WO2017175299A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2017175299A1
WO2017175299A1 PCT/JP2016/061091 JP2016061091W WO2017175299A1 WO 2017175299 A1 WO2017175299 A1 WO 2017175299A1 JP 2016061091 W JP2016061091 W JP 2016061091W WO 2017175299 A1 WO2017175299 A1 WO 2017175299A1
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Prior art keywords
refrigerant
refrigeration cycle
cycle apparatus
pressure
compressor
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PCT/JP2016/061091
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English (en)
Japanese (ja)
Inventor
悟 梁池
智隆 石川
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三菱電機株式会社
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Priority to JP2018510045A priority Critical patent/JPWO2017175299A1/ja
Priority to PCT/JP2016/061091 priority patent/WO2017175299A1/fr
Publication of WO2017175299A1 publication Critical patent/WO2017175299A1/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

Definitions

  • the present invention relates to a refrigeration cycle apparatus used for applications such as freezing and refrigeration.
  • a heat source unit having a compressor and a condenser and a cooling unit having an expansion valve and an evaporator are connected by a connecting pipe, and the refrigerant is circulated between the heat source unit and the cooling unit through the connecting pipe.
  • a freezer is known.
  • CO 2 which is a natural refrigerant and has a high pressure.
  • the conventional refrigerator as described above is used for a showcase or the like installed in a store such as a convenience store or a supermarket
  • a cooling unit is often installed at a location away from the heat source unit.
  • the length of the communication pipe is increased.
  • the total length of the connecting pipe is often about 100 m.
  • the material cost for constructing the connecting pipe on site is increased. For this reason, the working time and construction cost for installing the refrigerator have been increased.
  • the refrigerant in the conventional refrigerator high global warming potential R404A or chlorofluorocarbon refrigerant is used, such as R410A, compared with CO 2, the operating pressure becomes low. Therefore, when only the refrigerator is replaced with CO 2 , the conventional connecting pipe has a low design pressure, and thus cannot be reused, and the construction cost increases because the high-pressure connecting pipe is re-installed.
  • Patent Document 1 has been proposed as a technique using a communication pipe having a low design pressure.
  • a pipe with a low design pressure is used as it is, there is a possibility that the refrigerator stops at the time of a power failure or a compressor failure, and the refrigerant pressure rises above the design pressure as the outside air temperature rises.
  • the refrigerant is collected in a single container designed with a high pressure resistance, and the pressure rise is suppressed by reducing the amount of refrigerant in the refrigerant circuit.
  • Patent Document 2 a method of discharging the refrigerant once stored in the refrigerant storage means at the time of restart is also employed.
  • the refrigerant is returned to the refrigerant circuit at the time of restart after the refrigerant is collected in the refrigerant collection container at the time of a power failure, and whether the refrigerant is discharged from the refrigerant collection container.
  • Pressure is used as a criterion.
  • it since it is not possible to quickly and accurately determine whether the refrigerant has been sufficiently discharged from the refrigerant recovery container, it takes a long time to return to the normal operation after the refrigerant discharge operation, and the refrigeration capacity decreases and the cooling time becomes long. There is also a problem that efficiency is reduced.
  • the present invention has been made in order to solve the above-described problems, and can use piping with a low design pressure, reduce the cost of installation work at the site, and collect sufficient refrigerant during a power failure.
  • An object of the present invention is to provide a refrigeration cycle apparatus that achieves high reliability by carrying out and also realizes a compact container volume.
  • the refrigeration cycle apparatus is a refrigeration cycle apparatus having a refrigerant circuit to which a compressor, a first heat exchanger, a decompression device, and a second heat exchanger are connected, and the refrigerant inlet is the first heat exchange.
  • a refrigerant storage means connected between the pressure reducer and the refrigerant outlet, the refrigerant outlet being connected between the second heat exchanger and the compressor, and an outflow of the refrigerant stored in the refrigerant storage means.
  • the refrigerant storage means includes at least one of a refrigerant outflow promotion means for promoting the outflow of the stored refrigerant, and a temperature change and a superheat degree change of the refrigerant stored in the refrigerant storage means.
  • a control unit that controls the refrigerant outflow promotion means, so that piping with low design pressure can be used, the cost of installation work at the site can be reduced, and sufficient refrigerant recovery at the time of a power failure Thus, high reliability can be obtained, and a compact container volume can also be realized.
  • FIG. 1 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100A) according to Embodiment 1 of the present invention.
  • FIG. 2 is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of the refrigeration cycle apparatus 100A.
  • FIG. 3 is a schematic configuration diagram illustrating an example of a refrigerant circuit configuration of the refrigeration cycle apparatus 100A.
  • the refrigeration cycle apparatus 100A will be described with reference to FIGS.
  • the refrigeration cycle apparatus 100 ⁇ / b> A includes a heat source unit 1 and a cooling unit 2 disposed away from the heat source unit 1.
  • the refrigeration cycle apparatus 100 ⁇ / b> A is connected between the heat source unit 1 and the cooling unit 2, and the first communication pipe 5 and the second communication pipe that circulate the refrigerant between the heat source unit 1 and the cooling unit 2.
  • CO 2 that is a high-pressure refrigerant is used as the refrigerant of the refrigeration cycle apparatus 100A, and the pressure on the high-pressure side of the refrigeration cycle is equal to or lower than the critical pressure of the refrigerant.
  • the heat source unit 1 includes a compressor 3 and a condenser (high-pressure side heat exchanger) 4.
  • the heat source unit 1 is provided with a plurality of connecting pipes that connect the second connecting pipe 8, the compressor 3, the condenser 4, and the first connecting pipe 5 in this order.
  • the plurality of connection pipes of the heat source unit 1 are collectively referred to as a connection pipe 50A.
  • the cooling unit 2 includes a pressure reducing device (expansion valve) 6 and an evaporator (low pressure side heat exchanger) 7.
  • the cooling unit 2 is provided with a plurality of connecting pipes that connect the first connecting pipe 5, the decompression device 6, the evaporator 7, and the second connecting pipe 8 in this order.
  • the plurality of connecting pipes of the cooling unit 2 are collectively referred to as a connecting pipe 50B.
  • the compressor 3 when the compressor 3 is driven, the refrigerant is converted into the compressor 3, the condenser 4, the first communication pipe 5, the decompression device 6, the evaporator 7, and the second communication pipe 8. Are sent back to the compressor 3 in this order.
  • the compressor 3 compresses a gaseous refrigerant.
  • the refrigerant compressed by the compressor 3 is sent to the condenser 4.
  • the compressor 3 can be comprised by a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor etc., for example.
  • the condenser 4 cools the gaseous refrigerant from the compressor 3 to form a liquid refrigerant. That is, the condenser 4 cools and condenses the refrigerant by discharging heat from the gaseous refrigerant to a coolant (for example, air, water, antifreeze or another refrigeration cycle).
  • the refrigerant condensed in the condenser 4 is sent to the decompression device 6 via the first communication pipe 5.
  • the condenser 4 is, for example, a fin and tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, or a plate heat exchanger. Or the like.
  • the condenser 4 corresponds to the “first heat exchanger (heat source side heat exchanger)” of the present invention.
  • the first communication pipe 5 guides the refrigerant sent from the condenser 4 to the decompression device 6 between the heat source unit 1 and the cooling unit 2. In the first connecting pipe 5, a liquid refrigerant is guided.
  • the decompression device 6 expands the liquid refrigerant from the condenser 4 and decompresses it.
  • the decompression device 6 is an electric expansion valve capable of adjusting the flow rate of the refrigerant.
  • the decompression device 6 is controlled by the control unit 70.
  • the decompression device 6 not only an electric expansion valve but also a mechanical expansion valve employing a diaphragm for a pressure receiving portion, a capillary tube, or the like can be applied.
  • An on-off valve 22 is provided between the first communication pipe 5 and the pressure reducing device 6.
  • the evaporator 7 evaporates the refrigerant from the decompression device 6. That is, the evaporator 7 heats and evaporates the refrigerant by transferring heat from a heating material (for example, air, water, antifreeze or another refrigeration cycle) to the liquid refrigerant.
  • the evaporator 7 is provided in a cooling container (for example, a cooling showcase) installed in a store such as a convenience store or a supermarket. Such a cooling container is cooled by evaporating the refrigerant in the evaporator 7.
  • the refrigerant evaporated in the evaporator 7 is sent to the compressor 3 through the second connecting pipe 8.
  • the evaporator 7 is, for example, a fin and tube heat exchanger, a microchannel heat exchanger, a shell and tube heat exchanger, a heat pipe heat exchanger, a double pipe heat exchanger, or a plate heat exchanger. Or the like.
  • the evaporator 7 corresponds to the “second heat exchanger (use side heat exchanger)” of the present invention.
  • the second communication pipe 8 guides the refrigerant sent from the evaporator 7 to the compressor 3 between the heat source unit 1 and the cooling unit 2. In the second communication pipe 8, a gaseous refrigerant is guided.
  • the first communication pipe 5 is upstream of the decompression device 6 and is located on the high pressure side in the refrigeration cycle.
  • One second connecting pipe 8 is downstream of the decompression device 6 and is located on the low pressure side in the refrigeration cycle.
  • the high pressure side of the refrigeration cycle apparatus 100 ⁇ / b> A operates at a pressure equal to or lower than the design pressure of the first communication pipe 5.
  • the design pressure of the first connecting pipe 5 is 4.15 MPa.
  • the refrigeration cycle apparatus 100 has a refrigerant storage tank 9 that is an example of refrigerant storage means connected to the first communication pipe 5 and the second communication pipe 8.
  • the inlet 14, which is one of the refrigerant inlets and outlets of the refrigerant storage tank 9, is connected to the first connecting pipe 5 on the downstream side of the condenser 4, and the outlet 15, which is the other refrigerant inlet / outlet, is connected to the compressor 3. It is connected to the second connecting pipe 8 on the suction side.
  • the refrigerant storage tank 9 stores refrigerant.
  • the inlet-side electromagnetic valve 10 is provided at the inlet 14 of the refrigerant storage tank 9 and is energized and closed (open during a power failure).
  • the inlet-side check valve 11 is provided between the inlet-side electromagnetic valve 10 and the refrigerant storage tank 9 so that the refrigerant can flow only in the inflow direction to the refrigerant storage tank 9.
  • the mechanical on-off valve 12 is provided at the outlet 15 of the refrigerant storage tank 9 and is energized open (closed during a power failure).
  • the mechanical on-off valve 12 mechanically opens and closes the valve.
  • the refrigeration cycle apparatus 100A by having the refrigerant storage tank 9, it is possible to temporarily store the refrigerant.
  • the energized open solenoid valve is an electromagnetic valve configured to open only when the solenoid valve is energized and to shut off the valve by stopping energization of the solenoid valve.
  • a solenoid valve that is energized and closed is an electromagnetic valve that is configured such that the valve is cut off only when the solenoid valve is energized, and the valve is opened by stopping energization of the solenoid valve.
  • the mechanical on-off valve 12 is a temperature expansion valve that is used as a decompression device for a general refrigeration air conditioner.
  • the same refrigerant as that used in the unit is sealed in the temperature sensing cylinder, and the opening degree of the expansion valve is adjusted by a saturation pressure corresponding to the temperature of the temperature sensing cylinder.
  • the reference pressure is the refrigerant saturation pressure at the portion where the expansion valve body is located, and the valve opens when the temperature of the temperature sensing cylinder is higher than this and the saturation pressure is high.
  • the valve is closed when the temperature of the temperature sensing cylinder is low and the saturation pressure is low or equal to the reference pressure.
  • the mechanical on-off valve 12 corresponds to the “outflow valve” of the present invention.
  • the refrigeration cycle apparatus 100A includes a control unit 70 that performs overall control of the refrigeration cycle apparatus 100A.
  • the control unit 70 controls each actuator (driving components such as the compressor 3 and the decompression device 6) based on the detection value from each detector.
  • the control unit 70 can be configured by hardware such as a circuit device that realizes the function, or can be configured by an arithmetic device such as a microcomputer or a CPU and software executed thereon.
  • the temperature sensing cylinder 13 is connected to a connection pipe 50A (discharge pipe) on the discharge side of the compressor 3, and the mechanical on-off valve 12 is opened and closed by a saturated pressure corresponding to the discharge pipe temperature.
  • a connection pipe 50A discharge pipe
  • the mechanical on-off valve 12 is opened and closed by a saturated pressure corresponding to the discharge pipe temperature.
  • An installation location is not limited to this position. A location where the temperature higher than the saturation temperature corresponding to the reference pressure can be obtained during normal operation (for example, the first connecting pipe 5) may be set as a location where the temperature sensing cylinder 13 is installed.
  • the mechanical on-off valve 12 By using the mechanical on-off valve 12, it is possible to control the valve by a change in refrigerant pressure or temperature even during a power failure.
  • sufficient refrigerant recovery can be performed by degassing operation in refrigerant recovery at the time of power failure, which will be described later, and after the refrigerant recovery, the valve is closed and sealed in the refrigerant storage tank 9. it can.
  • the refrigerant storage tank 9 may be installed outside the heat source unit 1.
  • a refrigerant storage tank 9, an inlet-side electromagnetic valve 10, an inlet-side check valve 11, and a mechanical on-off valve 12 are provided in a unit (hereinafter referred to as a refrigerant storage unit 60) different from the heat source unit 1. It is good to accommodate.
  • the refrigerant storage unit 60 includes the inlet side electromagnetic valve 10, the inlet side check valve 11, the refrigerant storage tank 9, and the mechanical on-off valve 12 from the first communication pipe 5 to the second communication pipe 8. They are connected in series and accommodated.
  • the heat-source unit 1 can have the same configuration as an outdoor unit of an ordinary refrigeration cycle apparatus (an outdoor unit not including the refrigerant storage tank 9). As a result, the outdoor unit that is the heat source unit 1 can be shared, and the system construction cost can be reduced.
  • the design pressure of the component corresponding to the R410A refrigerant is 4.15 MPa which is the saturation pressure at 65 ° C., which corresponds to the saturation pressure at 8 ° C. with CO 2 refrigerant. That is, if the ambient temperature of the refrigeration cycle apparatus 100A is 8 ° C. or higher, the pressure resistance reference value may be exceeded. Therefore, in the refrigeration cycle apparatus 100A, by collecting and sealing the refrigerant in the refrigerant storage tank 9, it is possible to reduce the amount of refrigerant in the main refrigerant circuit and to suppress the increase in pressure.
  • the refrigerant storage tank 9 is set to a design pressure (for example, 12 MPa) corresponding to the CO 2 refrigerant having a high operating pressure. Moreover, in order to avoid that the inside of the refrigerant
  • a design pressure for example, 12 MPa
  • the refrigerant storage tank 9 during normal operation in the refrigeration cycle apparatus 100A will be described.
  • the valve is shut off by energizing the energized closed inlet side solenoid valve 10.
  • the mechanical on-off valve 12 in which the temperature-sensitive cylinder 13 is installed in the discharge pipe section (or the first connecting pipe 5) that is at a high temperature is in the open state. Therefore, the refrigerant storage tank 9 is maintained at a low pressure equivalent to the suction side pressure (evaporation pressure) of the compressor 3.
  • the inside of the refrigerant storage tank 9 is set to be equal to or lower than the suction side pressure of the compressor 3. Can be maintained. For example, if the rotation speed of the compressor 3 is increased, the low pressure is once reduced as much as possible, and then the operation is returned to the low pressure to be used, the inside of the refrigerant storage tank 9 provided with the outlet check valve is at the lower limit. It will be maintained at a low pressure. If a lower pressure can be maintained, an effect of promoting the refrigerant recovery effect can be obtained. That is, the control unit 70 increases the rotational speed of the compressor 3 and reduces the low pressure as much as possible to promote refrigerant discharge.
  • the refrigeration cycle apparatus 100A When the refrigeration cycle apparatus 100A is abnormally stopped due to a power failure or the like from the normal operation, the high-pressure refrigerant existing in the refrigerant circuit flows into the refrigerant circuit portion where the low-pressure refrigerant is present unless the valve is shut off. The pressure in the refrigerant circuit is equalized. At this time, liquid refrigerant exists in all the refrigerant circuits. For this reason, in the refrigeration cycle equipment that replaces the refrigerant used with a higher operating pressure than the conventional refrigerant and diverts the equipment parts, when the outside air becomes hot, the refrigerant pressure also rises, and the pressure resistance reference value of the diverted equipment parts May be exceeded. Therefore, in the refrigeration cycle apparatus 100A, it is possible to maintain the pressure of the diverted component below the pressure resistance reference value even in a state where electric power necessary for operation cannot be obtained, particularly in the case of an abnormal stop in the event of a power failure.
  • the refrigeration cycle apparatus 100A a state where power necessary for operation cannot be obtained, particularly an abnormal stop in the case of a power failure will be described.
  • the compressor 3 and the condenser 4 are stopped, and the energized closed inlet side electromagnetic valve 10 is opened.
  • the high-pressure side liquid refrigerant existing in the refrigerant circuit from the condenser 4 to the decompression device 6 can be passed to the refrigerant storage tank 9 maintained at a low pressure.
  • the mechanical on-off valve 12 installed on the outlet 15 side of the refrigerant storage tank 9 is opened because the discharge pipe immediately after the power failure is maintained at high temperature and pressure.
  • the outflow port in the refrigerant storage tank 9 connected to the outflow port 15 is installed above the refrigerant storage tank 9 so that only gas can flow out to the low pressure side.
  • the refrigeration cycle apparatus 100A it is possible to avoid that the pressure in the refrigerant storage tank 9 increases due to the gas refrigerant and the refrigerant cannot be recovered, and the liquid refrigerant with high density can be recovered efficiently. Refrigerant recovery is possible.
  • the operation of the control board for driving the mechanical on-off valve 12 is not required, so that the refrigerant can be recovered in the refrigerant storage tank 9 even during a power failure, and the diverted device It is possible to keep the pressure resistance below the component.
  • the pressure in the main refrigerant circuit is equalized, so that the temperature of the discharge pipe is lowered and the mechanical on-off valve 12 is shut off. Therefore, according to the refrigeration cycle apparatus 100A, even when a power failure occurs, it is possible to vent the gas at the time of refrigerant recovery, efficiently recover only the liquid refrigerant, and shut off the outlet 15 after recovery to seal the refrigerant. .
  • the liquid refrigerant in the refrigerant storage tank 9 needs to be returned to the main refrigerant circuit. Therefore, the second outflow port through which the liquid refrigerant that accumulates below the refrigerant storage tank 9 flows out is installed in the refrigerant storage tank 9 to enable the return to the normal operation.
  • the second outlet is common to the outlet 15 where the mechanical on-off valve 12 is installed, in order to prevent the outflow of the liquid refrigerant at the time of refrigerant recovery, the flow resistance is made narrower than the gas outlet. Need to be increased.
  • the refrigerant storage tank 9 is provided, so that piping with a low design pressure can be used, and the cost of installation work at the site can be reduced. It is also possible to obtain a high reliability by performing a proper refrigerant recovery and to make the container volume compact.
  • FIG. FIG. 4 is a schematic configuration diagram showing an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100B) according to Embodiment 2 of the present invention.
  • the refrigeration cycle apparatus 100B will be described based on FIG.
  • differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.
  • the temperature sensing cylinder 13 is installed between the refrigerant storage tank 9 and the mechanical on-off valve 12, and the refrigerant is discharged from the refrigerant storage tank 9 from at least one of the temperature and superheat degree of the refrigerant storage tank 9. It is detected, and it is possible to detect whether the refrigerant is discharged from the refrigerant storage tank 9 more directly.
  • the installation position of the temperature sensing cylinder 13 may be inside or on the surface of the refrigerant storage tank 9.
  • the refrigerant storage tank 9 has a large heat capacity and it is difficult to accurately measure the temperature
  • the refrigerant storage tank 9 and the mechanical opening / closing valve 12 It is more preferable to set it as the piping part between.
  • FIG. 5 is a graph showing a change in the pressure of the refrigerant over time in the vicinity of the temperature sensing cylinder 13 when the liquid refrigerant recovered in the refrigerant storage tank 9 is discharged.
  • FIG. 6 is a graph showing the change in the saturation temperature of the refrigerant over time in the vicinity of the temperature sensitive cylinder 13 when the liquid refrigerant collected in the refrigerant storage tank 9 is discharged.
  • FIG. 7 is a graph showing changes in the temperature of the refrigerant over time in the vicinity of the temperature sensitive cylinder 13 when the liquid refrigerant recovered in the refrigerant storage tank 9 is discharged.
  • FIG. 8 is a graph showing changes in the degree of superheat of the refrigerant over time in the vicinity of the temperature sensitive cylinder 13 when the liquid refrigerant recovered in the refrigerant storage tank 9 is discharged.
  • Patent Document 2 Japanese Patent Laid-Open No. 2014-222131
  • refrigerant discharge from the refrigerant storage tank is detected by pressure.
  • the pressure of the refrigerant gradually decreases as the liquid refrigerant flows out, it is difficult to know the timing of completion of discharge, and the time until switching to normal operation becomes longer than necessary and the cooling time becomes longer. There was a point.
  • the refrigerant discharge completion timing is determined from at least one of temperature change and superheat degree change.
  • the refrigerant flowing in the vicinity of the temperature sensing cylinder 13 changes in order into a supercritical state, a two-phase refrigerant, and a gas refrigerant (one-dot chain line A ).
  • the temperature becomes a temperature corresponding to the saturation pressure in the two-phase state, but when it becomes a gas refrigerant, the temperature approaches the outside air temperature, so that the temperature rises as indicated by a dashed line A in FIG. 7 and overheats as indicated by a dashed line A in FIG. The degree also rises.
  • the density of the gas refrigerant is about 1/30 of that of the liquid refrigerant, which is smaller than the liquid refrigerant, and the liquid refrigerant is dominant as the amount of the refrigerant. Therefore, it is sufficient to switch to the normal operation from the one-dot chain line A where the liquid refrigerant discharge can be confirmed.
  • the liquid refrigerant is discharged when the temperature before and after the alternate long and short dash line A and the change in the degree of superheat change from the reference range.
  • the one-dot chain line A may be set in advance as a time obtained by an experiment or the like.
  • the reference range of change may be set as a range that exceeds an allowable range that is determined to be a two-phase state.
  • At least one of a pressure sensor and a temperature sensor may be installed to measure at least one of temperature and superheat, and an electromagnetic valve may be installed instead of the mechanical on-off valve 12.
  • an electromagnetic valve may be installed instead of the mechanical on-off valve 12.
  • the installation position of the temperature sensing cylinder 13, the pressure sensor, and the temperature sensor may be a downstream portion of the mechanical on-off valve 12 when the refrigerant is discharged from the refrigerant storage tank 9.
  • the same effect as that of the refrigeration cycle apparatus 100A according to Embodiment 1 can be obtained, and the refrigerant can be quickly returned into the circuit at the time of restart after refrigerant recovery.
  • the completion of the refrigerant discharge from the refrigerant storage tank 9 can be quickly determined, and it is possible to avoid the extension of the cooling time by maintaining the refrigeration capacity.
  • FIG. 9 to 14 are schematic configuration diagrams showing an example of the refrigerant circuit configuration of the refrigerant discharge promoting means included in the refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100C) according to Embodiment 3 of the present invention.
  • the refrigerant discharge promoting means will be described with reference to FIGS.
  • the refrigeration cycle apparatus 100C is either the refrigeration cycle apparatus 100A according to the second embodiment or the refrigeration cycle apparatus 100C according to the third embodiment.
  • the refrigerant storage tank 9 is provided with refrigerant discharge promoting means for quickly discharging the liquid refrigerant.
  • the refrigerant discharge promoting means heats the refrigerant storage tank 9 to promptly discharge the liquid refrigerant in the refrigerant storage tank 9 by evaporating.
  • heating the lower part of the refrigerant storage tank 9 is more effective because the liquid refrigerant can be directly heated.
  • the heating method is suitable for the electric heater 16 because the heating amount can be easily controlled by power control. That is, the refrigerant discharge promoting means includes the electric heater 16 which is an example of the heating means. The driving of the electric heater 16 is controlled by the control unit 70.
  • the refrigerant discharge promoting means includes a blower 17 that is an example of a heating means. The driving of the blower 17 is controlled by the control unit 70.
  • the refrigerant on the high-pressure side of the main refrigerant circuit has a higher temperature than the refrigerant storage tank 9, heat can be obtained by heat exchange with the high-pressure refrigerant in the main refrigerant circuit.
  • the refrigerant in the main refrigerant circuit can obtain cold, if the refrigeration cycle apparatus is used for refrigeration, the refrigeration capacity can be improved and the energy saving effect can be obtained. Since the condensation can be promoted by heat exchange with the high-pressure refrigerant to reduce the high pressure, the compressor input can be further reduced.
  • the discharge gas refrigerant of the compressor 3 has a high temperature, heat exchange with the discharge gas is most suitable.
  • a branch pipe 33 is provided which branches the discharge pipe of the compressor 3 and passes through the refrigerant storage tank 9 and then reconnects to the discharge pipe.
  • the first on-off valve 31 is provided on the downstream side of the connection portion of the discharge pipe with the branch pipe 33
  • the second on-off valve 32 is provided on the upstream side of the refrigerant storage tank 9 of the branch pipe 33. Then, by controlling the opening / closing of the first opening / closing valve 31 and the second opening / closing valve 32, the refrigerant discharged from the compressor 3 can be guided to the refrigerant storage tank 9.
  • the refrigerant discharge promoting means includes the first on-off valve 31, the second on-off valve 32, and the branch pipe 33, which are examples of the heating means.
  • the opening / closing of the first opening / closing valve 31 and the second opening / closing valve 32 is controlled by the control unit 70.
  • the design pressure may be temporarily exceeded in the main refrigerant circuit. Therefore, when the pressure of the main refrigerant circuit is predicted to exceed the design pressure, a control method that suppresses the heating amount is suitable. As a result, the refrigerant can be discharged as quickly as possible while ensuring the reliability, so that it is possible to avoid extending the cooling time in the showcase cabinet on the use side.
  • the temperature of the refrigerant storage tank 9 starts to rise, and the degree of superheat increases. Therefore, it can be detected that a sufficient degree of superheat has been secured. For example, when the degree of superheat reaches 5 ° C., the heating by the refrigerant discharge promotion is terminated. Thereby, it can heat without excess and deficiency for discharging the liquid refrigerant, and the heating amount can be optimized. And since useless heating can be avoided, it becomes possible to avoid an increase in heating input and a decrease in operating efficiency of the refrigeration cycle at the same time.
  • means for increasing the pressure in the refrigerant storage tank 9 can be employed.
  • an injection pipe 34 branched from the discharge pipe of the compressor 3 is connected to the refrigerant storage tank 9, and the opening / closing valve 35 provided in the injection pipe 34 is controlled to open and close.
  • the high-pressure compressor discharge gas refrigerant may be injected into the refrigerant storage tank 9. Thereby, the pressure in the refrigerant
  • a means of securing a liquid head can be employed. As shown in FIG. 13, by installing the bottom surface of the refrigerant storage tank 9 at a position higher than the outlet (height 18 shown in FIG. 13), the liquid refrigerant head difference can be ensured and discharged more easily. Since it is only installed at a high position, there is no need to change operation control and design load is small.
  • a means for lowering the outlet pressure of the refrigerant storage tank 9, that is, the evaporation temperature can be employed.
  • coolant storage tank 9 and an outflow port expands, and discharge
  • the evaporation temperature is determined depending on the use of the use side heat exchanger (evaporator 7), but it is preferable to ensure the differential pressure by reducing the evaporation temperature as much as possible only when the liquid discharge is promoted at the time of startup.
  • the evaporation temperature can be lowered by increasing the compressor rotation speed. At this time, the refrigerating capacity is improved compared to the normal control, and the cooling time in the showcase cabinet on the use side can be further shortened.
  • the installation of the expansion tank 26 for enlarging the internal volume of the refrigerant circuit can be considered, but a significantly large volume is required, and the installation space, There is a possibility of lack of practicality in terms of cost.
  • the refrigerant storage tank 9 of the refrigeration cycle apparatus 100C is used in combination, the refrigerant in the main refrigerant circuit is largely removed, so the expansion tank 26 can be reduced in size, and the cost and installation area can be reduced. Can be obtained.
  • the expansion tank 26 only needs to be connected between the evaporator 7 and the compressor 3.
  • the state in which the mechanical on-off valve 12 is installed at the outlet of the refrigerant storage tank 9 has been described as an example.
  • a storage electromagnetic valve may be installed. The drive power of the energized open solenoid valve is stored, and energization is continued for about 1 minute after a power failure to recover the refrigerant, the valve is opened, and degassing is performed. Then, energization is stopped and the solenoid valve is shut off to seal the refrigerant. By doing so, an effect equivalent to that of the mechanical on-off valve 12 can be obtained.
  • the refrigerant storage tank 9 of the refrigeration cycle apparatus according to the present embodiment is effective for pressure suppression when high density liquid refrigerant is recovered and the refrigerant in the main refrigerant circuit is removed, the high pressure side is not supercritical. To control. For example, when a dual refrigeration cycle system that cools the high pressure side with another refrigeration cycle is adopted in the refrigeration cycle apparatus according to the present embodiment, the high pressure of the refrigeration cycle apparatus according to the present embodiment can be reduced, and the refrigerant storage tank It is possible to recover the liquid refrigerant having a high density in FIG.
  • FIG. 15 shows an example of a refrigerant circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100D) according to Embodiment 3 of the present invention that employs a dual refrigeration cycle system in which the high-pressure side is cooled by another refrigeration cycle.
  • the refrigeration cycle apparatus 100D includes a refrigerant circuit configuration similar to that of the refrigeration cycle apparatus 100C, and includes another refrigeration cycle 110 in which the compressor 103, the condenser 104, the decompression apparatus 106, and the evaporator 107 are connected in series with a connection pipe 115. I have. That is, the refrigeration cycle apparatus 100D is configured by connecting two refrigeration cycles by the evaporator 107.
  • the high pressure of the refrigeration cycle apparatus 100D can be reduced, and a high-density liquid refrigerant can be recovered in the refrigerant storage tank 9.
  • 16 to 18 are schematic configuration diagrams showing an example of the refrigerant circuit configuration of the refrigerant distribution increasing means provided in the refrigeration cycle apparatus 100C.
  • the refrigerant distribution increasing means will be described with reference to FIGS.
  • the pressure on the high pressure side becomes the driving force, and therefore the refrigerant staying on the low pressure side cannot be recovered. Therefore, when the refrigerant recovery amount is increased, the refrigerant distribution on the high-pressure side only needs to be increased, so that the liquid refrigerant at the outlet of the condenser 4 may be further cooled.
  • the cooling means as shown in FIG. 16, an internal heat exchanger 19 that exchanges heat with the refrigerant on the suction side of the compressor 3 can be used to supercool the liquid refrigerant and increase the refrigerant distribution on the high-pressure side. . That is, the internal heat exchanger 19 can be applied as an example of “refrigerant distribution increasing means”.
  • a bypass pipe 37 is provided for connecting the connection pipe 50 ⁇ / b> A on the downstream side of the condenser 4 to the suction side of the compressor 3 through the internal heat exchanger 19.
  • a decompression device 38 is provided upstream of the internal heat exchanger 19.
  • An on-off valve 39 is installed on the downstream side of the internal heat exchanger 19 of the bypass pipe 37. That is, the liquid refrigerant is supercooled by the bypass refrigerant to increase the refrigerant distribution on the high pressure side.
  • the bypassed refrigerant may be injected into the suction side of the compressor 3 or in the middle of the compression process of the compressor 3 and merged with the main refrigerant circuit.
  • the internal heat exchanger 19, the bypass pipe 37, and the pressure reducing device 38 can be applied as an example of “refrigerant distribution increasing means”.
  • the same effects as those of the refrigeration cycle apparatus 100A according to the first embodiment and the refrigeration cycle apparatus 100B according to the second embodiment can be obtained, and further after the refrigerant is recovered.
  • the refrigerant can be quickly returned to the circuit, and the completion of the refrigerant discharge from the refrigerant storage tank 9 can be quickly determined.
  • the refrigerating capacity it is possible to avoid the extension of the cooling time.
  • the refrigeration cycle apparatus shows a case where a CO 2 refrigerant having a pressure higher than that of the R410A refrigerant of the current refrigerator and a component having a low design pressure is used for cost reduction.
  • the refrigerant to be used is not limited to the CO 2 refrigerant.
  • Another example of the refrigerant having a high pressure is R1123, and the same effect can be obtained.
  • R1123 refrigerant becomes flammable, and if the refrigerant storage tank 9 is applied, the refrigerant is not dispersed even in the event of a power failure and most of the refrigerant can be concentrated in one refrigerant storage tank 9, thus preventing leakage into the room. And exhibits an excellent safety effect. Therefore, the same effects can be obtained for HC-based refrigerants (such as R600a and R290), HFO-based systems (such as R1234yf and R1234ze), and other toxic NH 3 refrigerants.
  • HC-based refrigerants such as R600a and R290
  • HFO-based systems such as R1234yf and R1234ze
  • FIG. 19 to 22 are schematic configuration diagrams showing an example of a medium circuit configuration of a refrigeration cycle apparatus (hereinafter referred to as refrigeration cycle apparatus 100E) according to Embodiment 4 of the present invention. Another embodiment of the present invention will be described with reference to FIGS.
  • the basic refrigerant circuit configuration of refrigeration cycle apparatus 100E is the same as the refrigerant circuit configuration of the refrigeration cycle apparatus according to Embodiments 1 to 3.
  • the refrigerant storage unit 60 of the refrigeration cycle apparatus 100E may be installed not on the heat source unit 1 side but on the cooling unit 2 side. In this way, the installation position of the refrigerant storage unit 60 can be appropriately determined according to the use or installation location of the refrigeration cycle apparatus 100.
  • a second decompression device 21 may be installed between the condenser 4 and the first communication pipe 5 of the refrigeration cycle apparatus 100E. In this way, the refrigerant flow rate of the refrigerant circuit of the refrigeration cycle apparatus 100E can be controlled in more detail.
  • a bypass pipe 41 that connects the discharge side of the compressor 3 and the downstream side (end portion 5 ⁇ / b> A side) of the first connecting pipe 5 is provided, and the on-off valve 42 is provided in the bypass pipe 41. You may do it. By doing so, it is possible to supply the refrigerant discharged from the compressor 3 to the evaporator 7 by bypassing the condenser 4 during the defrosting operation.
  • the refrigeration cycle apparatus has been described by dividing it into four embodiments.
  • the present invention is not limited thereto, and various modifications or changes can be made without departing from the scope and spirit of the present invention.
  • the refrigeration cycle apparatus described in each embodiment is applied to refrigeration apparatuses such as air conditioners (for example, refrigeration apparatuses, room air conditioners, packaged air conditioners, multi air conditioners for buildings, etc.), heat pump water heaters, etc. be able to.
  • air conditioners for example, refrigeration apparatuses, room air conditioners, packaged air conditioners, multi air conditioners for buildings, etc.
  • heat pump water heaters etc. be able to.
  • a flow path switching device for example, a combination of a four-way valve, a two-way valve, or a three-way valve

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un dispositif à cycle frigorifique, comprenant : un moyen de stockage de fluide frigorigène ayant une entrée de fluide frigorigène qui est raccordée entre un premier échangeur de chaleur et un dispositif de réduction de pression et ayant également une sortie de fluide frigorigène raccordée entre un second échangeur de chaleur et un compresseur; un moyen favorisant la sortie de fluide frigorigène pour favoriser la sortie d'un fluide frigorigène stocké dans le moyen de stockage de fluide frigorigène; et une unité de commande pour commander le moyen favorisant la sortie de fluide frigorigène au moyen d'un changement de température du fluide frigorigène stocké dans le moyen de stockage de fluide frigorigène et/ou d'un changement du degré de surchauffe de ce fluide frigorigène.
PCT/JP2016/061091 2016-04-05 2016-04-05 Dispositif à cycle frigorifique WO2017175299A1 (fr)

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PCT/JP2016/061091 WO2017175299A1 (fr) 2016-04-05 2016-04-05 Dispositif à cycle frigorifique

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020186842A (ja) * 2019-05-13 2020-11-19 三菱電機ビルテクノサービス株式会社 冷凍サイクル試験装置
WO2021048900A1 (fr) * 2019-09-09 2021-03-18 三菱電機株式会社 Unité extérieure et dispositif de cycle réfrigérant
WO2021048901A1 (fr) * 2019-09-09 2021-03-18 三菱電機株式会社 Unité extérieure et dispositif à cycle frigorifique
WO2021201242A1 (fr) 2020-04-01 2021-10-07 三菱重工サーマルシステムズ株式会社 Conditionneur d'air, procédé de commande et programme
US20230067007A1 (en) * 2020-04-07 2023-03-02 Mitsubishi Electric Corporation Refrigeration cycle device
WO2023176870A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Unité extérieure pour dispositif de réfrigération et dispositif de réfrigération

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0735429A (ja) * 1993-07-26 1995-02-07 Kubota Corp 空調装置の運転方法、及び、その方法を用いる空調装置
JP2000179958A (ja) * 1998-12-16 2000-06-30 Matsushita Electric Ind Co Ltd 空気調和装置
JP2006153349A (ja) * 2004-11-29 2006-06-15 Mitsubishi Electric Corp 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
WO2009091405A1 (fr) * 2008-01-18 2009-07-23 Carrier Corporation Récipient sous pression pour réduire une pression élevée unitaire pendant le stockage et le transport
JP2009236483A (ja) * 2006-04-11 2009-10-15 Mayekawa Mfg Co Ltd Ｃｏ２冷媒を用いた給湯装置及びその運転方法
JP4687710B2 (ja) * 2007-12-27 2011-05-25 三菱電機株式会社 冷凍装置
WO2014045394A1 (fr) * 2012-09-21 2014-03-27 三菱電機株式会社 Dispositif de réfrigération
JP2014222131A (ja) * 2013-05-14 2014-11-27 三菱電機株式会社 冷凍装置

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006234239A (ja) * 2005-02-23 2006-09-07 Mitsubishi Heavy Ind Ltd 空気調和装置のアキュームレータ内液冷媒検出方法、レシーバ内液冷媒検出方法、冷媒量調整方法、及び空気調和装置

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0735429A (ja) * 1993-07-26 1995-02-07 Kubota Corp 空調装置の運転方法、及び、その方法を用いる空調装置
JP2000179958A (ja) * 1998-12-16 2000-06-30 Matsushita Electric Ind Co Ltd 空気調和装置
JP2006153349A (ja) * 2004-11-29 2006-06-15 Mitsubishi Electric Corp 冷凍空調装置、冷凍空調装置の運転制御方法、冷凍空調装置の冷媒量制御方法
JP2009236483A (ja) * 2006-04-11 2009-10-15 Mayekawa Mfg Co Ltd Ｃｏ２冷媒を用いた給湯装置及びその運転方法
JP4687710B2 (ja) * 2007-12-27 2011-05-25 三菱電機株式会社 冷凍装置
WO2009091405A1 (fr) * 2008-01-18 2009-07-23 Carrier Corporation Récipient sous pression pour réduire une pression élevée unitaire pendant le stockage et le transport
WO2014045394A1 (fr) * 2012-09-21 2014-03-27 三菱電機株式会社 Dispositif de réfrigération
JP2014222131A (ja) * 2013-05-14 2014-11-27 三菱電機株式会社 冷凍装置

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020186842A (ja) * 2019-05-13 2020-11-19 三菱電機ビルテクノサービス株式会社 冷凍サイクル試験装置
JP7338229B2 (ja) 2019-05-13 2023-09-05 三菱電機ビルソリューションズ株式会社 冷凍サイクル試験装置
WO2021048900A1 (fr) * 2019-09-09 2021-03-18 三菱電機株式会社 Unité extérieure et dispositif de cycle réfrigérant
WO2021048901A1 (fr) * 2019-09-09 2021-03-18 三菱電機株式会社 Unité extérieure et dispositif à cycle frigorifique
JPWO2021048900A1 (fr) * 2019-09-09 2021-03-18
JPWO2021048901A1 (fr) * 2019-09-09 2021-03-18
JP7195449B2 (ja) 2019-09-09 2022-12-23 三菱電機株式会社 室外ユニットおよび冷凍サイクル装置
JP7224480B2 (ja) 2019-09-09 2023-02-17 三菱電機株式会社 室外ユニットおよび冷凍サイクル装置
WO2021201242A1 (fr) 2020-04-01 2021-10-07 三菱重工サーマルシステムズ株式会社 Conditionneur d'air, procédé de commande et programme
US20230067007A1 (en) * 2020-04-07 2023-03-02 Mitsubishi Electric Corporation Refrigeration cycle device
WO2023176870A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Unité extérieure pour dispositif de réfrigération et dispositif de réfrigération
WO2023175821A1 (fr) * 2022-03-17 2023-09-21 三菱電機株式会社 Appareil de réfrigération et unité extérieure d'appareil de réfrigération

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