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WO2020255355A1 - Unité extérieure, dispositif à cycle frigorifique et réfrigérateur - Google Patents

Unité extérieure, dispositif à cycle frigorifique et réfrigérateur Download PDF

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Publication number
WO2020255355A1
WO2020255355A1 PCT/JP2019/024585 JP2019024585W WO2020255355A1 WO 2020255355 A1 WO2020255355 A1 WO 2020255355A1 JP 2019024585 W JP2019024585 W JP 2019024585W WO 2020255355 A1 WO2020255355 A1 WO 2020255355A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
passage
flow path
outdoor unit
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2019/024585
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English (en)
Japanese (ja)
Inventor
亮 築山
智隆 石川
悟 梁池
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 CN201980097419.4A priority Critical patent/CN114127492B/zh
Priority to EP19933763.5A priority patent/EP3988871A4/fr
Priority to JP2021528581A priority patent/JP7278376B2/ja
Priority to PCT/JP2019/024585 priority patent/WO2020255355A1/fr
Publication of WO2020255355A1 publication Critical patent/WO2020255355A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • 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
    • F25B2400/16—Receivers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/22—Preventing, detecting or repairing leaks of refrigeration fluids
    • F25B2500/222—Detecting refrigerant leaks
    • 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
    • F25B2500/24—Low amount of refrigerant in the system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures

Definitions

  • the present invention relates to an outdoor unit, a refrigeration cycle device, and a refrigerator.
  • the air conditioner is described in Japanese Patent No. 5505477.
  • refrigerating cycle devices such as refrigerators in which a receiver is generally provided between the condenser and the expansion valve.
  • a refrigeration cycle device provided with a receiver, the degree of supercooling at the outlet of the condenser does not change much even if the amount of refrigerant decreases when the amount of refrigerant in the receiver is decreasing. Therefore, the method described in Japanese Patent No. 5505477 cannot detect a decrease in the amount of refrigerant unless the amount of leakage of the refrigerant is large.
  • the present invention has been made to solve the above problems, and it is possible to prevent performance deterioration due to incorrect setting of the refrigerant type, and even if the configuration has a receiver, leakage of the refrigerant occurs at a stage where the amount of leakage is small. It is an object of the present invention to provide an outdoor unit, a freezing cycle device and a refrigerator of a refrigerating cycle device capable of detecting.
  • the present disclosure relates to an outdoor unit of a refrigeration cycle device configured to be connected to a load device including a first expansion valve and an evaporator.
  • the outdoor unit includes a heat exchanger and a liquid receiver.
  • the heat exchanger has a compressor having an intake port and a discharge port, a condenser, and a first passage and a second passage, and heat exchange between the refrigerant flowing through the first passage and the refrigerant flowing through the second passage. Is configured to do.
  • the receiver is arranged between the condenser and the first passage of the heat exchanger and is configured to store the refrigerant.
  • the flow path from the compressor to the first passage of the condenser, the liquid receiver, and the heat exchanger is configured to form a circulation flow path through which the refrigerant circulates together with the load device.
  • the outdoor unit is arranged in the first refrigerant flow path configured to flow the refrigerant from the receiver of the circulation flow path or the outlet pipe of the liquid receiver to the inlet of the second passage, and the first refrigerant flow path.
  • the two expansion valves are further provided with a second refrigerant flow path configured to allow the refrigerant to flow from the outlet of the second passage to the compressor.
  • the possibility of performance deterioration due to incorrect setting of the refrigerant type is reduced, and even if the configuration has a receiver, the refrigerant is in the stage of a small leakage amount. Amount of leakage can be detected.
  • FIG. It is an overall block diagram of the refrigerating cycle apparatus 1 according to Embodiment 1.
  • FIG. It is a figure for demonstrating the structure of the receiver of Embodiment 1.
  • FIG. It is a flowchart for demonstrating the process concerning the refrigerant executed by the control device 100. It is a flowchart which showed the detail of the determination process of the amount of a refrigerant executed in step S1 of FIG. It is the figure which superposed the ph diagram of the case where the amount of refrigerant is appropriate and the case where the amount of refrigerant is insufficient. It is a figure for demonstrating the temperature change of the refrigerant in an injection flow path. It is a flowchart which shows the detail of the refrigerant type determination process executed in step S2.
  • FIG. 1 is an overall configuration diagram of a refrigeration cycle apparatus 1 according to the first embodiment. It should be noted that FIG. 1 functionally shows the connection relationship and the arrangement configuration of each device in the refrigeration cycle apparatus, and does not necessarily show the arrangement in the physical space.
  • the refrigeration cycle device 1 includes an outdoor unit 2, a load device 3, and extension pipes 84 and 88.
  • the outdoor unit 2 of the refrigeration cycle device 1 is configured to be connected to the load device 3 by extension pipes 84 and 88.
  • the outdoor unit 2 includes a compressor 10, a condenser 20, a heat exchanger 40, a liquid receiver (receiver) 30, and pipes 80 to 83, 89.
  • the heat exchanger 40 has a first passage H1 and a second passage H2, and is configured to exchange heat between the refrigerant flowing through the first passage H1 and the refrigerant flowing through the second passage H2.
  • the liquid receiver 30 is arranged between the first passage H1 of the heat exchanger 40 and the condenser 20, and is configured to store the refrigerant.
  • the flow path from the compressor 10 to the condenser 20, the liquid receiver 30, and the first passage H1 of the heat exchanger 40 is configured to form a circulation flow path through which the refrigerant circulates together with the load device 3.
  • this circulation flow path is also referred to as a "main circuit" of the refrigeration cycle.
  • the outdoor unit 2 further includes a first refrigerant flow path 91, a second expansion valve 92 arranged in the first refrigerant flow path 91, and a second refrigerant flow path 94.
  • the first refrigerant flow path 91 is configured to allow the refrigerant to flow from the liquid receiver 30 of the circulation flow path or the outlet pipe of the liquid receiver 30 to the inlet of the second passage H2.
  • the second refrigerant flow path 94 is configured to allow the refrigerant to flow from the outlet of the second passage H2 to the compressor 10.
  • this flow path that branches from the main circuit and sends the refrigerant to the compressor 10 via the second passage H2 is referred to as an “injection flow path”.
  • the load device 3 includes a first expansion valve 50, an evaporator 60, and pipes 85, 86, 87.
  • the first expansion valve 50 is, for example, a temperature expansion valve that is controlled independently of the outdoor unit 2.
  • the compressor 10 compresses the refrigerant sucked from the pipes 89 and 94 and discharges it to the pipe 80.
  • the compressor 10 has a suction port G1, a discharge port G2, and an intermediate pressure port G3.
  • the compressor 10 is configured to suck the refrigerant that has passed through the evaporator 60 from the suction port G1 and discharge the refrigerant from the discharge port G2 toward the condenser 20.
  • the second refrigerant flow path 94 is configured to allow the refrigerant to flow from the outlet of the second passage H2 to the intermediate pressure port G3 of the compressor 10.
  • the compressor 10 is configured to adjust the rotation speed according to a control signal from the control device 100. By adjusting the rotation speed of the compressor 10, the circulation amount of the refrigerant is adjusted, and the refrigerating capacity of the refrigerating cycle device 1 can be adjusted.
  • Various types of compressors 10 can be adopted, and for example, scroll type, rotary type, screw type and the like can be adopted.
  • the condenser 20 condenses the refrigerant discharged from the compressor 10 to the pipe 80 and flows it to the pipe 81.
  • the condenser 20 is configured such that a high-temperature and high-pressure gas refrigerant discharged from the compressor 10 exchanges heat with the outside air. By this heat exchange, the heat-dissipated refrigerant condenses and changes into a liquid phase.
  • a fan (not shown) supplies the condenser 20 with outside air through which the refrigerant exchanges heat in the condenser 20. By adjusting the rotation speed of the fan, the refrigerant pressure on the discharge side of the compressor 10 can be adjusted.
  • the outdoor unit 2 further includes pressure sensors 110, 111, 112, temperature sensors 121, 122, 123, and a control device 100 that controls the outdoor unit 2.
  • the pressure sensor 110 detects the pressure PL of the suction refrigerant of the compressor 10 and outputs the detected value to the control device 100.
  • the pressure sensor 111 detects the pressure PH of the discharged refrigerant of the compressor 10 and outputs the detected value to the control device 100.
  • the pressure sensor 112 detects the pressure PM of the pipe 93 at the outlet of the second expansion valve 92, and outputs the detected value to the control device 100.
  • the temperature sensor 121 detects the temperature T1 of the refrigerant in the pipe 82 at the outlet of the receiver 30, and outputs the detected value to the control device 100.
  • the temperature sensor 122 detects the temperature T2 of the refrigerant at the inlet of the second passage H2 on the cooling side of the heat exchanger 40, and outputs the detected value to the control device 100.
  • the temperature sensor 123 detects the temperature T3 of the refrigerant at the outlet of the second passage H2 on the cooling side of the heat exchanger 40, and outputs the detected value to the control device 100.
  • the control device 100 includes a CPU (Central Processing Unit) 102, a memory 104 (ROM (Read Only Memory) and RAM (Random Access Memory)), an input / output buffer (not shown) for inputting / outputting various signals, and the like. Consists of including.
  • the CPU 102 expands the 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 described.
  • the control device 100 executes control of each device in the outdoor unit 2 according to these programs. This control is not limited to software processing, but can also be processed by dedicated hardware (electronic circuit).
  • control device 100 includes a) determination of the amount of refrigerant sealed in the refrigeration cycle device 1, b) determination of the type of refrigerant sealed in the refrigeration cycle device 1, and c) determination of the refrigeration cycle device 1. It is configured to control the outdoor unit 2 corresponding to the type of the sealed refrigerant.
  • FIG. 2 is a diagram for explaining the configuration of the receiver of the first embodiment.
  • the liquid receiver 30 includes a housing 31 for storing the liquid refrigerant, an inlet pipe IP1, a first outlet pipe OP1, and a second outlet pipe OP2.
  • the outlet from the liquid receiver 30 to the circulation flow path, which is the main circuit, is the first outlet pipe OP1.
  • the second outlet pipe OP2 is an outlet from the receiver 30 that is different from the first outlet pipe OP1.
  • the first refrigerant flow path 91 is configured to allow the refrigerant to flow from the second outlet pipe OP2 to the inlet of the second passage H2 of the heat exchanger 40.
  • the suction port of the second outlet pipe OP2 is arranged at a position higher than the suction port of the first outlet pipe OP1.
  • the height L1 of the suction port of the first outlet pipe OP1 and the height L2 of the suction port of the second outlet pipe OP2 are lower than the liquid level height L0 when the amount of the refrigerant is appropriate.
  • the height L2 of the suction port of the second outlet pipe OP2 is between the height L1 and the height L0, and the position in the height direction is determined according to the sensitivity of the refrigerant shortage to be detected.
  • the height L2 is brought close to the height L0, the gas refrigerant is sucked even if the liquid level of the refrigerant is slightly lowered, so that the detection sensitivity of the refrigerant shortage becomes high.
  • the gas refrigerant is not sucked even if the liquid level of the refrigerant is slightly lowered, so that the refrigerant shortage can be detected, but the detection sensitivity is lowered.
  • the branch portion is often provided at the outlet of the first passage H1 of the heat exchanger 40. Even if the branch portion is provided at the outlet of the first passage H1 of the heat exchanger 40, the refrigerant shortage can be detected, but the detection sensitivity is lowered. In the present embodiment, this branch portion is changed to a portion for storing the liquid refrigerant of the receiver 30.
  • the control device 100 has a refrigerant amount determination process for early detecting that the refrigerant is insufficient due to refrigerant leakage, and a refrigerant type that distinguishes between the pseudo azeotropic refrigerant and the non-azeotropic refrigerant. The determination process and the control process of the compressor 10 that maintains the refrigerating capacity according to the composition when the composition of the non-azeotropic refrigerant changes can be executed.
  • FIG. 3 is a flowchart for explaining the processing related to the refrigerant executed by the control device 100.
  • the processing of this flowchart is executed at the initial start-up after the installation of the refrigeration cycle device 1 or every time the power is turned on after the installation.
  • the control device 100 executes a refrigerant amount determination process for early detection of refrigerant leakage.
  • the control device 100 executes a refrigerant type determination process for determining whether the refrigerant sealed in the refrigeration cycle device 1 is a pseudo-azeotropic refrigerant or a non-azeotropic refrigerant.
  • step S3 the control device 100 executes a process of controlling the compressor so as to maintain the refrigerating capacity according to the composition when the composition of the non-azeotropic refrigerant changes.
  • FIG. 4 is a flowchart showing the details of the refrigerant amount determination process executed in step S1 of FIG.
  • the position of the second outlet pipe OP2 for introducing the liquid refrigerant into the injection flow path is appropriate as shown in FIG.
  • the liquid refrigerant is sent from the receiver 30 to the injection flow path when the amount of the refrigerant is appropriate, and the gas refrigerant is sent to the injection flow path when the liquid refrigerant is insufficient.
  • step S11 the control device 100 adjusts the opening degree of the second expansion valve 92 so that the dryness X at point B on the intermediate pressure side of the heat exchanger 40 is smaller than 1 on the assumption that the amount of refrigerant is appropriate. ..
  • the control device 100 determines the target opening degree of the second expansion valve 92 based on the pressure PH of the high pressure portion, the intermediate pressure PM, and the operating frequency of the compressor 10. As a result, the two-phase refrigerant flows in the second passage H2 of the heat exchanger 40. This refrigerant is heated by heat exchange with the liquid refrigerant on the high pressure side flowing through the first passage H1.
  • step S12 the control device 100 detects the temperature T2 of the refrigerant at the inlet of the second passage of the heat exchanger 40 and the temperature T3 of the refrigerant at the outlet using the temperature sensors 122 and 123. Then, in step S13, the control device 100 determines whether or not the difference between the temperature T2 and the temperature T3 of the refrigerant is larger than the threshold value.
  • the temperature difference will be below the threshold value (NO in S13).
  • the amount of refrigerant is less than the appropriate amount, the refrigerant flowing in the second passage H2 becomes a gas state from the middle, so that all the heat given by heating becomes sensible heat, and the temperature difference is from the threshold value. Also increases (YES in S13). This temperature difference will be described in detail with reference to FIGS. 5 and 6.
  • FIG. 5 is a diagram showing the ph diagram in the case where the amount of refrigerant is appropriate and the case where the amount of refrigerant is insufficient.
  • the state of the refrigerant on the ph diagram shifts from the point A to the point B.
  • FIG. 1 shows the positions of points A and B before and after the second expansion valve 92.
  • the positions indicating the state of the refrigerant on the ph diagram before and after the second expansion valve 92 are from the points A and B to the points A'and B, respectively. Move to ′.
  • FIG. 6 is a diagram for explaining a temperature change of the refrigerant in the injection flow path.
  • the point A is the liquid region and the point B is the two-phase region, so that the refrigerant flowing into the second passage H2 of the heat exchanger 40 is It is in a two-phase state. Therefore, the temperature changes slowly with the change of enthalpy. At this time, the temperature change of the refrigerant passing through the second passage H2 of the heat exchanger 40 changes from the point B to the point C in FIG. 6, but the amount of the temperature change is small.
  • step S14 the control device 100 determines that the refrigerant is insufficient, and informs the user or the maintenance company of the refrigerant shortage. Notice.
  • the notification is performed by, for example, an LED display mounted on a board or a remote controller, an alarm sound, or the like.
  • the operation of the refrigeration cycle device may be stopped in step S15.
  • control is returned to the main routine of FIG. 3 in step S16. In this case, the process of determining the type of refrigerant in step S2 is subsequently performed.
  • FIG. 7 is a flowchart showing the details of the refrigerant type determination process executed in step S2.
  • the user When a device that can be shared by two types of refrigerants is developed, the user generally sets which refrigerant is filled in the device.
  • the apparatus automatically determines the type of the refrigerant.
  • step S21 the control device 100 adjusts the opening degree of the second expansion valve 92 so that the dryness X at point B on the intermediate pressure side of the heat exchanger 40 is smaller than 1 on the assumption that the amount of refrigerant is appropriate. ..
  • the control device 100 determines the target opening degree of the second expansion valve 92 based on the pressure PH of the high pressure portion, the intermediate pressure PM, and the operating frequency of the compressor 10. As a result, the two-phase refrigerant flows in the second passage H2 of the heat exchanger 40. This refrigerant is heated by heat exchange with the liquid refrigerant on the high pressure side flowing through the first passage H1.
  • step S22 the control device 100 detects the temperature T2 of the refrigerant at the inlet of the second passage of the heat exchanger 40 and the temperature T3 of the refrigerant at the outlet using the temperature sensors 122 and 123.
  • steps S21 and S22 may be omitted when the results of the processes executed in steps S11 and S12 in FIG. 4 are used as they are.
  • step S23 the control device 100 determines whether or not the temperature difference between the temperature T2 and the temperature T3 of the refrigerant is larger than the threshold value.
  • This threshold value is a threshold value set for determining the type of refrigerant.
  • the temperature difference between the temperature T2 and the temperature T3 of the refrigerant differs depending on whether the refrigerant is a non-azeotropic mixed refrigerant or a pseudo-azeotropic refrigerant. This temperature difference will be described in detail with reference to FIGS. 8 and 9.
  • FIG. 8 is a ph diagram when R410A, which is a pseudo azeotropic refrigerant, is used.
  • R410A which is a pseudo azeotropic refrigerant
  • the isotherms in the two-phase region sandwiched between the saturated liquid line and the saturated gas line are substantially horizontal. That is, there is no temperature gradient for enthalpy changes in the two-phase region. Therefore, there is almost no temperature difference between the temperature of the point B before being heated and the temperature of the point C after being heated in the second passage H2 of the heat exchanger 40.
  • FIG. 9 is a ph diagram when R463A, which is a non-azeotropic refrigerant, is used.
  • R463A which is a non-azeotropic refrigerant
  • the isotherm in the two-phase region sandwiched between the saturated liquid line and the saturated gas line is downward-sloping. That is, there is a temperature gradient for enthalpy changes in the two-phase region. Therefore, there is a temperature difference between the temperature of the point B before being heated and the temperature of the point C after being heated in the second passage H2 of the heat exchanger 40.
  • the point B is on the isotherms at 10 ° C. or lower.
  • the point C is on the isotherm around 10 ° C. That is, the temperature T3 of the two-phase refrigerant in the state of point C is higher than the temperature T2 of the two-phase refrigerant in the state of point B.
  • the threshold value in step S23 of FIG. 4 is set to a value that can distinguish the refrigerants of FIGS. 8 and 9.
  • step S24 the control device 100 determines that the enclosed refrigerant is a non-azeotropic refrigerant.
  • T3-T2> threshold value is not satisfied (NO in S23)
  • step S25 the control device 100 determines that the enclosed refrigerant is a pseudo azeotropic refrigerant.
  • step S24 or S25 When the refrigerant type is determined in step S24 or S25, the process proceeds to step S26, and subsequently, the compressor control in step S3 of FIG. 3 is executed.
  • FIG. 10 is a flowchart showing the details of the compressor control executed in step S3.
  • the control device 100 determines whether or not the refrigerant is a non-azeotropic refrigerant based on the determination result in step S2.
  • the control device 100 makes the conversion formula between the pressure and the evaporation temperature correspond to the pseudo azeotropic refrigerant in step S39. Then, in step S40, the control device 100 determines the suction pressure for controlling the evaporation temperature. Further, the control device 100 changes the operating frequency of the compressor 10 in step S41.
  • the composition of the refrigerant circulating in the refrigeration cycle apparatus is determined by the ratio of the mass of the gas refrigerant in the receiver 30 to the total mass of the enclosed refrigerant. For example, when the inside of the receiver 30 is full and there is no gas refrigerant, the composition of the circulating refrigerant matches the composition at the time of filling. However, when there is a gas refrigerant in the receiver 30, the gas refrigerant stays in the receiver 30 and does not circulate in the refrigeration cycle device. Therefore, the composition of the refrigerant circulating in the refrigeration cycle apparatus is the composition of the refrigerant excluding the gas refrigerant in the receiver 30.
  • step S32 the control device 100 acquires the temperature T1 at the inlet of the second expansion valve 92 from the temperature sensor 121. Then, in step S33, the control device 100 converts the temperature T1 into enthalpy. In parallel with these, in step S34, the control device 100 acquires the pressure PM and the temperature T2 at the inlet of the second passage H2 of the heat exchanger 40 from the pressure sensor 112 and the temperature sensor 122, respectively.
  • step S35 the control device 100 detects the composition of the refrigerant from the enthalpy, the pressure PM, and the temperature T2.
  • the saturation temperature can be obtained from the pressure and enthalpy, and conversely, if the pressure, enthalpy and saturation temperature are known, the composition can be specified.
  • the composition is known, if two of the pressure, enthalpy, and temperature are known, the other one can be known. Also, if the pressure, enthalpy, and temperature are all known, the composition can be known.
  • the conversion map is used by the controller 100 to identify the refrigerant composition.
  • FIG. 11 is a diagram for explaining the detection of the composition of the refrigerant in step S35.
  • FIG. 11 shows the relationship between composition and temperature when pressure and enthalpy are fixed.
  • the relationship between the composition and the temperature in the portion where the refrigerant composition is detected that is, the intermediate pressure portion in the refrigeration cycle apparatus is shown.
  • the vertical axis shows the temperature T2 of the refrigerant at the inlet of the heat exchanger 40
  • the horizontal axis shows the weight ratio of the amount of gas refrigerant / the amount of filled refrigerant in the receiver 30 as a percentage.
  • the enthalpy converted from the temperature T1 and the pressure PM are fixed to a certain value.
  • the temperature T2 corresponds to the weight ratio of the amount of gas refrigerant / the amount of filled refrigerant in a ratio of 1: 1.
  • the temperature T2 is ⁇ 6.8 ° C.
  • the actual temperature T2 is ⁇ 5 ° C. To do. Therefore, the temperature deviation ⁇ T from the case of the pure composition corresponds to 0.25 of the weight ratio (%) of the amount of gas refrigerant / the amount of enclosed refrigerant shown on the horizontal axis.
  • the composition of the circulating refrigerant can be determined if the temperature T2 is known.
  • the relationship shown in such a graph exists for each pressure and each enthalpy. Therefore, it is possible to create a map for determining the composition of the refrigerant from the pressure PM, the temperature T2, and the temperature T1.
  • step S35 The composition determination process of the circulating refrigerant described above is executed in step S35. Subsequently, in step S36, the control device 100 associates the pressure and evaporation temperature conversion formulas with the detected composition.
  • the evaporation temperature here is the average evaporation temperature of dew boiling.
  • FIG. 12 is a diagram for explaining the relationship between the composition and the evaporation temperature.
  • FIG. 12 shows the relationship between the composition and the temperature when the pressure and the enthalpy are fixed.
  • the relationship between the composition and the temperature in the portion reflected in the control of the refrigeration cycle apparatus, that is, the low pressure portion in the refrigeration cycle apparatus is shown.
  • the vertical axis shows the average evaporation temperature of the evaporator 60
  • the horizontal axis shows the weight ratio of the amount of gas refrigerant / the amount of filled refrigerant in the receiver 30 as a percentage.
  • the graph shown in FIG. 12 corresponds to a map for reflecting the detected composition in the control.
  • the average evaporation temperature is ⁇ 40 ° C.
  • the gas refrigerant corresponding to the composition is shown in the map shown in FIG.
  • the average evaporation temperature becomes ⁇ 38.5 ° C.
  • step S37 the control device 100 determines the pressure PL for controlling the refrigeration cycle device as the suction pressure so as to realize the average evaporation temperature obtained in step S36. Then, in step S38, the control device 100 changes the operating frequency of the compressor 10 so as to have a pressure PL.
  • control device 100 controls the compressor 10 with the pressure corresponding to the saturation temperature suitable for the detected composition as the target value of the pressure PL on the inlet side of the compressor 10.
  • step S38 or step S41 the control returns to the flowchart of FIG. 3 in step S42.
  • the flowchart of FIG. 3 is repeatedly executed to control the compressor 10 according to the composition of the circulating refrigerant when the amount of liquid in the receiver 30 changes. Will be done.
  • the control device 100 is configured to maintain the refrigerating capacity of the refrigerating cycle device by reflecting the change in the composition of the refrigerant in the control when a non-azeotropic refrigerant is used as the refrigerant.
  • the refrigeration cycle device According to the refrigeration cycle device according to the first embodiment described above, it is possible to detect a refrigerant shortage before the receiver is emptied, that is, at a stage where the amount of refrigerant leakage is small.
  • the refrigerating capacity of the refrigeration cycle apparatus can be maintained by reflecting the change in the composition of the refrigerant in the control.
  • the injection flow path and the heat exchanger 40 which are standard circuits for controlling the discharge temperature of the refrigerator, are used, so that a special composition detection circuit is not added and the cost is reduced. A space refrigerator can be realized.
  • FIG. 13 is a diagram showing the configuration of the refrigeration cycle device 101 according to the second embodiment.
  • the refrigeration cycle device 101 includes an outdoor unit 102, a load device 3, and extension pipes 84 and 88.
  • the load device 3 has the same configuration as that of the first embodiment.
  • the outdoor unit 102 of the refrigeration cycle device 101 is configured to be connected to the load device 3 by extension pipes 84 and 88.
  • the outdoor unit 102 includes a compressor 10, a condenser 20, a heat exchanger 40, a liquid receiver 30, and pipes 80 to 83, 89.
  • the flow path from the compressor 10 to the condenser 20, the liquid receiver 30, and the first passage H1 of the heat exchanger 40 is configured to form a circulation flow path through which the refrigerant circulates together with the load device 3.
  • the “main circuit”, which is the circulation flow path, has the same configuration as the refrigeration cycle device 1 of the first embodiment.
  • the outdoor unit 102 further includes a first refrigerant flow path 91, a second expansion valve 92 arranged in the first refrigerant flow path 91, and a second refrigerant flow path 94.
  • the "injection flow path” which is a flow path for branching from the main circuit and sending the refrigerant to the compressor 10 via the second passage H2
  • the compressor in the refrigeration cycle device 1 of the first embodiment shown in FIG. It was connected to 10 intermediate pressure ports.
  • the injection flow path is connected to the suction port of the compressor 10.
  • the control device 100 substitutes the pressure PL detected by the pressure sensor 110 in place of the pressure PM detected by the pressure sensor 112 in FIG. 1, and executes the refrigerant shortage detection, the refrigerant identification, and the refrigerant composition detection. be able to.
  • the second refrigerant flow path 94 is configured to allow the refrigerant to flow from the outlet of the second passage H2 to the suction port G1 of the compressor 10.
  • the pressure sensor 112 of the first embodiment can be reduced while realizing composition detection.
  • Embodiment 3 In the second embodiment, an example in which the connection destination of the injection flow path is changed from the intermediate pressure port of the compressor to the suction port has been described. In the third embodiment, an example of changing the branch portion b of the injection flow path from the receiver to the outlet piping portion of the receiver will be described.
  • FIG. 14 is a diagram showing the configuration of the refrigeration cycle device 201 according to the third embodiment.
  • the refrigeration cycle device 201 includes an outdoor unit 202, a load device 3, and extension pipes 84, 88.
  • the load device 3 has the same configuration as that of the first and second embodiments.
  • the outdoor unit 202 of the refrigeration cycle device 201 is configured to be connected to the load device 3 by extension pipes 84 and 88.
  • the outdoor unit 202 includes a compressor 10, a condenser 20, a heat exchanger 40, a liquid receiver 30, and pipes 80 to 83, 89.
  • the flow path from the compressor 10 to the condenser 20, the liquid receiver 30, and the first passage H1 of the heat exchanger 40 is configured to form a circulation flow path through which the refrigerant circulates together with the load device 3.
  • the “main circuit”, which is the circulation flow path, has the same configuration as the refrigeration cycle device 1 of the first embodiment and the refrigeration cycle device 101 of the second embodiment.
  • the outdoor unit 102 further includes a first refrigerant flow path 91, a second expansion valve 92 arranged in the first refrigerant flow path 91, and a second refrigerant flow path 94.
  • the refrigerating cycle device 1 of the first embodiment shown in FIG. 1 receives the liquid. It was branched from the vessel 30.
  • the injection flow path is branched from the portion where the rising pipe 95 is connected to the pipe 82 connected to the outlet of the liquid receiver 30.
  • the outdoor unit 202 further includes a rising pipe 95 configured to branch from the outlet pipe of the receiver 30.
  • the first refrigerant passage 91 is configured to allow the refrigerant to flow from the rising pipe 95 to the inlet of the second passage H2.
  • the refrigerant shortage detection, the refrigerant identification, and the refrigerant composition detection can be executed by the same control as in the first embodiment.
  • the configuration in which the liquid receiver 30 is provided with two outlet pipes as in the first embodiment is expensive to process, the configuration in which the rising pipe 95 is provided can realize the refrigeration cycle device at a lower cost.
  • connection destination of the injection flow path may be the suction port of the compressor 10 instead of the intermediate pressure port of the compressor 10 as in the second embodiment.

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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

Unité extérieure (2) qui comprend un échangeur de chaleur (40) et un récepteur de liquide (30). L'échangeur de chaleur (40) effectue un échange de chaleur entre un fluide frigorigène s'écoulant à travers un premier passage (H1) et un fluide frigorigène s'écoulant à travers un second passage (H2). Le récepteur de liquide (30) est disposé entre un condenseur (20) et le premier passage (H1) de l'échangeur de chaleur (40), et stocke le fluide frigorigène. Un trajet d'écoulement provenant d'un compresseur (10) jusqu'au premier passage (H1) de l'échangeur de chaleur (40), en traversant le condenseur (20) et le récepteur de liquide (30), forme conjointement avec un dispositif de charge (3), un trajet d'écoulement de circulation à travers lequel circule le fluide frigorigène. L'unité extérieure (2) comprend en outre un premier trajet d'écoulement de fluide frigorigène (91), un second détendeur (92) et un second trajet d'écoulement de fluide frigorigène (94). Le premier trajet d'écoulement de fluide frigorigène (91) permet au fluide frigorigène de s'écouler du récepteur de liquide (30) ou de la tuyauterie de sortie du récepteur de liquide (30) dans le trajet d'écoulement de circulation jusqu'à une entrée du second passage (H2). Le second trajet d'écoulement de fluide frigorigène (94) permet au fluide frigorigène de s'écouler depuis une sortie du second passage (H2) jusqu'au compresseur (10).
PCT/JP2019/024585 2019-06-20 2019-06-20 Unité extérieure, dispositif à cycle frigorifique et réfrigérateur Ceased WO2020255355A1 (fr)

Priority Applications (4)

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CN201980097419.4A CN114127492B (zh) 2019-06-20 2019-06-20 室外机组、制冷环路装置以及制冷机
EP19933763.5A EP3988871A4 (fr) 2019-06-20 2019-06-20 Unité extérieure, dispositif à cycle frigorifique et réfrigérateur
JP2021528581A JP7278376B2 (ja) 2019-06-20 2019-06-20 室外ユニット、冷凍サイクル装置および冷凍機
PCT/JP2019/024585 WO2020255355A1 (fr) 2019-06-20 2019-06-20 Unité extérieure, dispositif à cycle frigorifique et réfrigérateur

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PCT/JP2019/024585 WO2020255355A1 (fr) 2019-06-20 2019-06-20 Unité extérieure, dispositif à cycle frigorifique et réfrigérateur

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JP2005308393A (ja) * 2005-07-25 2005-11-04 Daikin Ind Ltd 冷凍装置及び冷凍装置の冷媒量検出方法
JP2007139244A (ja) * 2005-11-16 2007-06-07 Fujitsu General Ltd 冷凍装置
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JP4864110B2 (ja) * 2009-03-25 2012-02-01 三菱電機株式会社 冷凍空調装置
JP2013002801A (ja) * 2011-06-22 2013-01-07 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水暖房装置
JP2015034736A (ja) * 2013-08-08 2015-02-19 アズビル株式会社 乾き度測定装置

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JP4670329B2 (ja) * 2004-11-29 2011-04-13 三菱電機株式会社 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
WO2014080436A1 (fr) * 2012-11-20 2014-05-30 三菱電機株式会社 Dispositif de réfrigération
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JPS555477B2 (fr) 1976-07-28 1980-02-06
JPH0763430A (ja) * 1993-08-26 1995-03-10 Matsushita Electric Ind Co Ltd 冷凍サイクルの飽和蒸気温度検出回路
JP2005308393A (ja) * 2005-07-25 2005-11-04 Daikin Ind Ltd 冷凍装置及び冷凍装置の冷媒量検出方法
JP2007139244A (ja) * 2005-11-16 2007-06-07 Fujitsu General Ltd 冷凍装置
US20090235675A1 (en) * 2008-03-21 2009-09-24 Lg Electronics Inc. Air conditioner and method for changing refrigerant of air-conditioner
JP4864110B2 (ja) * 2009-03-25 2012-02-01 三菱電機株式会社 冷凍空調装置
JP2013002801A (ja) * 2011-06-22 2013-01-07 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水暖房装置
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JPWO2020255355A1 (fr) 2020-12-24
EP3988871A4 (fr) 2022-06-22
CN114127492B (zh) 2023-06-06
JP7278376B2 (ja) 2023-05-19
CN114127492A (zh) 2022-03-01
EP3988871A1 (fr) 2022-04-27

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