EP4071425A1 - Ausseneinheit und kühlzyklusvorrichtung - Google Patents

Ausseneinheit und kühlzyklusvorrichtung Download PDF

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Publication number
EP4071425A1
EP4071425A1 EP19955082.3A EP19955082A EP4071425A1 EP 4071425 A1 EP4071425 A1 EP 4071425A1 EP 19955082 A EP19955082 A EP 19955082A EP 4071425 A1 EP4071425 A1 EP 4071425A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
channel
outdoor unit
compressor
condenser
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.)
Pending
Application number
EP19955082.3A
Other languages
English (en)
French (fr)
Other versions
EP4071425A4 (de
Inventor
Ryo TSUKIYAMA
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
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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
Publication of EP4071425A1 publication Critical patent/EP4071425A1/de
Publication of EP4071425A4 publication Critical patent/EP4071425A4/de
Pending 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • 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
    • 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
    • F25B2400/01—Heaters
    • 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
    • F25B2500/24—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
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F25B2600/0253—Compressor control by controlling speed with variable speed
    • 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
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2101—Temperatures in a bypass

Definitions

  • the present disclosure relates to an outdoor unit and a refrigeration cycle apparatus.
  • a refrigeration apparatus comprising a unit that uses "temperature efficiency,” which is a value obtained by dividing a degree of supercooling of refrigerant at an outlet of a subcooler by a maximum temperature difference of the subcooler, to determine an amount of refrigerant introduced in a refrigerant circuit.
  • temperature efficiency is a value obtained by dividing a degree of supercooling of refrigerant at an outlet of a subcooler by a maximum temperature difference of the subcooler, to determine an amount of refrigerant introduced in a refrigerant circuit.
  • the method described in International Publication No. 2016/135904 may be unable to sense that the amount of refrigerant is decreased until the refrigerant is severely short after the amount of the refrigerant starts to decrease.
  • An object of the present disclosure is to provide an outdoor unit and a refrigeration cycle apparatus capable of detecting a shortage of refrigerant at an early stage.
  • the present disclosure relates to an outdoor unit of a refrigeration cycle apparatus, that has a normal mode and a refrigerant shortage sensing mode and is configured to be connected to a load device including an expansion device and an evaporator.
  • the outdoor unit includes: a first channel configured to form a circulation channel allowing refrigerant to circulate by being connected to the load device; a compressor and a condenser disposed along the first channel; a second channel branched from a branching point of the first channel downstream of the condenser in a direction in which the refrigerant circulates, and configured to return the refrigerant that has passed through the condenser to the compressor; a gas-liquid separation structure provided at the branching point; a flow rate regulation device disposed along the second channel and following the branching point, and a refrigerant heating device disposed along the second channel and following the flow rate regulation device; a dryness increasing device configured to increase a dryness of the refrigerant that has passed through the condenser in the ref
  • the presently disclosed outdoor unit that has a refrigerant shortage sensing mode to increase dryness of refrigerant that passes through a bypass channel to be larger than in a normal operation can detect a shortage of the refrigerant at an early stage.
  • Fig. 1 is a diagram showing a configuration of a refrigeration cycle apparatus 1 according to a first embodiment.
  • refrigeration cycle apparatus 1 comprises an outdoor unit 2, a load device 3, and extension pipes 84 and 88.
  • Outdoor unit 2 of refrigeration cycle apparatus 1 is configured to be connected to load device 3 by extension pipes 84 and 88.
  • Outdoor unit 2 includes a compressor 10, a condenser 20, a liquid receiver (a receiver) 30, and pipes 80 to 83 and 89.
  • Liquid receiver 30 is disposed between pipe 82 and condenser 20 and configured to store refrigerant.
  • a channel F1 extending from compressor 10 via condenser 20 and liquid receiver 30 to a port for connection to load device 3 is configured to form a circulation channel together with load device 3 to allow the refrigerant to circulate.
  • this circulation channel will also be referred to as a "main circuit" of the refrigeration cycle.
  • Load device 3 includes an expansion device 50, an evaporator 60, and pipes 85, 86 and 87.
  • Expansion device 50 is, for example, a thermal expansion valve controlled independently of outdoor unit 2.
  • Compressor 10 compresses refrigerant sucked from pipe 89 and discharges the compressed refrigerant to pipe 80.
  • Compressor 10 has a suction port G1 and a discharging port G2.
  • Compressor 10 is configured to suck through suction port G1 refrigerant having passed through evaporator 60 and discharge the refrigerant through discharging port G2 toward condenser 20.
  • Outdoor unit 2 further includes an erected pipe 71, a pipe 72, a flow rate regulation device 73, a pipe 74, and a refrigerant heating device 75.
  • Pipe 72 branches from pipe 82 connected to an outlet of liquid receiver 30 on the circulation channel and is connected to one end of flow rate regulation device 73.
  • Pipe 74 interconnects the other end of flow rate regulation device 73 and pipe 89.
  • Refrigerant heating device 75 is configured to heat refrigerant having passed through flow rate regulation device 73.
  • Refrigerant heating device 75 can for example be an electric heater.
  • flow rate regulation device 73 for example, a capillary tube may be typically used, any device such as an orifice may be used insofar as it can reduce a channel in cross section and thus cause a pressure difference. Further, an expansion valve may be used as flow rate regulation device 73.
  • a second channel F2 that branches from the main circuit and feeds refrigerant to compressor 10 via flow rate regulation device 73 will be referred to as a "bypass channel.”
  • the bypass channel is branched from a portion at which erected pipe 71 is connected to pipe 82 connected to the outlet of liquid receiver 30.
  • the bypass channel may not be connected to the suction port of compressor 10 and instead be connected to the intermediate pressure port.
  • Compressor 10 is configured to adjust rotational speed in response to a control signal received from a control device 100. By adjusting compressor 10 in rotational speed, an amount of refrigerant circulated is adjusted, and capacity of refrigeration cycle apparatus 1 for refrigeration can be adjusted.
  • Compressor 10 may be of various types, such as a scroll type, a rotary type, or a screw type.
  • Condenser 20 condenses refrigerant discharged from compressor 10 to pipe 80 and passes the condensed refrigerant to pipe 81.
  • Condenser 20 is configured such that high-temperature and high-pressure gaseous refrigerant discharged from compressor 10 exchanges heat with external air. The heat exchange allows the refrigerant to radiate heat, condense, and alter to liquid phase.
  • Fan 22 supplies condenser 20 with external air with which refrigerant exchanges heat in condenser 20. Adjusting fan 22 in rotational speed can adjust pressure of refrigerant on the discharging side of compressor 10.
  • Outdoor unit 2 further includes pressure sensors 110 and 111, temperature sensors 120, 121 and 122, and control device 100 configured to control outdoor unit 2.
  • Pressure sensor 110 senses a pressure PL of refrigerant sucked into compressor 10 and outputs the sensed value to control device 100.
  • Pressure sensor 111 senses a pressure PH of refrigerant discharged from compressor 10 and outputs the sensed value to control device 100.
  • Temperature sensor 120 senses a temperature TA of external air sent to condenser 20 and outputs the sensed value to control device 100.
  • Temperature sensor 121 senses a temperature TC of refrigerant in pipe 81 at the outlet of condenser 20 and outputs the sensed value to control device 100.
  • Temperature sensor 122 senses a temperature T1 of refrigerant having passed through flow rate regulation device 73 and thereafter heated by refrigerant heating device 75, and outputs the sensed value to control device 100.
  • 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 and outputting various signals, and the like.
  • CPU 102 loads a program that is stored in the ROM into a RAM or the like and executes the program.
  • the program stored in the ROM is a program describing a processing procedure for control device 100.
  • Control device 100 controls each device in outdoor unit 2 in accordance with these programs. This control is not limited to processing by software, and processing by dedicated hardware (electronic circuity) is also possible.
  • a bypass channel from an outlet of liquid receiver 30 serving as a high-pressure section to a suction inlet of compressor 10 serving as a low-pressure section.
  • Flow rate regulation device 73 and refrigerant heating device 75 are disposed along the bypass channel.
  • Temperature sensor 122, and pressure sensor 110 for sensing a low-pressure saturation temperature are provided at a portion at which refrigerant having passed through refrigerant heating device 75 arrives.
  • the low-pressure saturation temperature may be temperature measured at the outlet of flow rate regulation device 73.
  • a gas-liquid separation mechanism is provided at a branching point BP1 of the bypass channel.
  • Fig. 2 is a diagram for illustrating a state in which gas-liquid separation cannot be done in the gas-liquid separation mechanism.
  • Fig. 3 is a diagram for illustrating a state in which gas-liquid separation can be done in the gas-liquid separation mechanism.
  • the gas-liquid separation mechanism is configured by erected pipe 71 erected from pipe 82, which is a liquid pipe, in a direction opposite to gravity.
  • Fig. 4 is a Mollier diagram representing a refrigeration cycle when refrigerant has an appropriate amount.
  • points A, B and C correspond to points A, B and C indicated in Fig. 1 .
  • refrigerant at the outlet of liquid receiver 30 has a state on a line of saturated liquid such as point A indicated in Fig. 4 . That is, the inlet of the bypass channel is in a liquid state (point A).
  • the bypass passage provides passage at a flow rate corresponding to a differential pressure determined by expansion device 50 and evaporator 60 of the main circuit.
  • pipe 74 passes a large amount of liquid refrigerant, and when the refrigerant is heated and the point moves rightward, it does not exceed a saturated gas line, and the refrigerant's temperature stays at the saturation temperature and does not change.
  • Fig. 5 is a Mollier diagram representing a refrigeration cycle when refrigerant is short in amount.
  • refrigerant at point A increases in dryness. Therefore, refrigerant at point A in Fig. 1 separated by the gas-liquid separation mechanism has a state on the Mollier diagram, as indicated in Fig. 5 by a point A'.
  • flow rate regulation device 73 decompresses the refrigerant, the refrigerant's state changes from point A' to a point B'.
  • refrigerant heating device 75 heats the refrigerant the refrigerant's state changes from point B' to a point C'.
  • pipe 74 does not pass liquid refrigerant, and when the refrigerant in the pipe is heated, the point moves rightward and exceeds the saturated gas line. Since the heat is absorbed by the refrigerant as sensible heat, the refrigerant's temperature rises to be higher than the saturation temperature and the refrigerant thus has a degree of superheat SH > 0, and it can thus be determined that the refrigerant is short.
  • the refrigerant's temperature corresponding to the measured pressure i.e., saturation temperature
  • a conversion table indicating a correlation between the pressure and the saturation temperature is stored in advance in memory 104 of control device 100.
  • Control device 100 obtains a saturation temperature corresponding to pressure PL from the conversion table, and calculates a difference from temperature T1 actually measured by a temperature sensor.
  • Fig. 6 is a flowchart for controlling a fan in rotational speed in a normal operation.
  • the rotational speed of fan 22 is determined so that each device operates efficiently. For example, it is determined such that a difference between temperature TC representing condensation temperature and external air's temperature is set to be 10°C.
  • a target temperature is set to a value obtained by adding ⁇ °C to external air's temperature TA as measured with temperature sensor 120. Temperature ⁇ °C is set to a temperature at which condenser 20 provides efficient heat exchange, and it is for example 10°C.
  • condensation temperature TC is measured by temperature sensor 121, and condensation temperature TC as measured is compared with the target temperature. For TC > the target temperature (YES in S2), control device 100 increases the rotational speed of fan 22 in step S3 to decrease temperature TC. For TC ⁇ the target temperature (YES in S4), control device 100 decreases the rotational speed of fan 22 in step S5 to increase condensation temperature TC.
  • control device 100 When condensation temperature TC matches the target temperature (NO in S2 and NO in S4), control device 100 does not change and thus maintains the current rotational speed of fan 22. In order to avoid frequently changing the rotational speed of fan 22, a difference may be provided between the target temperatures in steps S2 and S4 to provide hysteresis.
  • An amount of liquid refrigerant held in liquid receiver 30 varies depending on the operating state of the refrigeration cycle apparatus.
  • the amount of refrigerant should be a sufficient amount of an extent such that liquid remains in liquid receiver 30 even in an operating state in which liquid receiver 30 holds a minimal amount of liquid.
  • the operating state in which the receiver holds a minimal amount of liquid is a state in which condensation temperature TC rises to be high (a state in which the high-pressure section has pressure increased as it is affected by external air's temperature, the fan's rotational speed, and the like).
  • refrigerant in the main circuit increases in density and decreases in volume.
  • Liquid refrigerant flows out of liquid receiver 30 toward the circulation circuit by the amount corresponding to the reduction in volume of the refrigerant in the main circuit, and accordingly, liquid receiver 30 has a reduced amount of liquid.
  • dryness at the outlet of the liquid receiver provided with the gas-liquid separation mechanism is increased to be larger than in the normal operation to facilitate a refrigerant shortage sensing unit provided along the bypass channel to sense that refrigerant is short.
  • Fig. 7 is a flowchart for control in the refrigerant shortage sensing mode.
  • the refrigerant shortage sensing mode is periodically run by a timer or the like, for example, once a day or once for several days.
  • control device 100 sets the operating frequency of compressor 10 to a predetermined fixed frequency. Note that in the configuration in which an injection channel is provided as in the second embodiment, the expansion valve of the injection channel also has a fixed degree of opening.
  • control device 100 sets the rotational speed of fan 22 to be equal to or lower than a minimum rotational speed that can be assumed in the normal operation. For example, fan 22 may be stopped from rotating. As a result, condenser 20 exchanges heat with external air less efficiently and thus less likely to condense refrigerant. Then, dryness at the outlet of liquid receiver 30 provided with the gas-liquid separation mechanism increases to be larger than in the normal operation. In other words, refrigerant has a larger ratio of gaseous refrigerant than in the normal operation.
  • control device 100 senses whether refrigerant is short based on whether there is degree of superheat SH at the outlet of the refrigerant heating device (or point C).
  • Fig. 8 is a diagram representing a relationship between the rotational speed of the fan, the amount of refrigerant, and the dryness of the refrigerant.
  • an amount of refrigerant which is 100% indicates an amount introduced as defined to be neither excessive nor insufficient in design, and it is assumed that a difference from 100% is an amount of a shortage.
  • the apparatus as originally installed, has refrigerant introduced in an amount with a margin, and the refrigerant may have an amount of 110% for example. And when the refrigerant leaks and has an amount decreased to be less than 100%, it is determined that the refrigerant is short.
  • Fig. 8 shows that, for refrigerant having an amount of 95%, gas-liquid separation cannot be done when the fan's rotational speed is reduced to 25%. For refrigerant having an amount of 85% gas-liquid separation cannot be done when the fan's rotational speed is reduced to 40%, and for refrigerant having an amount of 80% gas-liquid separation cannot be done when the fan's rotational speed is reduced to 60%.
  • the refrigerant shortage sensing mode ends, and the normal operation is performed, as controlled as shown in Fig. 6 .
  • control device 100 when the refrigerant is short (YES in S13), in the present embodiment, control device 100 further senses an amount of refrigerant in step S14, and in step S15 notifies the user of how much the refrigerant is short. Control device 100 causes notification device 101 to output an alarm indicating that the refrigerant is short.
  • Notification device 101 is for example a display device such as a liquid crystal display, a warning lamp, or the like, and may be a device that transmits a warning signal to an external device via a communication line.
  • control device 100 increases dryness at the outlet of condenser 20 and increases an amount of refrigerant circulated through the main circuit so that the receiver is close to an empty state, and thereafter, control device 100 checks degree of superheat SH at point C. By operating under a condition severer than a condition applied for normal use, whether refrigerant is short is easily determined based on degree of superheat SH.
  • step S14 to what level the refrigerant is reduced in amount is examined and used for maintenance and inspection of the refrigeration cycle apparatus.
  • a result of notification allows the user to consider whether to stop the refrigeration cycle apparatus, when to repair leakage of refrigerant or to supplement shortage of refrigerant, and the like.
  • control device 100 may notify a user or a service provider of emergency or an amount to be additionally sealed.
  • Fig. 9 is a flowchart of details of a process (S14) for sensing an amount of refrigerant.
  • control device 100 gradually increases the rotational speed of fan 22 while causing refrigerant heating device 75 (e.g., a heater) to heat refrigerant.
  • refrigerant heating device 75 e.g., a heater
  • control device 100 determines a rotational speed of the fan for which the refrigerant at point C has a degree of superheat SH of zero.
  • control device 100 determines an amount of refrigerant from a map indicating a previously stored correlation between the rotational speed of the fan and the amount of refrigerant.
  • Fig. 10 is an example of a map for determining an amount of refrigerant from a rotational speed of the fan.
  • the graph shown in Fig. 8 is transformed and the vertical axis represents the amount of refrigerant, the graph shown in Fig. 10 is obtained.
  • a boundary of whether the gas-liquid separation mechanism disposed at branching point BP1 can provide gas-liquid separation is a dryness of 0.05
  • a line in Fig. 10 representing the dryness of 0.05 will be a map representing a correlation between the fan's rotational speed and the amount of refrigerant.
  • a region above the line of the dryness of 0.05 is a region in which refrigerant has an amount equal to or larger than an appropriate amount, and a region below the line is a region in which refrigerant is short in amount.
  • the fan's rotational speed is decreased to 25% corresponding to an amount of refrigerant which is 95% for the sake of illustration, and whether the refrigerant is short is examined.
  • the fan's rotational speed is gradually increased from 25% to sense the amount of the refrigerant.
  • the amount of the refrigerant can be sensed to be 90%.
  • fan 22 While in the example described above, fan 22 is changed in rotational speed to change refrigerant in dryness to sense an amount of the refrigerant, fan 22 may have a rotational speed fixed to 30% and the compressor's operating frequency may instead be changed to change dryness to sense an amount of refrigerant.
  • Fig. 11 is an example of a map for determining an amount of refrigerant from a frequency of the compressor.
  • the vertical axis represents the amount of refrigerant (in %), and the horizontal axis represents the operating frequency (in Hz).
  • a line in Fig. 11 representing the dryness of 0.05 will be a map representing a correlation between the compressor's operating frequency and the amount of refrigerant.
  • a region above the line of the dryness of 0.05 is a region in which refrigerant has an amount equal to or larger than an appropriate amount, and a region below the line is a region in which refrigerant is short in amount.
  • the rotational speed of fan 22 is set to 30% and the operating frequency of the compressor is set to 80 Hz to determine whether the refrigerant is short, and when the refrigerant is short, then, the operating frequency of the compressor is gradually decreased from 80 Hz to examine an operating frequency of the compressor for which degree of superheat SH is zero. For example, when the operating frequency is 70 Hz, the amount of refrigerant can be sensed to be 85%, and when the operating frequency is 30 Hz, the amount of refrigerant can be sensed to be 77.5%.
  • the fan's rotational speed is set to be lower than that in the normal operation or zeroed to reduce condenser 20 in capacity so that refrigerant passing through the condenser is high in dryness to facilitate detecting shortage of refrigerant.
  • shortage of refrigerant can be detected even at an early stage thereof.
  • the fan or the like can operated to gradually reduce dryness of refrigerant passing through the condenser to detect an amount of refrigerant.
  • a user or a service provider can be notified of emergency or an amount to be additionally sealed, based on the amount of refrigerant sensed.
  • the fan's rotational speed is decreased or the compressor's frequency is increased as means for increasing dryness at the gas-liquid separator
  • the injection channel may have its expansion valve opened by an increased angle or these may be composited together.
  • Fig. 12 is a diagram showing a configuration of a refrigeration cycle apparatus 201 according to a second embodiment.
  • Refrigeration cycle apparatus 201 has the configuration of refrigeration cycle apparatus 1 shown in Fig. 1 with outdoor unit 2 replaced with an outdoor unit 202.
  • Load device 3 will not be described repeatedly as it is the same in configuration.
  • Outdoor unit 202 has the configuration of outdoor unit 2 having compressor 10 and control device 100 replaced with a compressor 210 and a control device 300, and further including a heat exchanger 40, an expansion valve 92, and pipes 93 and 94. Outdoor unit 202 has a remainder similar in configuration to outdoor unit 2, and accordingly, will not be described repeatedly.
  • Heat exchanger 40 has a first passage HI and a second passage H2, and is configured to exchange heat between refrigerant passing through first passage HI and refrigerant passing through second passage H2.
  • Liquid receiver 30 is disposed between first passage HI of heat exchanger 40 and condenser 20 and configured to store refrigerant.
  • Compressor 210 has an intermediate pressure port G3 in addition to suction port G1 and discharging port G2.
  • Compressor 10 is configured to suck through suction port G1 refrigerant having passed through evaporator 60 and discharge the refrigerant through discharging port G2 toward condenser 20 together with refrigerant sucked through intermediate pressure port G3.
  • Expansion valve 92, pipe 93, second passage H2 of heat exchanger 40, and pipe 94 constitute a third channel F3 passing refrigerant from a branching point BP2 of the main circuit to intermediate pressure port G3 of compressor 210.
  • Third channel F3 will also be referred to as an "injection channel.”
  • the rotational speed of fan 22 is changed to change refrigerant in dryness to sense an amount of the refrigerant
  • the rotational speed of fan 22 and the operating frequency of the compressor are fixed and a degree of opening of expansion valve 92 is instead changed to change dryness.
  • Fig. 13 is an example of a map for determining an amount of refrigerant from a degree of opening of an expansion valve.
  • the vertical axis represents the amount of refrigerant (in %)
  • the horizontal axis represents a pulse count of a control signal corresponding to a degree of opening of expansion valve 92.
  • a degree of opening of the expansion valve is represented by a pulse count.
  • a region above the line of the dryness of 0.05 is a region in which refrigerant has an amount equal to or larger than an appropriate amount, and a region below the line is a region in which refrigerant is short in amount.
  • the rotational speed of fan 22 is set to 30% and the degree of opening of expansion valve 92 is set to 60 pulses to determine whether refrigerant is short, and when the refrigerant is short, then, the degree of opening of expansion valve 92 is gradually decreased to examine a degree of opening of expansion valve 92 at which degree of superheat SH is zero.
  • the degree of opening of expansion valve 92 is 50 pulses, the amount of refrigerant can be sensed to be 77%, and when the degree of opening of expansion valve 92 is 30 pulses, the amount of refrigerant can be sensed to be 74.5%.
  • a change of either the rotational speed of fan 22 or the operating frequency of compressor 210 may be used in combination with a change of the degree of opening of expansion valve 92.
  • outdoor unit 2 of refrigeration cycle apparatus 1 has a normal mode and a refrigerant shortage sensing mode and is configured to be connected to load device 3 including expansion device 50 and evaporator 60.
  • Outdoor unit 2 includes first channel F1, compressor 10, condenser 20, second channel F2, erected pipe 71 as a gas-liquid separation structure, flow rate regulation device 73, refrigerant heating device 75, dryness increasing device 150, temperature sensor 122, and notification device 101.
  • First channel F1 is configured to form a circulation channel through which refrigerant circulates by being connected to load device 3.
  • Compressor 10 and condenser 20 are disposed along first channel F1.
  • Second channel F2 branches from branching point BP1 of first channel F1 downstream of condenser 20 in a direction in which the refrigerant circulates, and second channel F2 is configured to return to compressor 10 refrigerant having passed through condenser 20.
  • Erected pipe 71 that is a gas-liquid separation structure is provided at branching point BP1.
  • Flow rate regulation device 73 and refrigerant heating device 75 are disposed along second channel F2 such that flow rate regulation device 73 follows branching point BP1 and refrigerant heating device 75 follows flow rate regulation device 73.
  • Dryness increasing device 150 increases the dryness of the refrigerant that has passed through the condenser 20 in the refrigerant shortage sensing mode to be larger than in the normal mode.
  • Temperature sensor 122 senses temperature T1 of the refrigerant after it passes through refrigerant heating device 75 on second channel F2.
  • notification device 101 provides notification of shortage of the refrigerant.
  • dryness increasing device 150 includes fan 22 configured to deliver external air to condenser 20, and control device 100 configured to control fan 22. As shown in step S12 of Fig. 7 , in the refrigerant shortage sensing mode, fan 22 has a rotational speed set to be lower than that in the normal mode or zeroed.
  • notification device 101 in the refrigerant shortage sensing mode, is configured to provide notification of an amount of the refrigerant corresponding to a rotational speed of fan 22 for which degree of superheat SH calculated based on an output of temperature sensor 122 changes from positive to zero (steps S14 and S15 in Fig. 7 ).
  • notification device 101 in the refrigerant shortage sensing mode, is configured to provide notification of an amount of the refrigerant corresponding to an operating frequency of compressor 10 for which degree of superheat SH calculated based on the output of temperature sensor 122 changes from positive to zero.
  • outdoor unit 202 further includes heat exchanger 40 having first passage HI and second passage H2 and configured to exchange heat between refrigerant passing through first passage HI and refrigerant passing through second passage H2, and expansion valve 92.
  • Heat exchanger 40 has first passage HI disposed downstream of condenser 20 provided along first channel F1.
  • Compressor 210 has intermediate pressure port G3 in addition to suction port G1 and discharging port G2.
  • Compressor 210 is configured to suck through suction port G1 refrigerant having passed through evaporator 60 and discharge the refrigerant through discharging port G2 toward condenser 20 together with refrigerant sucked through intermediate pressure port G3.
  • Outdoor unit 202 further includes third channel F3 passing refrigerant from branching point BP2 of the main circuit to intermediate pressure port G3 of compressor 210.
  • Third channel F3 includes expansion valve 92, pipe 93, second passage H2 of heat exchanger 40, and pipe 94.
  • Notification device 101 in the refrigerant shortage sensing mode, is configured to provide notification of an amount of the refrigerant corresponding to a degree of opening of expansion valve 92 at which degree of superheat SH calculated based on the output of temperature sensor 122 changes from positive to zero.
  • second channel F2 branches at erected pipe 71 on branching point BP from first channel F1 in a direction opposite to gravity.
  • refrigeration cycle apparatus 1 may be utilized for an air conditioner or the like.

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  • 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)
EP19955082.3A 2019-12-04 2019-12-04 Ausseneinheit und kühlzyklusvorrichtung Pending EP4071425A4 (de)

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JPS63169461A (ja) * 1986-12-27 1988-07-13 三菱電機株式会社 空気調和機
JPH0460359A (ja) * 1990-06-28 1992-02-26 Nippondenso Co Ltd 冷媒不足検出装置
JPH06207766A (ja) * 1992-03-31 1994-07-26 Unisia Jecs Corp 空調装置
JP2005147456A (ja) * 2003-11-13 2005-06-09 Daikin Ind Ltd 空気調和装置
CN101498535B (zh) * 2005-04-07 2011-01-05 大金工业株式会社 空调装置的制冷剂量判定系统
JP5582773B2 (ja) * 2009-12-10 2014-09-03 三菱重工業株式会社 空気調和機および空気調和機の冷媒量検出方法
CN101876474B (zh) * 2010-07-22 2012-06-27 四川长虹空调有限公司 空调器缺少制冷剂的自动检测方法
CN103348197B (zh) * 2011-07-05 2016-02-10 松下知识产权经营株式会社 制冷循环装置
CN107110586B (zh) 2015-02-25 2020-01-24 三菱电机株式会社 制冷装置
CN104949411B (zh) * 2015-06-09 2018-07-17 广东美的暖通设备有限公司 一种冷媒量检测装置、具有该检测装置的空调及检测方法
JP2017198375A (ja) * 2016-04-26 2017-11-02 株式会社デンソー 冷媒量不足検知装置および冷凍サイクル装置
JP6888418B2 (ja) * 2017-05-23 2021-06-16 ダイキン工業株式会社 熱源側ユニット及び冷凍装置
ES2886912T3 (es) * 2017-11-22 2021-12-21 Mitsubishi Electric Corp Acondicionador de aire

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