WO2020066001A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

Info

Publication number
WO2020066001A1
WO2020066001A1 PCT/JP2018/036526 JP2018036526W WO2020066001A1 WO 2020066001 A1 WO2020066001 A1 WO 2020066001A1 JP 2018036526 W JP2018036526 W JP 2018036526W WO 2020066001 A1 WO2020066001 A1 WO 2020066001A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
pressure
receiver
liquid level
refrigeration cycle
Prior art date
Application number
PCT/JP2018/036526
Other languages
English (en)
Japanese (ja)
Inventor
亮 築山
野本　宗
悟 梁池
智隆 石川
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 JP2020547864A priority Critical patent/JP6972370B2/ja
Priority to PCT/JP2018/036526 priority patent/WO2020066001A1/fr
Priority to CN201880097320.XA priority patent/CN112752935B/zh
Publication of WO2020066001A1 publication Critical patent/WO2020066001A1/fr

Links

Images

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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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 a refrigeration cycle device, and more particularly to a refrigeration cycle device using a non-azeotropic mixed refrigerant.
  • Patent Document 1 discloses a refrigeration cycle apparatus that can easily and accurately detect the amount of refrigerant in a refrigeration cycle.
  • a liquid level detection pipe provided with a pressure reducing means is provided in a container of a liquid receiver, and this is connected to a low pressure pipe.
  • Temperature detecting means is provided on the outlet side of the pressure reducing means and the low pressure side pipe, and the liquid level of the receiver is detected from the detected refrigerant temperature.
  • the suction port of the liquid level detection pipe is a fixed position.
  • the suction port of the liquid level detection pipe is provided at a position where the refrigerant is significantly insufficient, and it is possible to detect even if the refrigerant has been reduced due to leakage or the like by then. Did not.
  • An object of the present invention is to provide a refrigeration cycle device capable of accurately detecting a shortage of refrigerant regardless of a change in outside air temperature.
  • the present disclosure relates to a refrigeration cycle device using a non-azeotropic mixed refrigerant.
  • the refrigeration cycle device includes a compressor, a first heat exchanger, a receiver, a first expansion device, a second heat exchanger, a compressor, a first heat exchanger, a receiver, a first expansion device, and a second expansion device.
  • a refrigerant circuit that circulates the non-azeotropic mixed refrigerant in the order of the heat exchanger, a bypass pipe that sends the non-azeotropic mixed refrigerant from the receiver to the suction port of the compressor without passing through the first expansion device and the second heat exchanger, and And a second expansion device provided in the bypass pipe.
  • the end of the bypass pipe inserted into the receiver is provided with a refrigerant inlet through which the non-azeotropic mixed refrigerant flows.
  • the opening area of the refrigerant inlet is configured such that when the liquid level of the receiver changes, the amount of the non-azeotropic mixed refrigerant in the gas state flowing into the refrigerant inlet changes.
  • FIG. 2 is a diagram illustrating a configuration of a refrigeration cycle device according to Embodiment 1. It is a figure which shows the detail of a receiver and piping.
  • FIG. 3 is a ph diagram of a refrigeration cycle using a pseudo azeotropic refrigerant.
  • FIG. 3 is a ph diagram of a refrigeration cycle using a non-azeotropic refrigerant.
  • 4 is a flowchart for describing a refrigerant shortage detection process according to the first embodiment. It is the figure which showed several holes provided in the bypass piping of the receiver. It is a graph which shows the relationship between dryness Q and liquid level height H1. 5 is a graph showing a relationship between a condensation temperature and an appropriate liquid level.
  • FIG. 7 is a diagram for explaining a change in the total area of the openings for sucking gas when the liquid level of the refrigerant in the receiver changes in the first example. It is the graph which showed the dryness corresponding to the change of the area of the hole of the gas part in the 1st example. It is the graph which showed the relationship between the entrance dryness of the bypass piping and the exit temperature of the bypass piping in the 1st example. It is a figure which shows the structure of the 2nd example of the suction end part of a bypass piping. It is a figure showing the composition of the 3rd example of the suction end of a bypass pipe.
  • FIG. 3 is a ph diagram for describing a degree of superheat SH.
  • Embodiment 1 FIG.
  • mixed refrigerants in which GWP is reduced by mixing other refrigerants having a lower global warming potential (GWP) with a refrigerant composed of a single component in a refrigerant May be used.
  • the mixed refrigerants there are azeotropic refrigerants and non-azeotropic refrigerants.
  • An azeotropic refrigerant exhibits a constant boiling point when a plurality of components of a refrigerant are mixed at a certain ratio, has the same composition in the gas phase and the liquid phase, and exhibits a phase change as if it were a single component.
  • the azeotropic refrigerant has the same temperature at the same pressure during the two-phase phase change, while the non-azeotropic refrigerant has the characteristic that the temperature changes during the phase change under the same pressure.
  • FIG. 1 is a diagram illustrating a configuration of a refrigeration cycle device according to the first embodiment.
  • This refrigeration cycle apparatus uses a non-azeotropic mixed refrigerant.
  • the connection relation and arrangement of each device in the refrigeration apparatus are shown functionally, and the arrangement in a physical space is not necessarily shown.
  • refrigeration cycle apparatus 1 includes outdoor unit 2 and indoor unit 3.
  • the outdoor unit 2 includes a compressor 10, a condenser 20, a fan 22, a receiver (liquid receiver) 42, and pipes 80 to 84.
  • the outdoor unit 2 further includes a bypass pipe 85, a second expansion device 71, a temperature sensor 73, a first pressure sensor 90 and a second pressure sensor 92, and a control device 100.
  • the second expansion device 71 is, for example, a capillary tube.
  • the indoor unit 3 includes a first expansion device 50, an evaporator 60, a fan 62, and a pipe 83.
  • the first expansion device 50 is, for example, an electronic expansion valve.
  • the indoor unit 3 is connected to the outdoor unit 2 by pipes 82 and 84.
  • the refrigerant circulates in the refrigerant circuit 110 and is bypassed by the bypass pipe 85 without passing through the first expansion device 50 and the evaporator 60.
  • the pipe 80 connects the discharge port of the compressor 10 and the condenser 20.
  • the pipe 81 connects the condenser 20 and the receiver 42.
  • the pipe 82 connects the receiver 42 and the first expansion device 50.
  • the pipe 83 connects the first expansion device 50 and the evaporator 60.
  • the pipe 84 connects the evaporator 60 and the suction port of the compressor 10.
  • the bypass pipe 85 is constituted by bypass pipes 86 and 87.
  • the bypass pipe 86 connects the receiver 42 and the second expansion device 71.
  • the bypass pipe 87 connects the second expansion device 71 and the pipe 84.
  • the compressor 10 sucks the refrigerant from the pipe 84, compresses the sucked refrigerant, and discharges the compressed refrigerant to the pipe 80.
  • the compressor 10 is configured to adjust the rotation speed according to a control signal from the control device 100. By adjusting the operating frequency or the rotation speed of the compressor 10, the circulation amount of the refrigerant is adjusted, and the capacity of the refrigeration cycle apparatus 1 can be adjusted.
  • Various types can be used for the compressor 10, and for example, a scroll type, a rotary type, a screw type, and the like can be used.
  • the condenser 20 condenses the refrigerant discharged from the compressor 10 to the pipe 80.
  • the condensed refrigerant is sent out to the pipe 81.
  • the condenser 20 is configured such that the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 performs heat exchange (radiation) with the outside air. By this heat exchange, the refrigerant is condensed and changes to a liquid phase.
  • the fan 22 supplies the outside air to the condenser 20 where the refrigerant performs heat exchange in the condenser 20. By adjusting the rotation speed of the fan 22, the refrigerant pressure (high-pressure side pressure) on the discharge side of the compressor 10 can be adjusted.
  • the receiver 42 stores the high-pressure liquid refrigerant condensed by the condenser 20.
  • the first expansion device 50 decompresses the refrigerant sent from the receiver 42 to the pipe 82.
  • the depressurized refrigerant is sent to the pipe 83.
  • the evaporator 60 evaporates the refrigerant sent from the first expansion device 50 to the pipe 83.
  • the refrigerant having passed through the evaporator 60 flows to the pipe 84.
  • the evaporator 60 is configured such that the refrigerant decompressed by the first expansion device 50 performs heat exchange (heat absorption) with the air in the indoor unit 3.
  • the refrigerant evaporates by passing through the evaporator 60 to become superheated steam.
  • the fan 62 supplies the air in which the refrigerant performs heat exchange in the evaporator 60 to the evaporator 60.
  • bypass pipes 86 and 87 As a configuration for detecting the shortage of the refrigerant, bypass pipes 86 and 87, a second expansion device 71 provided between the bypass pipes 86 and 87, and a temperature sensor 73 are provided.
  • the bypass pipe 86, the second expansion device 71, and the bypass pipe 87 constitute a bypass flow path that returns a part of the refrigerant that has passed through the condenser 20 to the compressor 10 without passing through the indoor unit 3.
  • the second expansion device 71 is, for example, a capillary tube.
  • the second expansion device 71 is connected between the bypass pipe 86 and the bypass pipe 87, and adjusts the flow rate of the refrigerant flowing through the bypass circuit. As the refrigerant passes through the second expansion device 71, the pressure of the refrigerant decreases.
  • the temperature sensor 73 is provided in the bypass pipe 87.
  • the temperature sensor 73 detects the temperature T1 of the refrigerant that has passed through the second expansion device 71, and outputs the detected value to the control device 100.
  • the temperature sensor 73 is provided inside the bypass pipe 87 to reliably detect the temperature of the refrigerant. The principle and method of refrigerant shortage detection using these will be described later in detail.
  • the first pressure sensor 90 detects the pressure LP of the refrigerant in the pipe 84 and outputs the detected value to the control device 100. That is, the first pressure sensor 90 detects the refrigerant pressure (low pressure side pressure) on the suction side of the compressor 10.
  • the second pressure sensor 92 detects the pressure HP of the refrigerant in the pipe 80 and outputs the detected value to the control device 100. That is, the second pressure sensor 92 detects the refrigerant pressure (high pressure side pressure) on the discharge side of the compressor 10.
  • the control device 100 includes a CPU (Central Processing Unit) 102, a memory 104 (ROM (Read Only Memory) and RAM (Random Access Memory)), and an input / output buffer (not shown) for inputting and outputting various signals. It is comprised including.
  • the CPU 102 executes a program stored in the ROM by expanding the program in the RAM or the like.
  • 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 controls each device of the refrigeration cycle device 1 according to these programs. This control is not limited to processing by software, and processing by dedicated hardware (electronic circuit) is also possible.
  • FIG. 2 is a diagram showing details of the receiver and the piping.
  • gas refrigerant and liquid refrigerant are stored in receiver 42.
  • the liquid refrigerant flows out of the pipe 82 from the bottom of the receiver 42.
  • the end opening of the pipe 82 is provided at a position lower than the end opening of the pipe 81 so that the liquid refrigerant preferentially flows out of the receiver 42 even when the refrigerant mixed with the gas flows in from the pipe 81.
  • the bypass pipe 86 is inserted from the upper part of the receiver 42 toward the inside.
  • the bypass pipe 86 has a plurality of openings on the side surface inside the receiver 42. With such a configuration, the dryness of the refrigerant sucked into the bypass pipe 86 changes depending on the liquid level of the refrigerant in the receiver 42.
  • the lower end of the bypass pipe 86 needs to be provided at a higher position than the pipe 82 in order to prevent the gas refrigerant from flowing out of the pipe 82 due to the shortage of the refrigerant and the performance of the refrigeration cycle being reduced. That is, considering the height based on the bottom surface of the receiver 42, the lower end of the bypass pipe 86 is detected in order to detect the shortage of the refrigerant before the liquid level H1 of the liquid refrigerant falls below the height Hout1 of the outlet pipe. Height Hout2 is higher than Hout1.
  • FIG. 3 is a ph diagram of a refrigeration cycle using a pseudo-azeotropic refrigerant.
  • FIG. 4 is a ph diagram of a refrigeration cycle using a non-azeotropic refrigerant.
  • a pseudo-azeotropic refrigerant exhibits a constant boiling point when a plurality of components of a refrigerant are mixed at a certain ratio, has the same composition in a gas phase and a liquid phase, and exhibits a phase change as if it were a single component.
  • R410A can be mentioned as an example of the pseudo azeotropic refrigerant.
  • the pseudo-azeotropic refrigerant As shown in FIG. 3, in the two-phase region sandwiched between the saturated liquid line and the saturated vapor line, the pseudo-azeotropic refrigerant has a very small slope of the isotherm and can be regarded as zero in design. Therefore, it may be considered that there is no gradient between the temperature of the two-phase region in the condenser and the temperature of the two-phase region in the evaporator.
  • non-azeotropic refrigerants change temperature during phase change under the same pressure.
  • R463A can be mentioned as an example of the non-azeotropic refrigerant.
  • the azeotropic refrigerant has a gradient in the isotherm in the two-phase region sandwiched between the saturated liquid line and the saturated vapor line. Therefore, the temperature of the two-phase region in the condenser and the temperature of the two-phase region in the evaporator change with the degree of dryness even under the same pressure.
  • line segment AB indicates a change in state of the refrigerant when the refrigerant flows through the bypass flow path from point A to point B in FIG.
  • Line segment AB indicates a case where the liquid level is high, that is, the degree of dryness is small
  • line segment A′-B ′ indicates a case where the liquid level is low, that is, a case where the dryness is large.
  • the enthalpy of the refrigerant at point B can be specified by measuring the temperature T1 and pressure LP at point B in FIG. Since the adiabatic expansion is performed in the second expansion device 71, the enthalpy does not change. Therefore, the enthalpy of the point A can be considered to be equal to the enthalpy of the point B. Thus, the enthalpy of the point A can be specified.
  • Dryness is 0 when the position of point A in FIG. 4 is on the saturated liquid line and 1 when it is on the saturated vapor line, and is determined by the position of point A between the saturated liquid line and the saturated vapor line.
  • the dryness at the point A can be obtained from the temperature T1 and the pressures LP and HP. Therefore, it is possible to prepare in advance a map for obtaining the degree of dryness at the point A from the temperature T1, the pressures LP and HP.
  • the shortage of the refrigerant occurs when the initial charge amount of the refrigerant in the refrigerant circuit is insufficient or when the refrigerant leaks after the start of use.
  • FIG. 5 is a flowchart for explaining the refrigerant shortage detection process according to the first embodiment. The process of this flowchart is repeatedly called from the main routine of the control of the refrigeration cycle device to check the refrigerant amount.
  • control device 100 detects temperature T1 and pressure LP at point B, which is the capillary outlet. Subsequently, in Step S2, the control device 100 calculates the enthalpy of the point B.
  • the enthalpy calculated here is equal to the enthalpy of the point A which is the capillary entrance.
  • the pressure HP can be detected in step S3, and the dryness of the point A can be calculated from the enthalpy obtained in step S2.
  • the dryness at the point A may be obtained from the temperature T1, the pressure LP, and the HP using a map prepared in advance.
  • step S4 the control device 100 calculates the receiver liquid level H1 from the dryness at the point A.
  • FIG. 6 is a diagram showing a plurality of holes provided in the bypass pipe of the receiver.
  • FIG. 7 is a graph showing the relationship between the dryness Q and the liquid level H1. As the liquid level increases, the holes are closed by the liquid refrigerant, so that the gas refrigerant is less likely to be sucked, and the dryness Q decreases. Conversely, as the liquid level becomes lower, the number of holes for sucking the gas refrigerant increases, so that the dryness Q increases.
  • the relationship between the dryness Q and the liquid level H1 as shown in FIG. 7 can be obtained in advance and made into a map.
  • control device 100 calculates an appropriate liquid level H2 with respect to the condensation temperature in step S5.
  • FIG. 8 is a graph showing the relationship between the condensation temperature and the appropriate liquid level.
  • the condensation temperature can be determined by measuring the pressure HP.
  • the horizontal axis in FIG. 8 may be replaced by the pressure HP instead of the condensation temperature.
  • the condensing temperature t is a condensing temperature when the condenser 20 exchanges heat with the outside air, and varies depending on the outside air temperature, the rotation of the fan 22, and the operating frequency of the compressor 10.
  • the reference height for comparing the current liquid level H1 in the receiver 42 obtained in FIG. 7 needs to be changed according to the outside air temperature. There is. In the present embodiment, since the reference value is changed according to FIG. 7, even if the outside air temperature changes, it can be accurately determined that the refrigerant is insufficient for an appropriate amount.
  • step S5 When the calculation of the liquid level H2 when the refrigerant amount is appropriate is completed in step S5, the control device 100 determines in step S6 whether the current liquid level H1 is lower than the liquid level H2. I do.
  • control device 100 determines in step S7 that the refrigerant is insufficient, and outputs an alarm in step S8.
  • the alarm is issued by, for example, turning on a lamp or an LED (Light Emitting Diode), or displaying a shortage of refrigerant on a liquid crystal display.
  • control device 100 derives from temperature T1 detected by temperature sensor 73, pressure LP detected by first pressure sensor 90, and pressure HP detected by second pressure sensor 92. When the first liquid level height H1 is lower than the second liquid level height H2 corresponding to the pressure detected by the second pressure sensor 92, it is determined that the amount of non-azeotropic mixed refrigerant charged is insufficient. I do.
  • control device 100 returns to the main routine in step S9 without performing the processes in steps S7 and S8.
  • step S6 of FIG. 5 the liquid level height H1 and the liquid level height H2 are simply compared. However, if the difference between the liquid level height H1 and the liquid level height H2 is calculated, the difference is large. Thus, the shortage of the refrigerant can be notified.
  • the control device 100 determines the first liquid level H1 derived from the temperature T1 detected by the temperature sensor 73, the pressure LP detected by the first pressure sensor 90, and the pressure HP detected by the second pressure sensor 92. And the second liquid level height H2 corresponding to the pressure HP detected by the second pressure sensor 92, and determines the insufficient amount of the non-azeotropic refrigerant mixture.
  • ⁇ H H2 ⁇ H1
  • ⁇ H is calculated in step S6
  • the shortage corresponding to ⁇ H is read from the map
  • the user may be notified of the shortage amount instead of the alarm or together with the alarm.
  • the shortage amount may be represented by a numerical value, or may be represented in a stepwise manner by the number of blinks or the color of the LED.
  • FIG. 9 is a diagram showing a configuration of a first example of the suction end of the bypass pipe.
  • a plurality of openings D1 to D5 are provided at the end of the bypass pipe 86.
  • the openings D1 to D5 are arranged at equal intervals L along the flow direction in which the refrigerant is sucked.
  • the opening D5 is provided at the closed end of the bypass pipe, the end may be completely closed and provided on the side of the pipe in the same manner as the openings D1 to D4.
  • FIG. 10 is a diagram for explaining a change in the total area of the gas suction opening when the liquid level of the refrigerant in the receiver changes in the first example.
  • FIG. 10 shows the total area ratio of the openings D1 to D5 in the gas portion above the liquid surface when the total area of the openings D1 to D5 is 1.
  • the area ratio is zero.
  • the area ratio is 0.6.
  • the area ratio is 0.76.
  • the area ratio is 0.88.
  • the area ratio is 0.95.
  • the area ratio is 1.0.
  • the sizes of the openings D1 to D5 are determined so that the total area of the openings located in the gas part changes in this way. The reason why the sizes of the openings D1 to D5 are determined as described above will be described below.
  • FIG. 11 is a graph showing the dryness corresponding to the change in the area of the gas hole in the first example.
  • the horizontal axis indicates the total area ratio of the openings located in the gas part
  • the vertical axis indicates the dryness of the refrigerant sucked from the bypass pipe 86 at the inlet of the second expansion device 71.
  • FIG. 12 is a graph showing the relationship between the inlet dryness of the bypass pipe and the outlet temperature of the bypass pipe in the first example.
  • the dryness of the inlet and the outlet temperature (temperature T1) of the second expansion device 71 have a substantially linear relationship.
  • the inlet dryness with respect to the total opening area of the gas portion shows a shape like a quadratic curve, and is not a straight line. Therefore, if the openings D1 to D5 are the same size, the inlet dryness does not change much when the total opening area ratio is small, and the amount of change increases as the total opening area ratio approaches 1. In this case, the amount of change in the degree of dryness and the amount of change in the temperature T1 change depending on the position of the liquid surface, and therefore, it is difficult to use the device for detecting the amount of refrigerant.
  • the inlet dryness is divided into five equal parts, and the areas of the openings D1 to D5 are determined so as to obtain the ratio of the total sectional area of the openings corresponding to each dryness.
  • the change in the temperature T1 can linearly indicate the change in the liquid level, which is convenient for detecting the shortage of the refrigerant.
  • FIG. 13 is a diagram showing a configuration of a second example of the suction end of the bypass pipe.
  • a slit whose height direction is the longitudinal direction may be provided on the side surface of the end of the bypass pipe 86.
  • the change in the temperature T1 is linear.
  • the change in the liquid level can be represented as follows.
  • FIG. 14 is a diagram showing the configuration of a third example of the suction end of the bypass pipe.
  • a plurality of pipes having different suction ports may be provided.
  • the temperature becomes The change in T1 can linearly represent the change in liquid level.
  • FIG. 15 is a diagram showing a configuration of a fourth example in which the end of the bypass pipe is inserted into the receiver from below.
  • FIG. 16 is a diagram showing the configuration of the suction end of the bypass pipe of the fourth example.
  • a plurality of openings D1 to D5 are provided at the end of the bypass pipe 86 as shown in FIG.
  • the openings D1 to D5 are arranged at equal intervals L along the flow direction in which the refrigerant is sucked.
  • the opening D1 is provided on the tip side (upper side), and the opening D5 is provided on the lower side.
  • FIG. 17 is a diagram for describing a change in the total area of the gas suction opening when the liquid level of the refrigerant in the receiver changes in the fourth example. Assuming that the total area of the openings D1 to D5 is 1, the area ratio of the openings D1 to D5 located in the gas portion above the liquid level is described.
  • the area ratio is zero.
  • the area ratio is 0.6.
  • the area ratio is 0.76.
  • the area ratio is 0.88.
  • the area ratio is 0.95.
  • the area ratio is 1.0.
  • the sizes of the openings D1 to D5 are determined so that the total area of the openings located in the gas part changes in this way.
  • FIG. 18 is a graph showing the dryness corresponding to the change in the area of the hole in the gas part in the fourth example.
  • the horizontal axis indicates the total area ratio of the openings located in the gas part
  • the vertical axis indicates the dryness of the refrigerant sucked from the bypass pipe 86 at the entrance of the second expansion device 71.
  • the dryness at the inlet of the second expansion device 71 and the temperature T1 have a substantially linear relationship. Therefore, as shown on the vertical axis of FIG. 18, the inlet dryness is divided into five equal parts, and the areas of the openings D1 to D5 are determined so as to obtain the ratio of the total cross-sectional area of the openings corresponding to each dryness.
  • the change in the temperature T1 can linearly represent the change in the liquid level, which is convenient for detecting the shortage of the refrigerant.
  • a slit may be provided on the side surface as in the second example, or a plurality of suction port heights may be formed as in the third example.
  • a different branch pipe may be provided.
  • the refrigeration cycle apparatus 1 includes a compressor 10, a condenser 20 as a first heat exchanger, a receiver 42, a first expansion device 50, an evaporator 60 as a second heat exchanger, and pipes 80 to 84. , A bypass pipe 85, and a second expansion device 71 provided in the bypass pipe 85.
  • the pipes 80 to 84 constitute a refrigerant circuit 110 for circulating a non-azeotropic mixed refrigerant in the order of the compressor 10, the first heat exchanger, the receiver 42, the first expansion device 50, and the second heat exchanger.
  • the bypass pipe 85 sends the non-azeotropic mixed refrigerant from the receiver 42 to the suction port of the compressor 10 without passing through the first expansion device 50 and the second heat exchanger.
  • a refrigerant inlet D is provided at an end of the bypass pipe 85 inserted into the receiver 42.
  • the refrigerant inlet D is configured such that when the liquid level of the receiver 42 changes, the opening area for sucking the non-azeotropic mixed refrigerant in the gas state changes.
  • the refrigerant inlet D is configured such that, when the liquid level of the receiver 42 changes, the opening area changes in a range from zero to the cross-sectional area of the bypass pipe.
  • the liquid level H1 can be obtained from the dryness Q based on the relationship shown in FIG.
  • the end of the bypass pipe 85 inserted into the receiver 42 serves as a refrigerant inlet in the direction in which the liquid level of the receiver 42 changes.
  • a plurality of openings D1 to D5 provided at different positions are provided.
  • a slit S is provided at the end of the bypass pipe 85 inserted into the receiver 42, as a refrigerant inlet, in which the direction of change in the liquid level of the receiver 42 is the longitudinal direction.
  • the refrigeration cycle apparatus 1 includes a temperature sensor 73 that detects a temperature T1 of the non-azeotropic mixed refrigerant that has passed through the second expansion device 71, and a pressure of the non-azeotropic mixed refrigerant that has passed through the second expansion device 71.
  • the control device 100 further includes a control device 100 that determines whether the amount of the non-azeotropic mixed refrigerant to be charged is appropriate based on the pressure LP detected by the pressure sensor 90 and the pressure HP detected by the second pressure sensor 92.
  • Embodiment 2 The refrigerant shortage detection method described in the first embodiment utilizes a point in which a non-azeotropic refrigerant has a temperature gradient in a two-phase state. Therefore, it is assumed that the outlet of the second expansion device 71 is in a two-phase state. However, when the dryness of the inlet of the second expansion device 71 approaches 1, the refrigerant at the outlet of the second expansion device 71 may be in a gas state.
  • a refrigeration cycle device that can detect the shortage of the refrigerant including this case will be described.
  • the main configuration of the refrigeration cycle apparatus is as shown in FIG. 1, and thus description thereof will not be repeated.
  • FIG. 19 is a flowchart for explaining the processing of the refrigerant shortage detection according to the second embodiment. The process of this flowchart is repeatedly called from the main routine of the control of the refrigeration cycle device to check the refrigerant amount.
  • step S11 it is determined whether or not the degree of superheat SH of the refrigerant at point B is greater than zero. If it is determined in step S11 that SH> 0, the process proceeds to step S15, and the control device 100 determines that the refrigerant is insufficient, and outputs a warning in step S16.
  • FIG. 20 is a ph diagram for describing the degree of superheat SH.
  • the point B ′ is located in the gas region on the left side of the saturated steam line LG. Since it is located, the refrigerant is in a gaseous state, and the method described in the first embodiment cannot detect refrigerant shortage.
  • step S11 in FIG. 19 It is possible to determine whether SH> 0 in step S11 in FIG. 19 based on the pressure LP and the temperature T1.
  • a map indicating the relationship between the pressure LP and the saturated gas temperature Ts is prepared in advance. First, a saturated gas temperature Ts corresponding to the pressure LP is obtained from a map. If the temperature T1 is higher than the saturated gas temperature Ts, SH> 0, and if the temperature T1 is equal to or lower than the saturated gas temperature Ts, it can be determined that the refrigerant is not in an overheated state.
  • step S11 if SH> 0 is not satisfied, a liquid level height H1 is calculated in step S12, and a process of comparing the liquid level height H1 with the proper height H2 is performed in step S13. Details of the processing in steps S12 and S13 have been described in steps S1 to S5 in FIG. 5, and thus description thereof will not be repeated here.
  • step S14 it is determined in step S14 that the refrigerant amount is appropriate, and the process returns to the main routine. On the other hand, if H1> H2 is not satisfied in step S13 (NO in S13), it is determined that the refrigerant is insufficient in step S13, and an alarm is output in step S16.
  • the control device 100 controls the temperature T1 detected by the temperature sensor 73, the pressure LP detected by the first pressure sensor 90, and the second pressure
  • the first liquid level height H1 derived from the pressure HP detected by the sensor 92 is lower than the second liquid level height H2 corresponding to the pressure detected by the second pressure sensor 92, the non-azeotropic mixed refrigerant Is determined to be insufficient.
  • the control device 100 determines the superheat degree SH of the non-azeotropic mixed refrigerant determined based on the temperature T1 detected by the temperature sensor 73 and the pressure LP detected by the first pressure sensor 90.
  • the refrigeration cycle apparatus according to the second embodiment has the same effect as the refrigeration cycle apparatus according to the first embodiment, and also has a shortage of refrigerant even when the refrigerant in the bypass pipe is almost gaseous. Can be detected.
  • 1 refrigeration cycle device 2 outdoor unit, 3 indoor unit, 10 compressor, 20 condenser, 22,62 fan, 42 receiver, 50,71 expansion device, 60 evaporator, 73 temperature sensor, 80,81,82,83 , 84, 85 pipe, 86, 87 bypass pipe, 90, 92 pressure sensor, 100 control device, 104 memory, 110 refrigerant circuit.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un dispositif à cycle frigorifique (1) comprenant un compresseur (10), un condenseur (20) qui présente un premier échangeur de chaleur, un récepteur (42), un premier dispositif de détente (50), un évaporateur (60) qui est un second échangeur de chaleur, des conduites (80-84), une conduite de dérivation (85), et un second dispositif de détente (71) qui est disposé dans la conduite de dérivation (85). Les conduites (80-84) constituent un circuit de fluide frigorigène (110) pour faire circuler un mélange de fluide frigorigène non azéotrope à travers, dans l'ordre, le compresseur (10), le premier échangeur de chaleur, le récepteur (42), le premier dispositif de détente (50), et le second échangeur de chaleur. La conduite de dérivation (85) envoie le mélange de fluide frigorigène non azéotrope du récepteur (42) à l'orifice d'entrée du compresseur (10) sans passer à travers le premier dispositif de détente (50) et le second échangeur de chaleur. L'extrémité de la conduite de dérivation (85) insérée dans le récepteur (42) est pourvue d'une entrée de fluide frigorigène (D). L'entrée de fluide frigorigène (D) est conçue de telle sorte que la surface d'une ouverture pour laisser entrer le mélange de fluide frigorigène non azéotrope à l'état gazeux est modifiée lorsque le niveau de liquide dans le récepteur (42) change.
PCT/JP2018/036526 2018-09-28 2018-09-28 Dispositif à cycle frigorifique WO2020066001A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2020547864A JP6972370B2 (ja) 2018-09-28 2018-09-28 冷凍サイクル装置
PCT/JP2018/036526 WO2020066001A1 (fr) 2018-09-28 2018-09-28 Dispositif à cycle frigorifique
CN201880097320.XA CN112752935B (zh) 2018-09-28 2018-09-28 制冷循环装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/036526 WO2020066001A1 (fr) 2018-09-28 2018-09-28 Dispositif à cycle frigorifique

Publications (1)

Publication Number Publication Date
WO2020066001A1 true WO2020066001A1 (fr) 2020-04-02

Family

ID=69950400

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2018/036526 WO2020066001A1 (fr) 2018-09-28 2018-09-28 Dispositif à cycle frigorifique

Country Status (3)

Country Link
JP (1) JP6972370B2 (fr)
CN (1) CN112752935B (fr)
WO (1) WO2020066001A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022210794A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif de pompe à chaleur

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5516879U (fr) * 1978-07-20 1980-02-02
JPH0634221A (ja) * 1992-07-16 1994-02-08 Daikin Ind Ltd 空気調和装置
JP2002162086A (ja) * 2000-11-24 2002-06-07 Hitachi Ltd 空気調和機
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
JP2009210151A (ja) * 2008-02-29 2009-09-17 Daikin Ind Ltd 空気調和装置および冷媒量判定方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3339302B2 (ja) * 1996-04-26 2002-10-28 三菱電機株式会社 アキュムレータ
JP2008057807A (ja) * 2006-08-29 2008-03-13 Samsung Electronics Co Ltd 冷凍サイクル及びそれを用いた空気調和機、冷蔵庫
CN201852382U (zh) * 2010-11-16 2011-06-01 Tcl空调器(中山)有限公司 一种空调器的贮液筒结构
US10126026B2 (en) * 2014-10-16 2018-11-13 Mitsubishi Electric Corporation Refrigeration cycle apparatus
CN106052177A (zh) * 2016-04-29 2016-10-26 广东美的制冷设备有限公司 单冷型空调器及其控制方法
CN105972822B (zh) * 2016-06-14 2019-04-02 珠海格力电器股份有限公司 热泵热水器和热泵热水器的调节方法
CN106225280A (zh) * 2016-08-25 2016-12-14 赵向辉 一种制冷或热泵系统以及一种压缩冷凝机组
CN106482376A (zh) * 2016-09-10 2017-03-08 赵向辉 制冷或热泵系统及其冷媒循环量调节方法

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5516879U (fr) * 1978-07-20 1980-02-02
JPH0634221A (ja) * 1992-07-16 1994-02-08 Daikin Ind Ltd 空気調和装置
JP2002162086A (ja) * 2000-11-24 2002-06-07 Hitachi Ltd 空気調和機
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
JP2009210151A (ja) * 2008-02-29 2009-09-17 Daikin Ind Ltd 空気調和装置および冷媒量判定方法

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022210794A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif de pompe à chaleur

Also Published As

Publication number Publication date
JP6972370B2 (ja) 2021-11-24
CN112752935A (zh) 2021-05-04
CN112752935B (zh) 2022-08-09
JPWO2020066001A1 (ja) 2021-08-30

Similar Documents

Publication Publication Date Title
US6247320B1 (en) Refrigerating and air-conditioning apparatus and method of determining refrigerant composition of refrigerating and air-conditioning apparatus
US20180058740A1 (en) Refrigeration cycle apparatus
JP6902390B2 (ja) 冷凍サイクル装置
US10684051B2 (en) Refrigeration cycle apparatus determining refrigerant condenser amount
JP2019011899A (ja) 空気調和装置
JP2943613B2 (ja) 非共沸混合冷媒を用いた冷凍空調装置
JP5487831B2 (ja) 漏洩診断方法、及び漏洩診断装置
WO2020066001A1 (fr) Dispositif à cycle frigorifique
JP7154388B2 (ja) 室外機及びそれを備える冷凍サイクル装置
JP7282157B2 (ja) 室外機及びそれを備える冷凍サイクル装置
JP2948105B2 (ja) 非共沸混合冷媒を用いた冷凍空調装置
CN112739961B (zh) 制冷循环装置的室外机、制冷循环装置以及空调装置
US20200348037A1 (en) Air conditioner system and control method thereof
WO2021192275A1 (fr) Unité extérieure et dispositif à cycle de réfrigération équipé de cette dernière
US20220235982A1 (en) Refrigeration cycle apparatus
CN112714854B (zh) 制冷循环装置
WO2024047954A1 (fr) Appareil à cycle de réfrigération et climatiseur
CN112714852B (zh) 制冷循环装置的室外机、制冷循环装置以及空调装置
WO2024047832A1 (fr) Dispositif à cycle de réfrigération et dispositif de climatisation
WO2024009394A1 (fr) Climatiseur et procédé de détection de fuite de fluide frigorigène
CN115667820A (zh) 冷热源单元、制冷循环装置以及制冷机

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18935264

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2020547864

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18935264

Country of ref document: EP

Kind code of ref document: A1