EP3267130B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3267130B1
EP3267130B1 EP15883950.6A EP15883950A EP3267130B1 EP 3267130 B1 EP3267130 B1 EP 3267130B1 EP 15883950 A EP15883950 A EP 15883950A EP 3267130 B1 EP3267130 B1 EP 3267130B1
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EP
European Patent Office
Prior art keywords
refrigerant
pressure
heat exchanger
expansion valve
sub
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EP15883950.6A
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English (en)
French (fr)
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EP3267130A1 (de
EP3267130A4 (de
Inventor
Kazuyuki Ishida
Yasushi Okoshi
Takuya Ito
Masahiro Ito
Takahito HIKONE
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3267130A4 publication Critical patent/EP3267130A4/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
    • F25B2345/003—Control issues for charging or collecting refrigerant to or from a 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
    • 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
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube
    • 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
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • 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
    • F25B2600/2501—Bypass 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2519—On-off 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

Definitions

  • the present invention relates to a refrigeration cycle apparatus, and more particularly, to suppression of liquid backflow during a defrosting operation.
  • Air-cooled heat pump chillers correspond to those refrigeration cycle apparatus, for example.
  • Examples of a defrosting method include a hot-gas reverse type in which an air-heat exchanger operates as a condenser, an off cycle defrost type in which a refrigeration cycle apparatus is stopped, and a heater defrost type in which heat is generated by a heater installed near a heat exchanger.
  • the air-cooled heat pump chillers employ the hot-gas reverse type defrosting operation.
  • a refrigerant circuit includes, for example, a compressor, an air-heat exchanger, an expansion valve, a water-heat exchanger, a refrigerant tank, and a four-way valve that are connected by refrigerant pipes.
  • the expansion valve provided between the air-heat exchanger and the water-heat exchanger is connected to the circuit in series.
  • the refrigerant tank is installed between the expansion valve and the water-heat exchanger, and is connected in parallel to the refrigerant pipe connecting the expansion valve and the water heat exchanger to each other.
  • the four-way valve is connected so that when one of the suction port side and the discharge port side of the compressor is connected to the air-heat exchanger, the other is connected to the water-heat exchanger, and that the connection may be reversed.
  • the four-way valve is switched so that refrigerant may circulate through the compressor, the water-heat exchanger, the expansion valve, and the air-heat exchanger in the stated order in the heating operation, with the result that hot water is produced in the water-heat exchanger.
  • the four-way valve is switched in the cooling operation so that the refrigerant may circulate through the compressor, the air-heat exchanger, the expansion valve, and the water-heat exchanger in the stated order, with the result that cold water is produced in the water-heat exchanger.
  • frost may be formed on the air-heat exchanger that serves as an evaporator during the heating operation, and hence the hot-gas reverse type defrosting operation is performed.
  • the hot-gas reverse type defrosting operation is a defrosting method involving sending high-temperature refrigerant gas (hot gas) discharged from the compressor to the air-heat exchanger on which frost is formed, to thereby melt the frost by the heat of the high-temperature refrigerant gas.
  • hot gas high-temperature refrigerant gas
  • Patent Literature 1 there is disclosed a refrigerant circuit including a compressor, a condenser, an expansion device, and an evaporator that are connected by refrigerant pipes, in which the expansion device is provided in parallel to a circuit including a flow rate adjusting device and a receiver configured to accumulate surplus refrigerant in the refrigerant circuit that are connected in series.
  • Patent Literature 2 there is disclosed a refrigeration cycle apparatus in which the discharge portion of a compressor and low-pressure refrigerant part of the refrigerant circuit after a solenoid valve are connected to each other by a hot gas bypass, a refrigerant circuit is divided into a low-pressure part and a high-pressure part in performing a defrosting operation, and an accumulator is connected to the suction side of the compressor.
  • Patent Literature 3 there is disclosed a technology for reducing pressure on the high-pressure side in a refrigerant circuit by allowing, when the pressure on the high-pressure side of the refrigerant circuit in operation rises, refrigerant to flow to a refrigerant tank connected between a suction portion of the compressor and a solenoid valve.
  • the refrigerant circuit is configured to adjust a refrigerant flow rate depending on the necessary amount of refrigerant, and during power outage, control of opening the flow rate adjusting device to return refrigerant accumulated in the receiver to the refrigerant circuit is performed.
  • This technology is not conceived for control during a defrosting operation.
  • the hot gas bypass which connects between the solenoid valve and the discharge side of the compressor so that hot gas may be allowed to flow from the solenoid valve to an evaporator, is provided, and during the defrosting operation, defrosting is performed by a circuit in which a valve provided downstream of a condenser is closed to connect the high-pressure side of the compressor and the evaporator to each other.
  • This configuration prevents liquid backflow to the compressor by the accumulator provided between the evaporator and the suction port of the compressor, and requires a space for installing the accumulator.
  • the hot gas bypass is provided for defrosting.
  • the present invention has been made in order to overcome the above-mentioned problems, and it is an object of the present invention to enable suppression of liquid backflow in a refrigerant circuit including a refrigerant tank (high-pressure receiver) during a defrosting operation of the refrigerant circuit.
  • a refrigeration cycle apparatus including the features of claim 1.
  • the sub-expansion valve and the solenoid valve are controlled so that a refrigerant amount in the refrigerant tank may be adjusted, and refrigerant may be discharged to the refrigerant circuit by an amount necessary for the defrosting operation. In this way, liquid backflow to the compressor that occurs during the defrosting operation can be suppressed.
  • Fig. 1 is a schematic diagram of a refrigerant circuit 2 of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • the refrigeration cycle apparatus 1 according to Embodiment 1 is, for example, an air-conditioning apparatus configured to use cold water or hot water, which is obtained by cooling or heating water, for a cooling or heating operation.
  • the refrigeration cycle apparatus 1 corresponds to, for example, an air-cooled heat pump chiller.
  • the refrigerant circuit 2 of the refrigeration cycle apparatus 1 includes a compressor 21, an air-heat exchanger 22 corresponding to a heat source-side heat exchanger of the invention of the subject application, a main-expansion valve 24, a water-heat exchanger 25 corresponding to a use-side heat exchanger of the invention of the subject application, a sub-expansion valve 26, a refrigerant tank 27, a solenoid valve 28, and a four-way valve 29 corresponding to a flow switching valve of the invention of the subject application that are connected by refrigerant pipes.
  • the sub-expansion valve 26, the refrigerant tank 27, and the solenoid valve 28 are connected in series in the refrigerant circuit.
  • the sub-expansion valve 26, the refrigerant tank 27, and the solenoid valve 28, which are connected, are connected in parallel to the main-expansion valve 24 provided between the air-heat exchanger 22 and the water-heat exchanger 25.
  • the four-way valve 29 is connected so that when one of the suction port side and the discharge port side of the compressor 21 is connected to the air-heat exchanger 22, the other may be connected to the water-heat exchanger 25, and that the connection may be reversed.
  • the connection targets may be switched using a flow switching valve other than the four-way valve 29 as long as the respective connection targets of the suction port side and the discharge port side of the compressor 21 are switched to reverse a circulation direction of refrigerant in the refrigerant circuit 2.
  • the main-expansion valve 24 serves as a pressure reducing device in the refrigerant circuit 2.
  • the opening degree of the sub-expansion valve 26 can be switched among a fully-open opening degree, a fully-closed opening degree, and a throttled opening degree through change of its opening degree.
  • the sub-expansion valve 26 allows refrigerant to pass therethrough while the pressure of the refrigerant is not reduced or reduced by a small amount.
  • the sub-expansion valve 26 can block the flow of the refrigerant.
  • the sub-expansion valve 26 with the throttled opening degree serves as a pressure reducing device in the refrigerant circuit 2, as in the main-expansion valve 24.
  • the solenoid valve 28 can be controlled to be open or closed.
  • the solenoid valve 28 When being open, the solenoid valve 28 allows refrigerant to flow therethrough while not reducing the pressure of the refrigerant or reducing the pressure of the refrigerant by a small amount, and when being closed, the solenoid valve 28 can block the flow of the refrigerant.
  • the refrigeration cycle apparatus 1 includes a pressure sensor 3 configured to measure pressure on the high-pressure side of the refrigerant circuit 2. Further, the refrigeration cycle apparatus 1 includes a controller 4. The controller 4 controls the operations of the compressor 21, the four-way valve 29, and the main-expansion valve 24, and controls opening and closing of the sub-expansion valve 26 and the solenoid valve 28 based on a value measured by the pressure sensor 3.
  • the controller 4 comprises a microcomputer, for example. The relationships between the pressure on the high-pressure side of the refrigerant circuit 2, and the opening degree control for the sub-expansion valve 26 and the opening and closing control for the solenoid valve 28 are described later.
  • the air-heat exchanger 22 is provided with a fan 23.
  • the fan 23 is configured to send air outside the refrigeration cycle apparatus 1 (outdoor air) into the air-heat exchanger 22 so that heat may be exchanged between refrigerant and the outdoor air.
  • frost When frost is formed on the air-heat exchanger 22 during the heating operation, the frost prevents air sent by the fan 23 from entering the air-heat exchanger 22, leading to drop in heat exchange efficiency.
  • Refrigerant flowing through the pipes of the refrigerant circuit 2 is compressed in the compressor 21 to have high-temperature and high-pressure, and then enters the four-way valve 29.
  • the four-way valve 29 is switched as indicated by the dotted lines of Fig. 1 at the time of the heating operation, and the high-temperature and high-pressure refrigerant discharged from the discharge port of the compressor 21 flows into the water-heat exchanger 25.
  • the water-heat exchanger 25 serves as a condenser and exchanges heat between water and the refrigerant.
  • the high-temperature and high-pressure refrigerant transfers heat to the water in the water-heat exchanger 25 to be condensed, thereby becoming liquid refrigerant.
  • the liquid refrigerant that has flowed out of the water-heat exchanger 25 is subjected to pressure reduction through the main-expansion valve 24 to become low-temperature and low-pressure two-phase gas-liquid refrigerant.
  • the solenoid valve 28 is generally opened, and hence the refrigerant that has flowed out of the water-heat exchanger 25 also flows to the refrigerant tank 27.
  • the refrigerant tank has a role of accumulating surplus refrigerant during the heating operation.
  • the sub-expansion valve 26 connected to the refrigerant tank 27 has the throttled opening degree, and thus serves as a pressure reducing device for the refrigerant.
  • the refrigerant which is now two-phase gas-liquid refrigerant through the main-expansion valve 24 and the sub-expansion valve 26, flows into the air-heat exchanger 22.
  • the air-heat exchanger 22 serves as an evaporator and exchanges heat between outdoor air and the refrigerant.
  • the low-temperature and low-pressure two-phase gas-liquid refrigerant receives heat from the outdoor air in the air-heat exchanger 22 to become superheat gas.
  • the refrigerant, which is now superheat gas flows into the suction port of the compressor 21 through the four-way valve 29. After that, the refrigerant circulates again in the same route.
  • frost may be formed on the air-heat exchanger 22.
  • the frost formed on the air-heat exchanger 22 inhibits the heat exchange between the outdoor air and the refrigerant in the air-heat exchanger 22, thereby reducing performance for water heating on the water-heat exchanger 25 side.
  • the frost formed on the air-heat exchanger 22 is removed by the defrosting operation.
  • the refrigeration cycle apparatus 1 employs hot-gas reverse type defrosting.
  • the four-way valve 29 is switched as indicated by the solid lines of Fig. 1 .
  • High-temperature and high-pressure gas refrigerant discharged from the discharge port of the compressor 21 flows into the air-heat exchanger 22 on which frost is formed.
  • frost formed on the air-heat exchanger 22 is melted, that is, defrosting is achieved.
  • Fig. 2 is a schematic diagram of a refrigerant circuit 102 of a refrigeration cycle apparatus 101 according to the related art (Comparative Example).
  • the refrigerant circuit 102 of the refrigeration cycle apparatus 101 includes a compressor 11, an air-heat exchanger 12, a main-expansion valve 14, a water-heat exchanger 15, a refrigerant tank 17, and a four-way valve 19 that are connected by refrigerant pipes.
  • the refrigerant tank 17 is connected in parallel to the main-expansion valve 14 provided between the air-heat exchanger 12 and the water-heat exchanger 15.
  • the four-way valve 19 is connected so that when one of the suction port side and the discharge port side of the compressor 11 is connected to the air-heat exchanger 12, the other may be connected to the water-heat exchanger 15, and that the connection may be reversed.
  • the air-heat exchanger 12 is provided with a fan 13.
  • the fan 13 is configured to send air outside the refrigeration cycle apparatus 101 (outdoor air) into the air-heat exchanger 12 so that heat may be exchanged between refrigerant and the outdoor air.
  • the internal volume of an air-heat exchanger is large as compared to a water-heat exchanger.
  • the water heat exchanger 15 which has a relatively small internal volume, serves as a condenser, and hence the necessary amount of refrigerant is small as compared to a cooling operation.
  • surplus refrigerant is generated.
  • refrigerant is accumulated in the refrigerant tank 17. This also occurs in the refrigeration cycle apparatus 1 according to Embodiment 1.
  • the discharge side of the compressor 11 is connected to the air-heat exchanger 12 and the suction side thereof is connected to the water-heat exchanger 15 so that refrigerant may circulate in a direction opposite to that in the heating operation.
  • the entire refrigerant accumulated in the refrigerant tank 17 flows out on a main refrigerant circuit.
  • the amount of refrigerant is larger than a refrigerant amount necessary for the defrosting operation, and the liquid refrigerant accumulated in the refrigerant tank 17 flows into the suction side of the compressor 11 through the water-heat exchanger 15, resulting in liquid backflow.
  • some measures for liquid backflow need to be taken in the refrigeration cycle apparatus 101 according to Comparative Example.
  • Fig. 3 is a diagram of the control flow of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • the controller 4 installed in the refrigeration cycle apparatus 1 receives a value from the pressure sensor 3 configured to measure the pressure on the high-pressure side in the refrigerant circuit 2, for example, pressure in the refrigerant pipe from the discharge port of the compressor 21 to the four-way valve 29, detects a temporal change in pressure on the high-pressure side of the refrigerant circuit 2, and determines whether the high-pressure-side pressure is equal to or higher than reference high-pressure, which corresponds to a defined value of the invention of the subject application, or lower than the reference high-pressure (Control Step S1).
  • the controller 4 closes the solenoid valve 28 (Control Step S2) and fully opens the sub-expansion valve 26 (Control Step S3) so that refrigerant in the refrigerant tank 27 may be discharged into a main circuit 5.
  • the main circuit 5 refers to a circuit portion for circulating refrigerant, in which the compressor 21, the four-way valve 29, the air-heat exchanger 22, the main-expansion valve 24, and the water-heat exchanger 25 are connected by the refrigerant pipes.
  • the refrigerant in the refrigerant tank 27 is discharged to the main circuit 5, and hence shortage of a refrigerant amount in the main circuit 5 is eliminated. There is therefore provided an effect that failures including a superheat operation of the compressor 21 can be avoided.
  • the controller 4 opens the solenoid valve 28 (Control Step S4) and fully closes the sub-expansion valve 26 (Control Step S5) so that refrigerant in the main circuit 5 may be charged to the refrigerant tank 27 from the solenoid valve 28 side.
  • the refrigerant can be discharged to the main circuit 5 by an amount necessary for defrosting, and there is therefore provided an effect that failures including liquid backflow to the compressor 21, which occur due to surplus refrigerant in the main circuit 5, can be avoided.
  • the controller 4 determines whether or not defrosting-operation end conditions are satisfied (Control Step S6). When the defrosting-operation end conditions are not satisfied, the controller 4 returns to Control Step S1 again. When the defrosting-operation end conditions are satisfied, the control for the defrosting operation is ended. Whether or not the defrosting-operation end conditions are satisfied is determined by, for example, determining whether or not the temperature of the air-heat exchanger 22 becomes equal to or higher than a defined value or elapsed time from the start of the defrosting operation becomes equal to or longer than a defined value, or both the conditions are satisfied.
  • Fig. 4 is an explanatory graph for showing the relationship of the operation of the solenoid valve 28 that depends on the elapsed time and change in high-pressure-side pressure in the refrigerant circuit 2 during the defrosting operation .
  • the pressure shown in Fig. 4 is the pressure on the high-pressure side in the refrigerant circuit 2. Specifically, the pressure of refrigerant on the discharge side of the compressor 21, that is, at a point in the section from the compressor 21 to the four-way valve 29 is measured.
  • pressure in the refrigerant circuit 2 increases as time elapses.
  • the controller 4 determines that the pressure is high pressure.
  • the controller 4 determines that the pressure is low pressure.
  • the controller 4 controls the sub-expansion valve 26 and the solenoid valve 28 to be open or closed as described above, based on the determination.
  • the controller 4 can also perform control of closing the solenoid valve 28 and reducing the opening degree of the sub-expansion valve 26 .
  • pressure in the main circuit 5 may increase rapidly, and control of fully closing the sub-expansion valve 26 and opening the solenoid valve 28 is performed again when the high-pressure-side pressure becomes equal to or higher than the reference high-pressure. Consequently, the opening and closing control for the sub-expansion valve 26 and the solenoid valve 28 is required to be frequently performed, resulting in unstable operation.
  • the flow rate of the refrigerant from the refrigerant tank 27 to the main circuit 5 can be controlled, and fluctuations in pressure in the main circuit 5 can be reduced.
  • the frequency at which the sub-expansion valve 26 and the solenoid valve 28 are opened or closed can be reduced, and there is therefore provided an effect that the defrosting operation of the refrigeration cycle apparatus 1 can be stably performed.
  • Embodiment 2 of the present invention to the refrigerant circuit 2 and its control in Embodiment 1, steps of controlling the sub-expansion valve 26 and the solenoid valve 28 are further added after the start of the defrosting operation and before the end of the defrosting operation.
  • points changed from Embodiment 1 are mainly described.
  • Fig. 5 is a diagram of a control flow of the refrigeration cycle apparatus 1 according to Embodiment 1.
  • the refrigeration cycle apparatus 1 performs the heating operation under a state in which the sub-expansion valve 26 is throttled in opening degree and the solenoid valve 28 is opened. At the start of the defrosting operation, the refrigeration cycle apparatus 1 switches the four-way valve 29 so that the circulation direction of refrigerant may be changed. After that, the controller 4 fully opens the sub-expansion valve 26 and closes the solenoid valve 28 (Control Step S0).
  • Control Step S1 to detect a change in pressure on the high-pressure side of the refrigerant circuit 2 with respect to time, and determine whether the high-pressure-side pressure is equal to or higher than the reference high-pressure, which corresponds to the defined value of the invention of the subject application, or lower than the reference high-pressure.
  • the same Control Steps S1 to S6 as in Embodiment 1 are performed.
  • Control Step S1 the control in Control Steps S4 and S5 is performed through Control Step S1.
  • refrigerant in the refrigerant circuit 2 flows into the refrigerant tank 27 through the solenoid valve 28.
  • the amount of refrigerant, which has now high pressure, in the refrigerant circuit 2 is reduced and the pressure in the refrigerant circuit 2 is reduced.
  • the controller 4 opens the sub-expansion valve 26 and closes the solenoid valve 28.
  • the controller 4 determines whether or not the defrosting-operation end conditions are satisfied. When the defrosting-operation end conditions are not satisfied, the controller 4 returns to Control Step S1 again. When the defrosting-operation end conditions are satisfied, the controller 4 performs control of fully opening the sub-expansion valve 26 and closing the solenoid valve 28 (Control Step S7). After that, the four-way valve 29 is switched, and the heating operation is restarted. During the heating operation, the air-heat exchanger 22 side of the refrigerant circuit 2 corresponds to a low-pressure side, but immediately after the start of the heating operation, liquid refrigerant exists in the air-heat exchanger 22 due to the defrosting operation.
  • Timing to proceed to Control Step S7 may be set to time that is a predetermined period of time before the end of the defrosting operation (before the restart of the heating operation) depending on the specifications of the refrigeration cycle apparatus 1, for example.
  • Control Step S7 is ended after the predetermined period of time elapses to end the defrosting control. After that, the heating operation is restarted. Further, for example, a change in pressure in the refrigerant circuit 2 is detected, and the processing proceeds to Control Step S7 when the pressure satisfies predetermined conditions. Control Step S7 is ended to end the defrosting control when the pressure is reduced to the defined value.
  • the refrigerant amount in the main circuit 5 is kept appropriate, and the pressure is also kept at an appropriate value. As a result, it is possible to prevent liquid backflow to the compressor 21 from occurring in switching from the heating operation to the defrosting operation and switching from the defrosting operation to the heating operation.
  • refrigeration cycle apparatus refrigerant circuit 3 pressure sensor 4 controller 5 main circuit 11 compressor 12 air-heat exchanger 13 fan 14 main-expansion valve 15 water-heat exchanger 17 refrigerant tank 18 solenoid valve 19 four-way valve 21 compressor 22 air-heat exchanger 23 fan 24 main-expansion valve 25 water-heat exchanger 26 sub-expansion valve 27 refrigerant tank 28 solenoid valve 29 four-way valve 101 refrigeration cycle apparatus 102 refrigerant circuit

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)

Claims (4)

  1. Kältekreislaufvorrichtung (1), die Folgendes umfasst:
    einen Kühlmittelkreislauf, umfassend einen Kompressor (11), ein Durchflussumschaltventil (19), einen wärmequellenseitigen Wärmetauscher (22), ein Hauptentspannungsventil (24) und einen nutzungsseitigen Wärmetauscher (25), die mittels Kältemittelrohren verbunden sind, und die konfiguriert sind, um einen Abtauvorgang eines Heißgas-Umkehrkreislauftyps durchzuführen,
    einen Drucksensor (3), der konfiguriert ist, um Druck auf einer Hochdruckseite im Kühlmittelkreislauf zu messen; und
    eine Steuerung (4), die konfiguriert ist, um den Kompressor (11), das Durchflussumschaltventil (19) und das Hauptentspannungsventil (24) zu steuern,
    wobei das Hauptentspannungsventil (24) zwischen den wärmequellenseitigen Wärmetauscher (22) und den nutzungsseitigen Wärmetauscher (25) geschaltet ist und mit einer Reihenschaltung parallelgeschaltet ist, in der ein Unterentspannungsventil (26) mit einem variablen Öffnungsgrad, ein Kühlmitteltank, der konfiguriert ist, um überschüssiges Kühlmittel zu sammeln, und ein Solenoid-Ventil (28) in Reihe geschaltet sind,
    wobei die Steuerung (4) konfiguriert ist, um den Öffnungsgrad des Unterentspannungsventils (26) und die Öffnung und Schließung des Solenoid-Ventils (28) auf Basis des durch den Drucksensor (3) gemessenen Drucks zu steuern, und dadurch gekennzeichnet, dass
    wenn der Druck unter einem definierten Wert liegt, das Unterentspannungsventil (26) geöffnet und das Solenoid-Ventil (28) geschlossen wird, wohingegen, wenn der Druck gleich dem definierten Wert ist oder über diesem liegt, das Unterentspannungsventil (26) vollständig geschlossen und das Solenoid-Ventil (28) geöffnet wird.
  2. Kältekreislaufvorrichtung (1), die Folgendes umfasst:
    einen Kühlmittelkreislauf, umfassend einen Kompressor (11), ein Durchflussumschaltventil (19), einen wärmequellenseitigen Wärmetauscher (22), ein Hauptentspannungsventil (24) und einen nutzungsseitigen Wärmetauscher (25), die mittels Kältemittelrohren verbunden sind, und die konfiguriert sind, um einen Abtauvorgang eines Heißgas-Umkehrkreislauftyps durchzuführen,
    einen Drucksensor (3), der konfiguriert ist, um Druck auf einer Hochdruckseite im Kühlmittelkreislauf zu messen; und
    eine Steuerung (4), die konfiguriert ist, um den Kompressor (11), das Durchflussumschaltventil (19) und das Hauptentspannungsventil (24) zu steuern,
    wobei das Hauptentspannungsventil (24) zwischen den wärmequellenseitigen Wärmetauscher (22) und den nutzungsseitigen Wärmetauscher (25) geschaltet ist und mit einer Reihenschaltung parallelgeschaltet ist, in der ein Unterentspannungsventil (26) mit einem variablen Öffnungsgrad, ein Kühlmitteltank, der konfiguriert ist, um überschüssiges Kühlmittel zu sammeln, und ein Solenoid-Ventil (28) in Reihe geschaltet sind,
    wobei die Steuerung (4) konfiguriert ist, um den Öffnungsgrad des Unterentspannungsventils (26) und die Öffnung und Schließung des Solenoid-Ventils (28) auf Basis des durch den Drucksensor (3) gemessenen Drucks zu steuern, und dadurch gekennzeichnet, dass
    wenn der Druck unter einem definierten Wert liegt, der Öffnungsgrad des Unterentspannungsventils (26) verringert und das Solenoid-Ventil (28) geschlossen wird, wohingegen, wenn der Druck gleich dem definierten Wert ist oder über diesem liegt, das Unterentspannungsventil (26) vollständig geschlossen und das Solenoid-Ventil (28) geöffnet wird.
  3. Kältekreislaufvorrichtung (1) nach einem der Ansprüche 1 oder 2, wobei in einem Zeitraum ab dem Beginn des Auftauvorgangs bis zu dem Zeitpunkt, an dem der Druck einen definierten Wert erreicht, das Unterentspannungsventil (26) vollständig geöffnet und das Solenoid-Ventil (28) geschlossen ist.
  4. Kältekreislaufvorrichtung (1) nach einem der Ansprüche 1 bis 3, wobei in einem vorbestimmten Zeitraum vor dem Ende des Auftauvorgangs das Unterentspannungsventil (26) vollständig geöffnet und das Solenoid-Ventil (28) geschlossen ist.
EP15883950.6A 2015-03-04 2015-03-04 Kältekreislaufvorrichtung Active EP3267130B1 (de)

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EP3267130A1 (de) 2018-01-10
EP3267130A4 (de) 2018-11-07
WO2016139783A1 (ja) 2016-09-09
JP6545252B2 (ja) 2019-07-17
JPWO2016139783A1 (ja) 2017-09-14

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