port P1 (first port), port P2 (second port), and port P3 (third port).
  • the port P1 is connected to the suction port Ps2.
  • the port P2 communicates with the suction port Ps1 via the gas-liquid separator 45.
  • the port P3 is connected to the discharge port Pd.
  • the three-way valve 47 selectively switches the communication state of ports P1 to P3 between a state in which ports P1 and P2 communicate with each other and a state in which ports P1 and P3 communicate with each other. In FIGS. 15 and 16 and 17, which will be described later, the ports that do not communicate with other ports are hatched.
  • the control device 40 controls the drive frequency of the compression mechanisms 411 and 412, for example, in the range of 50 Hz to 60 Hz, so that the temperature of the indoor space becomes the target temperature (for example, the temperature set by the user). 41 controls the amount of refrigerant discharged per unit time.
  • the control device 40 controls the expansion valve 43 as in the first embodiment.
  • the control device 40 controls the four-way valve 46 to switch the circulation direction of the refrigerant.
  • the control device 40 communicates the discharge port Pd of the compressor 41 with the heat exchanger 44 and the suction ports Ps1 and Ps2 of the compressor 41 with the heat exchanger 42 in the cooling operation.
  • the control device 40 communicates the ports P1 and P2 in the cooling operation.
  • the refrigerant circulates in the circulation direction (second circulation direction) of the compressor 41, the heat exchanger 44, the expansion valve 43, and the heat exchanger 42.
  • the heat exchangers 42 and 44 function as evaporators and condensers, respectively.
  • the gas-liquid separator 45 receives the refrigerant from the heat exchanger 42, separates the gas refrigerant and the liquid refrigerant, stores the liquid refrigerant, and guides the gas refrigerant to the compressor 41.
  • the gas-liquid separator 45 prevents the liquid refrigerant from being sucked into the compressor 41.
  • the gas-liquid separator 45 includes an accumulator or a suction muffler.
  • FIG. 16 is a functional block diagram showing the configuration of the refrigeration cycle device 400 according to the fourth embodiment and the flow of the refrigerant in the normal mode of the heating operation.
  • the refrigeration cycle device 400 includes a start mode and a normal mode as an operation mode of the heating operation.
  • the start mode is executed when the compressor 41 is started.
  • Normal mode is executed following boot mode.
  • the control device 40 communicates the discharge port Pd of the compressor 41 with the heat exchanger 42 and the suction ports Ps1 and Ps2 of the compressor 41 with the heat exchanger 44 in the heating operation. ..
  • the control device 40 communicates the ports P1 and P2 in the normal mode of the heating operation.
  • the control device 40 operates the compression mechanisms 411 and 412 in the normal mode of heating operation.
  • the control device 40 acquires the temperature T4 of the refrigerant flowing out from the heat exchanger 44 in the heating operation from the temperature sensor TS4.
  • the refrigerant circulates in the circulation direction (first circulation direction) of the compressor 41, the heat exchanger 42, the expansion valve 43, and the heat exchanger 44.
  • the heat exchangers 42 and 44 function as condensers and evaporators, respectively.
  • FIG. 17 is a functional block diagram showing the configuration of the refrigeration cycle device 400 according to the fourth embodiment and the flow of the refrigerant in the start mode of the heating operation.
  • the control device 40 communicates the ports P1 and P3 with each other in the activation mode, operates the compression mechanism 411, and does not activate the compression mechanism 412.
  • the stopped compression mechanism 412 is hatched. Since the compression mechanism 412 is stopped in the start mode, the amount of refrigerant sucked into the compressor 41 per unit time is smaller than the amount of the refrigerant sucked into the compressor 41 in the normal mode.
  • the control device 40 controls the compressor 41 and the flow rate adjusting unit 430 to reduce the amount of refrigerant passing through the heat exchanger 42 and the expansion valve 43 per unit time in the start mode from the amount of the refrigerant in the normal mode. ..
  • the amount of refrigerant sucked into the compressor 41 per unit time is smaller than in the normal mode, so that the amount of refrigerant flowing between the heat exchanger 44 and the compressor 41 suddenly increases when the compressor 41 is started up. It is prevented from decreasing. As a result, it is possible to prevent the refrigerant sucked into the compressor 41 from becoming a negative pressure when the compressor 41 is started.
  • FIG. 18 is a flowchart showing the flow of the operation mode switching process performed by the control device 40 of FIGS. 15 to 17.
  • the process shown in FIG. 14 is called at the start of operation of the refrigeration cycle device 400 by the main routine that integrally controls the refrigeration cycle device 400.
  • the control device 40 starts the start mode from S401.
  • the control device 40 communicates the ports P1 and P3 with each other in S401 to advance the process to S403.
  • the control device 40 advances the process to S404 with the expansion valve 43 fully opened in S403.
  • the control device 40 activates the compression mechanism 411 in S404 and advances the process to S405.
  • the control device 40 determines in S405 whether or not the reference time Tm4 has elapsed from the activation of the compression mechanism 411.
  • the reference time Tm4 is appropriately determined by an actual machine experiment or a simulation. If the reference time Tm4 has not elapsed since the start of the compression mechanism 411 (NO in S405), the control device 40 waits for a certain period of time in S406 and then returns the process to S405.
  • the control device 40 determines in S407 whether the temperature T4 is higher than the reference temperature Trf4.
  • the reference temperature Trf4 is appropriately determined by an actual experiment or a simulation.
  • the control device 40 waits for a certain period of time in S408 and then returns the process to S407.
  • the control device 40 advances the process to S409 and switches the operation mode from the start mode to the normal mode.
  • the start mode ends and the normal mode starts.
  • the control device 40 communicates the ports P1 and P2 in S409 and advances the process to S410.
  • the control device 40 activates the compression mechanism 412 in S410 and returns the process to the main routine.
  • the refrigerating cycle apparatus According to the refrigerating cycle apparatus according to the fourth embodiment, it is possible to suppress a pressure drop of the refrigerant sucked into the compressor at the start of operation of the refrigerating cycle apparatus regardless of the type of the refrigerant.
  • Embodiment 5 In the second embodiment, the configuration in which the density of the refrigerant sucked into the compressor is reduced by heating the refrigerant flowing out of the evaporator by the refrigerant discharged by the compressor has been described. In the fifth embodiment, a configuration in which the refrigerant sucked into the compressor is heated by the heater will be described.
  • FIG. 19 is a functional block diagram showing the configuration of the refrigeration cycle device 500 according to the fifth embodiment and the flow of the refrigerant in the cooling operation.
  • the refrigeration cycle device 500 includes an outdoor unit 510 and an indoor unit 520.
  • the indoor unit 520 is arranged in the indoor space.
  • the outdoor unit 510 is arranged outdoors.
  • the refrigerating cycle device 500 is filled with a refrigerant containing R290.
  • the indoor unit 520 includes a heat exchanger 52 (first heat exchanger).
  • the outdoor unit 510 includes a compressor 51, an expansion valve 53, a heat exchanger 54 (second heat exchanger), a gas-liquid separator 55, a four-way valve 56, a flow rate adjusting unit 530, and a temperature sensor TS5. , And the control device 50.
  • the flow rate adjusting unit 530 has a heater 57.
  • the control device 50 may be included in the indoor unit 520, or may be provided separately from the outdoor unit 510 and the indoor unit 520.
  • the control device 50 controls the compressor 51 and the expansion valve 53 as in the first embodiment.
  • the control device 50 controls the four-way valve 56 to switch the circulation direction of the refrigerant.
  • the control device 50 communicates the discharge port of the compressor 51 with the heat exchanger 54 and the suction port of the compressor 51 with the heat exchanger 52 in the cooling operation.
  • the refrigerant circulates in the circulation direction (second circulation direction) of the compressor 51, the heat exchanger 54, the expansion valve 53, and the heat exchanger 52.
  • the heat exchangers 52 and 54 function as evaporators and condensers, respectively.
  • the gas-liquid separator 55 receives the refrigerant from the heat exchanger 52, separates the gas refrigerant and the liquid refrigerant, stores the liquid refrigerant, and guides the gas refrigerant to the compressor 51.
  • the gas-liquid separator 55 prevents the liquid refrigerant from being sucked into the compressor 51.
  • the gas-liquid separator 55 includes an accumulator or a suction muffler.
  • the heater 57 is arranged to heat the refrigerant flowing into the gas-liquid separator 55.
  • the heater 57 is stopped in the cooling operation.
  • FIG. 20 is a functional block diagram showing the configuration of the refrigeration cycle device 500 according to the fifth embodiment and the flow of the refrigerant in the normal mode of the heating operation.
  • the refrigeration cycle device 500 includes a start mode and a normal mode as an operation mode of the heating operation.
  • the start mode is executed when the compressor 51 is started.
  • Normal mode is executed following boot mode.
  • the control device 50 communicates the discharge port of the compressor 51 with the heat exchanger 52 and the suction port of the compressor 51 with the heat exchanger 54 in the heating operation.
  • the control device 50 does not operate the heater 57 in the normal mode of heating operation.
  • the control device 50 acquires the temperature T5 of the refrigerant that has passed through the heated portion of the heater 57 in the heating operation from the temperature sensor TS5.
  • the heating portion is included in the flow path through which the refrigerant flowing between the heat exchanger 54 and the compressor 51 passes in the heating operation.
  • the refrigerant circulates in the circulation direction (first circulation direction) of the compressor 51, the heat exchanger 52, the expansion valve 53, and the heat exchanger 54.
  • the heat exchangers 52 and 54 function as condensers and evaporators, respectively.
  • FIG. 21 is a functional block diagram showing the configuration of the refrigeration cycle device 500 according to the fifth embodiment and the flow of the refrigerant in the start mode of the heating operation.
  • the control device 50 operates the heater 57 in the activation mode.
  • the density of the refrigerant sucked into the compressor 51 in the start mode is smaller than the density of the refrigerant sucked into the compressor 51 in the normal mode due to heating by the heater 57.
  • the control device 50 controls the compressor 51 and the flow rate adjusting unit 530 to reduce the amount of refrigerant passing through the heat exchanger 52 and the expansion valve 53 per unit time in the start mode than the amount of the refrigerant in the normal mode. ..
  • the amount of the refrigerant sucked into the compressor 51 per unit time decreases, so that the amount of the refrigerant flowing between the heat exchanger 54 and the compressor 51 sharply decreases when the compressor 51 is started. Is prevented.
  • FIG. 22 is a flowchart showing the flow of the operation mode switching process performed by the control device 50 of FIGS. 19 to 21.
  • the process shown in FIG. 22 is called at the start of operation of the refrigeration cycle device 500 by the main routine that integrally controls the refrigeration cycle device 500.
  • the control device 50 starts the activation mode from S501.
  • the control device 50 activates the heater 57 in S501 to advance the process to S503.
  • the control device 50 advances the process to S504 with the expansion valve 53 fully opened in S503.
  • the control device 50 activates the compressor 51 in S504 and advances the process to S505.
  • the control device 50 determines in S505 whether or not the reference time Tm5 has elapsed from the start of the compressor 51.
  • the reference time Tm5 is appropriately determined by an actual machine experiment or a simulation.
  • the control device 50 waits for a certain period of time in S506 and then returns the process to S505.
  • the control device 50 determines whether or not the temperature T5 is higher than the reference temperature Trf5 in S507.
  • the reference temperature Trf5 is appropriately determined by an actual experiment or a simulation.
  • the control device 50 waits for a certain period of time in S508 and then returns the process to S507.
  • the control device 50 advances the process to S509 and switches the operation mode from the start mode to the normal mode.
  • the start mode ends and the normal mode starts.
  • the control device 50 stops the heater 57 in S509 and returns the process to the main routine.
  • the refrigerating cycle apparatus According to the refrigerating cycle apparatus according to the fifth embodiment, it is possible to suppress a pressure drop of the refrigerant sucked into the compressor at the start of operation of the refrigerating cycle apparatus regardless of the type of the refrigerant.

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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)
  • Air Conditioning Control Device (AREA)
PCT/JP2019/031273 2019-08-07 2019-08-07 冷凍サイクル装置 Ceased WO2021024443A1 (ja)

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EP19940618.2A EP4012293B1 (en) 2019-08-07 2019-08-07 Refrigeration cycle device
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CN115993016A (zh) * 2022-12-02 2023-04-21 珠海格力电器股份有限公司 空调系统、空调机组及控制方法
CN116007248A (zh) * 2022-12-22 2023-04-25 无锡市好冰冷暖技术有限公司 一种制冷及化霜系统
CN117870183A (zh) * 2023-12-15 2024-04-12 北京京仪自动化装备技术股份有限公司 半导体温控装置及温控方法

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CN117870183A (zh) * 2023-12-15 2024-04-12 北京京仪自动化装备技术股份有限公司 半导体温控装置及温控方法

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JPWO2021024443A1 (https=) 2021-02-11

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