WO2019234914A1 - Unité externe et dispositif à cycle frigorifique - Google Patents

Unité externe et dispositif à cycle frigorifique Download PDF

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Publication number
WO2019234914A1
WO2019234914A1 PCT/JP2018/022019 JP2018022019W WO2019234914A1 WO 2019234914 A1 WO2019234914 A1 WO 2019234914A1 JP 2018022019 W JP2018022019 W JP 2018022019W WO 2019234914 A1 WO2019234914 A1 WO 2019234914A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
compressor
pressure
receiver
liquid level
Prior art date
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PCT/JP2018/022019
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English (en)
Japanese (ja)
Inventor
亮 築山
悟 梁池
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020523953A priority Critical patent/JP6903233B2/ja
Priority to PCT/JP2018/022019 priority patent/WO2019234914A1/fr
Priority to CN201880093742.XA priority patent/CN112166290B/zh
Publication of WO2019234914A1 publication Critical patent/WO2019234914A1/fr

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

Definitions

  • the present invention relates to an outdoor unit and a refrigeration cycle apparatus, and particularly to an outdoor unit and a refrigeration cycle apparatus that use a non-azeotropic refrigerant mixture.
  • a mixed refrigerant in which GWP is lowered by mixing a refrigerant composed of a single component with another refrigerant having a lower global warming potential (GWP). May be used.
  • mixed refrigerants there are azeotropic mixed refrigerants and non-azeotropic mixed refrigerants.
  • An azeotropic refrigerant mixture has a constant boiling point when mixed in a certain ratio, and the composition in the gas phase and liquid phase is the same, showing a phase change as if it were a single component.
  • the non-azeotropic refrigerant mixture has only a property as a simple mixture in which the dew point and the boiling point are separated.
  • Patent Document 1 discloses a refrigeration / air conditioning apparatus that can maintain an appropriate operating state even when the composition of the non-azeotropic refrigerant mixture circulating in the refrigeration cycle changes. ing.
  • the refrigerant composition changes depending on the relationship between the refrigerant filling amount in the device and the gas-phase refrigerant amount separated in the receiver. Since the gas-phase refrigerant separated in the receiver does not circulate in the refrigerant circuit, it is necessary to change the control according to the composition of the circulating refrigerant in order to maintain the refrigerating capacity. If the amount of liquid refrigerant in the receiver is known, the amount of gas-phase refrigerant in the receiver can also be known. Therefore, in the refrigeration / air conditioning apparatus disclosed in Japanese Patent Application Laid-Open No. 8-152208 (Patent Document 1), It is calculated from the compressor frequency, and then the composition calculation is performed.
  • This composition calculation method is based on the premise that the refrigerant charging amount is fixed.
  • the amount of refrigerant contained in a refrigeration cycle apparatus such as a refrigerator varies depending on the local equipment connection status (number of indoor units, extended pipe length). Therefore, since the amount of encapsulated refrigerant cannot be assumed at the time of device design, this composition calculation method may not be used.
  • the amount of receiver liquid is determined by the number of indoor units operating and the amount of indoor unit liquid refrigerant. Since the number of indoor unit operations is determined by the compressor frequency under conditions where the load fluctuation (opening / closing of the door, entering / exiting people and objects) is small, the amount of the receiver liquid can be estimated based on the compressor frequency. However, when the compressor frequency fluctuates due to load fluctuations, the number of indoor unit operating units cannot be estimated from the compressor frequency, and therefore the receiver liquid amount cannot be estimated.
  • An object of the present invention is to provide an outdoor unit and a refrigeration cycle apparatus that can detect the composition of a non-azeotropic refrigerant mixture and maintain the refrigeration capacity regardless of whether there is a load fluctuation or the local installation situation. .
  • the outdoor unit includes a compressor, an outdoor heat exchanger, a receiver, a liquid level sensor, a storage device, and a control device.
  • the receiver accommodates the surplus non-azeotropic mixed refrigerant among the refrigerant sealed in the refrigerant circuit including the compressor, the outdoor heat exchanger, the expansion valve, and the indoor heat exchanger.
  • the liquid level sensor is configured to detect the liquid level of the liquid non-azeotropic refrigerant mixture in the receiver.
  • the storage device stores the amount of the non-azeotropic refrigerant mixture enclosed in the refrigerant circuit.
  • the input unit is configured to input the enclosed amount to the storage device.
  • the control device changes the pressure on the suction side of the compressor by controlling the compressor and the expansion valve. The smaller the enclosed amount stored in the storage device, the larger the amount of change in the pressure on the suction side of the compressor when the liquid level changes.
  • the refrigerant composition can be detected even when the air-conditioning load fluctuates or when the local piping length and the number of indoor units are various, and by performing control according to the composition, the refrigeration cycle apparatus Can exhibit an appropriate refrigeration capacity.
  • FIG. It is a figure which shows the structure of the refrigeration cycle apparatus of Embodiment 1.
  • FIG. It is a flowchart for demonstrating the control performed by a control part at the time of construction.
  • 5 is a flowchart for illustrating control executed by a control unit during operation in the first embodiment.
  • It is the figure which showed an example of the refrigerant composition map.
  • It is the graph which showed the relationship between gas density and pressure.
  • 6 is a graph showing how much the gas density varies depending on the gas refrigerant ratio R;
  • Embodiment 2 it is a flowchart for demonstrating the control performed by a control part at the time of a driving
  • FIG. 1 is a diagram illustrating a configuration of the refrigeration cycle apparatus according to the first embodiment.
  • This refrigeration cycle apparatus uses a non-azeotropic refrigerant mixture.
  • a refrigeration cycle apparatus 1 includes a compressor 10, an outdoor heat exchanger 40, a fan 41, an expansion valve 21, an indoor heat exchanger 20, a fan 22, a receiver 42, a liquid, A surface sensor 43, pressure sensors 44 and 45, a storage device 52, a control unit 51, and an input unit 53 are provided.
  • the fan 41 blows air to the outdoor heat exchanger 40.
  • the fan 22 blows air to the indoor heat exchanger 20.
  • the pressure sensor 44 detects the suction side pressure (low pressure) of the compressor 10.
  • the pressure sensor 45 detects the discharge side pressure (high pressure) of the compressor 10.
  • the receiver 42 stores, as a liquid refrigerant, excess refrigerant among the refrigerants circulated in the compressor 10, the outdoor heat exchanger 40, the expansion valve 21, and the indoor heat exchanger 20.
  • the liquid level sensor 43 is configured to detect the liquid level of the receiver 42.
  • various types such as an ultrasonic type, a capacitance type, a float type, and a self-heating type can be used.
  • a sensor for detecting the presence or absence of the liquid level may be installed at a plurality of heights of the receiver 42 to form the liquid level sensor 43.
  • the storage device 52 stores the amount of non-azeotropic refrigerant mixed in the refrigerant circuit.
  • the input unit 53 is used to input the enclosed amount to the storage device 52.
  • the control unit 51 controls the compressor 10 and the expansion valve 21 based on the enclosed amount and the liquid level.
  • the control unit 51 changes the pressure on the suction side of the compressor 10 according to the change in the liquid level.
  • the control unit 51, the storage device 52, and the input unit 53 constitute a control device 50.
  • the outdoor unit 2 includes the compressor 10, the outdoor heat exchanger 40, the fan 41, the receiver 42, the liquid level sensor 43, the pressure sensors 44 and 45, and the control device 50.
  • the indoor unit 3 includes an indoor heat exchanger 20, an expansion valve 21, and a fan 22.
  • the outdoor unit 2 and the indoor unit 3 are connected by liquid piping and gas piping.
  • the receiver 42 stores, as a liquid refrigerant, excess refrigerant among the refrigerants enclosed in the refrigerant circuit including the compressor 10, the outdoor heat exchanger 40, the expansion valve 21, and the indoor heat exchanger 20.
  • the excess liquid refrigerant corresponds to an amount obtained by subtracting the minimum amount of circulating refrigerant necessary for the current operation of the refrigeration cycle from the total amount of refrigerant sealed in the refrigerant circuit.
  • the liquid level sensor 43 is configured to detect the liquid level of the receiver 42.
  • the storage device 52 stores the amount of the non-azeotropic refrigerant mixture enclosed in the refrigerant circuit.
  • the input unit 53 is used to input a sealed amount of the non-azeotropic refrigerant mixture to the storage device 52.
  • the control unit 51 controls the compressor 10 and the expansion valve 21 based on the amount of the non-azeotropic refrigerant mixture and the liquid level of the receiver 42.
  • the control unit 51 changes the pressure on the suction side of the compressor 10 according to the change in the liquid level of the receiver 42.
  • FIG. 2 is a flowchart for explaining the control executed by the control unit during construction.
  • control unit 51 receives from the input unit 53 the amount of non-azeotropic refrigerant mixture input by a construction worker or the like.
  • the input unit 53 may be an input button or a keyboard operated by a construction worker, or may be a connector for connecting a terminal device provided with the input button or the like.
  • the amount of refrigerant that is input varies depending on the length of the refrigerant pipe and the number of indoor units.
  • step S ⁇ b> 2 the input refrigerant amount is transmitted to the control unit 51 and stored in the storage device 52.
  • FIG. 3 is a flowchart for explaining the control executed by the control unit during operation in the first embodiment.
  • the liquid level in the receiver 42 is detected by the liquid level sensor 43 and transmitted to the control unit 51 in step S11.
  • the control unit 51 estimates a refrigerant composition from the refrigerant composition map stored in advance in the storage device 52 according to the refrigerant filling amount and the liquid level height.
  • step S13 the control unit 51 changes the target pressure of the pressure sensor 44 in accordance with the estimated refrigerant composition. And the control part 51 changes the operating frequency of the compressor 11 and the opening degree of the expansion valve 21 so that it may become the changed target pressure.
  • steps S11 to S13 is repeatedly executed at regular time intervals or every time the start condition is satisfied during operation of the refrigeration cycle apparatus.
  • FIG. 4 is a diagram showing an example of a refrigerant composition map.
  • the composition of the non-azeotropic refrigerant that circulates in the refrigerant circuit can be estimated if the proportion of the gas in the sealed container is known.
  • the high-pressure refrigerant is a refrigerant that is easily vaporized
  • the low-pressure refrigerant is a refrigerant that is less easily vaporized than the high-pressure refrigerant.
  • the non-azeotropic refrigerant is a mixture of refrigerants having different boiling points, and each refrigerant to be mixed has a different easiness of vaporization under a certain pressure. If all the refrigerant in the receiver is in a liquid state, the composition of the refrigerant circulating in the refrigerant circuit is equal to the enclosed composition. However, as the proportion of gas in the receiver increases, the composition of the refrigerant circulating in the refrigerant circuit differs from the enclosed composition.
  • the gas in the receiver contains a larger amount of the refrigerant A that is easy to vaporize.
  • the ratio of decreases. Therefore, as the ratio of the refrigerant A in the gas increases, the ratio of the refrigerant B in the liquid refrigerant in the receiver increases. Since the receiver normally sends liquid refrigerant with priority, the gas refrigerant in the receiver does not circulate through the refrigerant circuit.
  • the horizontal axis of FIG. 4 shows the gas refrigerant ratio R, which is a value obtained by dividing the mass of the gas refrigerant in the receiver by the mass of the encapsulated refrigerant, and the vertical axis shows the low-pressure refrigerant ratio of the liquid refrigerant in the receiver.
  • the receiver is designed so that all refrigerants can be collected even when the number of indoor units and the length of the extension pipe are both maximum.
  • the gas refrigerant ratio R 0.5 indicates that the mass of the non-azeotropic refrigerant mixture in the gas state in the receiver is 50% of the mass of the refrigerant enclosed in the entire refrigerant circuit.
  • FIG. 4 shows a case where the pressure in the receiver is high (P H ), an intermediate case (P M ), and a low case (P L ). The lower the pressure in the receiver, the higher the increase rate of the low-pressure refrigerant ratio.
  • FIG. 5 is a graph showing the relationship between gas density and pressure.
  • FIG. 6 is a graph showing how much the gas density varies depending on the gas refrigerant ratio R.
  • R 0.1, 0.3, 0.5.
  • the gas mass in the receiver can be calculated as the gas density.
  • the liquid level detected by the liquid level sensor 43 can be converted into the gas volume in the above receiver.
  • the gas volume in the receiver may be calculated by substituting the liquid level height into a calculation formula determined by the shape. For example, if the shape of the receiver is a vertical cylinder, the volume of liquid refrigerant can be calculated by low area ⁇ liquid level height, and the gas volume can be calculated by subtracting the volume of liquid refrigerant from the receiver volume of the cylinder Can do.
  • FIG. 7 is a diagram showing the relationship between the low-pressure refrigerant ratio and the change in the saturation temperature of the evaporator in the comparative example in which the control of Embodiment 1 is not applied.
  • FIG. 8 is a diagram illustrating the relationship between the low-pressure refrigerant ratio and the change in the saturation temperature of the condenser in the comparative example in which the control of Embodiment 1 is not applied.
  • FIG. 9 is a diagram showing the relationship between the low-pressure refrigerant ratio and the change in the saturation temperature of the evaporator when the control of Embodiment 1 is applied.
  • FIG. 10 is a diagram showing the relationship between the low-pressure refrigerant ratio and the change in the saturation temperature of the condenser when the control of Embodiment 1 is applied.
  • the target value of the pressure P is changed in accordance with the estimated composition (low-pressure refrigerant ratio).
  • the blowing temperature on the evaporator side is stabilized at ⁇ 10 ° C.
  • the blowing temperature on the condenser side is stabilized at around 40 ° C. This process is executed in steps S12 and S13 of FIG.
  • the control unit 51 changes the suction side pressure of the compressor 10 by controlling the compressor 10 and the expansion valve 21 when the liquid level of the receiver 42 changes.
  • the smaller the amount of the non-azeotropic refrigerant mixture stored in the storage device 52 the larger the amount of change in the pressure on the suction side of the compressor 10 when the liquid level of the receiver 42 changes. This relationship will be specifically described below with reference to FIGS. 4, 9, and 10.
  • the control unit 51 decreases the pressure P. Therefore, when the liquid level of the receiver 42 decreases, the control unit 51 decreases the pressure P.
  • the controller 51 increases the pressure P when the cold pressure refrigerant ratio decreases. Therefore, when the liquid level of the receiver 42 increases, the control unit 51 increases the pressure P.
  • the amount of non-azeotropic refrigerant mixture enclosed is the denominator of the calculation formula of the gas refrigerant ratio R, the larger the amount of non-azeotropic refrigerant mixture, the smaller the gas refrigerant ratio R.
  • the refrigeration cycle apparatus of the first embodiment when a non-azeotropic refrigerant mixture is used, even if the length of the refrigerant pipes and the number of indoor units are different, the refrigerant filling amount to be input By changing this numerical value, the composition of the fluctuating refrigerant can be correctly estimated, and control according to the composition can be performed. Thereby, the temperature of a refrigerator, an air conditioner, etc. can be matched with target temperature correctly.
  • the temperature is made constant by changing the target pressure in accordance with the change in the refrigerant composition.
  • refrigerant leakage may occur from the refrigeration cycle apparatus.
  • the refrigerant composition may change when refrigerant leakage occurs. For example, when the refrigerant leaks from the gas refrigerant portion, the refrigerant A that is easy to vaporize leaks more than the refrigerant B that is difficult to vaporize. Further, when the refrigerant leaks from the liquid refrigerant portion, the composition of the remaining refrigerant also changes depending on the composition of the liquid refrigerant leaked at that time. Therefore, when the refrigerant leaks, it is not appropriate to perform the control shown in the first embodiment.
  • a refrigerant leak can be detected by adding a temperature sensor to the configuration of the first embodiment, and when the refrigerant leak is detected, the control described in the first embodiment is not performed. To do.
  • FIG. 11 is a diagram illustrating a configuration of the refrigeration cycle apparatus according to the second embodiment.
  • This refrigeration cycle apparatus uses a non-azeotropic refrigerant mixture.
  • the refrigeration cycle apparatus 101 includes a compressor 10, an outdoor heat exchanger 40, a fan 41, an expansion valve 21, an indoor heat exchanger 20, a fan 22, a receiver 42, a liquid,
  • storage device 152, and the input part 153 are provided.
  • the storage device 152 stores the amount of non-azeotropic refrigerant mixed in the refrigerant circuit.
  • the input unit 153 is used to input a sealed amount of the non-azeotropic refrigerant mixture into the storage device 152.
  • the control unit 151 controls the compressor 10 and the expansion valve 21 on the basis of the amount of the non-azeotropic refrigerant mixture and the liquid level of the refrigerant in the receiver 42.
  • the controller 151 changes the pressure on the suction side of the compressor 10 according to the change in the liquid level.
  • the control unit 151, the storage device 152, and the input unit 153 constitute the control device 150.
  • the outdoor unit 102 includes a compressor 10, an outdoor heat exchanger 40, a fan 41, a receiver 42, a liquid level sensor 43, pressure sensors 44 and 45, a temperature sensor 26, among these components. And a control device 150.
  • the indoor unit 3 includes an indoor heat exchanger 20, an expansion valve 21, and a fan 22.
  • the outdoor unit 102 and the indoor unit 3 are connected by liquid piping and gas piping.
  • the compressor 10 the outdoor heat exchanger 40, the fan 41, the expansion valve 21, the indoor heat exchanger 20, the fan 22, the receiver 42, the liquid level sensor 43, and the pressure sensors 44 and 45 are the same as those in the first embodiment. The description will not be repeated.
  • the outdoor unit 102 further includes a pressure sensor 45 that detects the pressure on the discharge side of the compressor 10 and a temperature sensor 46 that detects the temperature of the liquid refrigerant accommodated in the receiver 42.
  • the control unit 151 determines whether or not refrigerant has leaked from the refrigerant circuit based on the pressure detected by the pressure sensor 45 and the temperature detected by the temperature sensor 46.
  • FIG. 12 is a flowchart for explaining the control executed by the control unit during operation in the second embodiment.
  • it is determined in step S21 whether or not there is a refrigerant leak. If there is no refrigerant leakage in step S21 (NO in S21), the refrigerant composition is detected in step S22 in the same manner as in S11 to S13 of the first embodiment, and the target pressure is changed in accordance with the composition in step S23.
  • steps S21 to S24 is repeatedly executed at regular time intervals or when the activation condition is satisfied during operation of the refrigeration cycle apparatus.
  • step S21 when it is determined that there is refrigerant leakage (YES in S21), the operation of the refrigeration cycle apparatus is stopped in step S25, and the process ends in step S26. That is, when it is determined that the refrigerant has leaked from the refrigerant circuit, the control unit 151 stops the process of changing the pressure on the suction side of the compressor 10 according to the change in the liquid level of the refrigerant in the receiver 42. In this case, as shown in FIGS. 7 and 8, the compressor 10 and the expansion valve 21 are controlled so that the pressure on the suction side of the compressor 10 is kept constant as in the conventional case.
  • FIG. 13 is a graph for explaining determination of refrigerant leakage.
  • a saturated liquid temperature map corresponding to the refrigerant filling amount and the liquid level in the receiver when there is no refrigerant leakage is stored in advance.
  • the controller 151 compares the saturated liquid temperature T 0 converted from the pressure detected by the pressure sensor 45 with the temperature Td detected by the temperature sensor 46 to determine refrigerant leakage. Specifically, if
  • control unit 151 determines that the magnitude
  • the compressors 10 and 21 are controlled so that the pressure on the suction side of the compressor 10 is kept constant regardless of the change in the liquid level of the receiver.
  • FIG. 14 is a graph showing the relationship between the saturated liquid temperature and the gas refrigerant ratio.
  • the saturated liquid temperature T 0 estimated on the assumption that there is no refrigerant leakage increases as the gas refrigerant ratio R increases.
  • the control unit 151 determines that refrigerant leakage is not.
  • the control unit 151 determines that refrigerant leakage is present.
  • the upper limit determination value T U and the lower limit determination value T L as shown in FIG. 14 is determined for each of the saturated liquid temperature of the line of each pressure shown in FIG. 13.
  • the control unit 151 selects one of the lines in FIG. 13 based on the detected pressure of the pressure sensor 45 and estimates the saturated liquid temperature T 0 corresponding to R obtained from the detected value of the liquid level sensor 43. . Look at whether or not the temperature Td of the temperature sensor 46 detects contrast is between the upper threshold value T U and the lower limit determination value T L, it is determined refrigerant leakage.
  • the leakage of the refrigerant can be detected at the same time. As a result, it is possible to avoid the execution of inappropriate control when the refrigerant leaks.
  • the user may be notified by turning on an abnormal lamp.
  • Embodiment 3 FIG.
  • the construction worker inputs the amount of the non-azeotropic refrigerant mixture when the refrigeration cycle apparatus is constructed and stores it in the storage device.
  • the refrigerant filling amount is automatically calculated based on parameters that are easy for a construction worker to input.
  • FIG. 15 is a diagram showing a configuration of the refrigeration cycle apparatus of the third embodiment.
  • the refrigeration cycle apparatus 201 includes a compressor 10, an outdoor heat exchanger 40, an expansion valve 21, an indoor heat exchanger 20, a receiver 42, a liquid level sensor 43, and a pressure sensor 44. , 45 and a control device 250.
  • the fan is not shown.
  • the control device 250 includes a control unit, a storage device, and an input unit as in FIG.
  • the outdoor unit 202 includes the compressor 10, the outdoor heat exchanger 40, the receiver 42, the liquid level sensor 43, the pressure sensors 44 and 45, and the control device 250 among these components.
  • the indoor unit 203 includes an indoor heat exchanger 20, an expansion valve 21, and a fan 22.
  • the outdoor unit 202 and the indoor unit 203 are connected by a liquid pipe 205 and a gas pipe 204.
  • the lengths of the liquid pipe 205 and the gas pipe 204 may vary from construction site to construction site.
  • the number of indoor units 203 installed may be different for each construction site.
  • the control device 250 receives information such as the length of the extended pipe and the number of connected indoor units from the construction worker. This information may further include the extended pipe diameter, the indoor unit configuration (unit cooler / showcase), and the target evaporation temperature.
  • control device 250 performs the composition estimation of the circulating refrigerant using the refrigerant filling amount calculated based on the information inputted in advance, and performs the control according to the composition as in the first embodiment. Execute.
  • FIG. 16 is a diagram for explaining the calculation of the refrigerant charging amount.
  • the amount M of non-azeotropic mixed refrigerant to be sealed in the refrigerant circuit includes a condenser in the refrigerant quantity M A, the refrigerant quantity M B in the receiver, the refrigerant quantity M C in the liquid extension pipe, an evaporator in the refrigerant quantity M D, the sum of the gas extension pipe refrigerant quantity M E. That is, the following expression is established.
  • M M A + M B + M C + M D + M E
  • the condenser in the refrigerant quantity M A, and the receiver in the refrigerant quantity M B is calculated at the time of the refrigerator design.
  • the remaining liquid extension pipe refrigerant quantity M C, evaporator refrigerant quantity M D, for the gas extension pipe refrigerant quantity M E is calculated from information input to the device during installation.
  • - high-pressure side refrigerant amount (M A, M B, M C): When designing the upper limit of the condensing temperature (saturation temperature) (for calculating the refrigerant charging amount in most refrigerant requirements)
  • low-pressure side refrigerant amount (M D, M E): condenser refrigerant quantity M A when the evaporation temperature to be set at the time of construction (saturation temperature), n-number as the amount of change of dry condenser is equalized
  • the amount of refrigerant in each of the divided portions can be calculated and used as the sum.
  • the refrigerant quantity M B is the receiver, from the design value of the receiver liquid level height, the liquid refrigerant in the receiver, to calculate the volume of the gas refrigerant, liquid density, respectively, multiplied by the gas density, the liquid refrigerant mass, gas refrigerant mass Is the sum of these.
  • Liquid extension pipe refrigerant quantity M C can be construction worker by entering the pipe length L, it is calculated by multiplying the L to the refrigerant amount per unit length (liquid).
  • Gas extension pipe refrigerant quantity M E can construction worker by entering the pipe length L, is calculated by multiplying the L to the refrigerant amount per unit length (gas).
  • Evaporator refrigerant quantity M D is basically calculated in the same manner as in the condenser, since there is a case where connecting multiple units, the connection number N may be multiplied by the charging amount per one.
  • the refrigeration cycle apparatus according to the third embodiment has the same effects as the refrigeration cycle apparatus according to the first embodiment, and the amount of refrigerant filled from easy-to-understand information such as the extended pipe length and the number of connected indoor units. Is calculated automatically, which is convenient for construction workers.
  • Refrigeration cycle device 1, 101, 201 Refrigeration cycle device, 2, 102, 202 Outdoor unit, 3,203 Indoor unit, 10, 11 Compressor, 20 Indoor heat exchanger, 21 Expansion valve, 22, 41 Fan, 40 Outdoor heat exchanger, 42 receiver, 43 liquid level sensor, 44, 45 pressure sensor, 46 temperature sensor, 50, 150, 250 control device, 51, 151 control unit, 52, 152 storage device, 53, 153 input unit, 204 gas piping, 205 liquid Piping.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Unité externe (2) qui est pourvue d'un compresseur (10), d'un échangeur de chaleur externe (40), d'un récepteur (42), d'un capteur de niveau de liquide (43), d'un dispositif de stockage (52) et d'une unité de commande (51). Le récepteur (42) reçoit, comme fluide frigorigène en phase liquide, un excès de fluide frigorigène résultant du fluide frigorigène qui a été scellé dans un circuit de fluide frigorigène comprenant le compresseur (10), l'échangeur de chaleur extérieur (40), un détendeur (21), et un échangeur de chaleur interne (20). Le capteur de niveau de liquide (43) est configuré pour détecter le niveau de liquide dans le récepteur (42). Le dispositif de stockage (52) stocke la quantité de mélange de fluide frigorigène zéotrope scellé dans le circuit de fluide frigorigène. Une unité d'entrée (53) est utilisée pour entrer la quantité scellée dans le dispositif de stockage (52). L'unité de commande (51) commande le compresseur (10) et le détendeur (21) sur la base de la quantité de fluide frigorigène scellée et du niveau de liquide, et modifie la pression du compresseur (10) sur le côté d'admission en fonction d'un changement du niveau de liquide.
PCT/JP2018/022019 2018-06-08 2018-06-08 Unité externe et dispositif à cycle frigorifique WO2019234914A1 (fr)

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JP2020523953A JP6903233B2 (ja) 2018-06-08 2018-06-08 室外機および冷凍サイクル装置
PCT/JP2018/022019 WO2019234914A1 (fr) 2018-06-08 2018-06-08 Unité externe et dispositif à cycle frigorifique
CN201880093742.XA CN112166290B (zh) 2018-06-08 2018-06-08 室外机以及制冷循环装置

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06101912A (ja) * 1992-08-31 1994-04-12 Hitachi Ltd 冷凍サイクル
JPH08152208A (ja) * 1994-11-25 1996-06-11 Mitsubishi Electric Corp 冷媒循環システムおよび冷凍・空調装置
JPH09113078A (ja) * 1995-10-18 1997-05-02 Idemitsu Kosan Co Ltd 冷媒圧縮熱処理装置の制御装置および制御方法
JPH1068555A (ja) * 1996-08-27 1998-03-10 Mitsubishi Heavy Ind Ltd 冷凍サイクルの循環冷媒組成検出方法並びにその検出方法を用いた冷凍装置
JP2002267232A (ja) * 2001-03-12 2002-09-18 Hitachi Ltd 空気調和機のサービスシステム及びサービス提供装置
JP2008256254A (ja) * 2007-04-04 2008-10-23 Daikin Ind Ltd 冷凍装置および冷媒組成の推定方法
JP2014016138A (ja) * 2012-07-11 2014-01-30 Mitsubishi Heavy Ind Ltd 冷凍・空調機の冷媒充填装置

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5651263A (en) * 1993-10-28 1997-07-29 Hitachi, Ltd. Refrigeration cycle and method of controlling the same
JP4734161B2 (ja) * 2006-04-19 2011-07-27 日立アプライアンス株式会社 冷凍サイクル装置及び空気調和機
US9677799B2 (en) * 2012-07-23 2017-06-13 Mitsubishi Electric Corporation Refrigeration and air-conditioning apparatus, refrigerant leakage detection device, and refrigerant leakage detection method
JP6072311B2 (ja) * 2014-01-30 2017-02-01 三菱電機株式会社 冷凍サイクル装置、空気調和装置、及び、冷凍サイクル装置における循環組成の算出方法

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06101912A (ja) * 1992-08-31 1994-04-12 Hitachi Ltd 冷凍サイクル
JPH08152208A (ja) * 1994-11-25 1996-06-11 Mitsubishi Electric Corp 冷媒循環システムおよび冷凍・空調装置
JPH09113078A (ja) * 1995-10-18 1997-05-02 Idemitsu Kosan Co Ltd 冷媒圧縮熱処理装置の制御装置および制御方法
JPH1068555A (ja) * 1996-08-27 1998-03-10 Mitsubishi Heavy Ind Ltd 冷凍サイクルの循環冷媒組成検出方法並びにその検出方法を用いた冷凍装置
JP2002267232A (ja) * 2001-03-12 2002-09-18 Hitachi Ltd 空気調和機のサービスシステム及びサービス提供装置
JP2008256254A (ja) * 2007-04-04 2008-10-23 Daikin Ind Ltd 冷凍装置および冷媒組成の推定方法
JP2014016138A (ja) * 2012-07-11 2014-01-30 Mitsubishi Heavy Ind Ltd 冷凍・空調機の冷媒充填装置

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