WO2017037771A1 - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
- Publication number
- WO2017037771A1 WO2017037771A1 PCT/JP2015/074365 JP2015074365W WO2017037771A1 WO 2017037771 A1 WO2017037771 A1 WO 2017037771A1 JP 2015074365 W JP2015074365 W JP 2015074365W WO 2017037771 A1 WO2017037771 A1 WO 2017037771A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- refrigerant
- heat exchanger
- valve
- refrigeration cycle
- compressor
- Prior art date
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
- 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
- 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
- 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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/003—Indoor unit with water as a heat sink or heat source
-
- 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
- F25B2345/001—Charging refrigerant to 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
- F25B2345/00—Details for charging or discharging refrigerants; Service stations therefor
- F25B2345/002—Collecting refrigerant 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
- 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
- F25B2400/06—Several compression cycles arranged in parallel
-
- 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
- F25B2400/19—Pumping down refrigerant from one part of the cycle to another part of the cycle, e.g. when the cycle is changed from cooling to heating, or before a defrost cycle is started
-
- 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
- F25B2600/21—Refrigerant outlet evaporator temperature
-
- 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
- F25B2600/2523—Receiver 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
- F25B2700/04—Refrigerant level
-
- 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
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
Definitions
- the present invention relates to a refrigeration cycle apparatus that can be operated by switching between a cooling mode and a heating mode.
- the liquid refrigerant after passing through the decompression device becomes a gas refrigerant in a heat exchanger functioning as an evaporator, and this gas refrigerant is sucked into the compressor.
- the refrigerant sucked by the compressor is in a gas state. This is because if the liquid refrigerant is sucked into the compressor, the compressor may be broken, and the operation efficiency of the refrigeration cycle is reduced.
- liquid refrigerant can be included in the refrigerant after passing through the evaporator.
- the refrigerant is circulated in the same cycle as the cooling mode, that is, the cycle opposite to the heating mode, as the defrosting mode for melting frost attached to the heat exchanger functioning as an evaporator in the heating mode.
- the defrosting mode for melting frost attached to the heat exchanger functioning as an evaporator in the heating mode is reversed, and the heat exchanger functioning as a condenser in the defrost mode functions as an evaporator.
- the evaporation capacity is not stable, and the refrigerant may not be sufficiently gasified and may be liquid-backed.
- the amount of refrigerant required in both modes differs, so the capacity of the heat exchanger that functions as the heat source side heat exchanger is reduced to the load side heat exchanger. Although it may be larger than the heat exchanger that functions as, the possibility of liquid back increases with such a configuration. Therefore, there has been a demand for a refrigeration cycle apparatus that can sufficiently gasify the refrigerant in the evaporator and suppress liquid back.
- an accumulator is provided on the suction side of the compressor, thereby suppressing liquid refrigerant from flowing into the compressor.
- the volume of the accumulator is generally set to about 70% of the total amount of refrigerant circulating in the refrigeration cycle apparatus in order to suppress the inflow of liquid refrigerant into the compressor.
- An accumulator is generally installed in a machine room together with a compressor, a flow path switching device, and the like.
- the volume of the accumulator is large, the machine room is also enlarged. For example, because the space on the rooftop or dedicated site where the machine room is installed is limited, a refrigeration cycle apparatus capable of suppressing liquid back has been desired for miniaturization of the accumulator.
- the present invention has been made against the background of the above-described problems, and provides a refrigeration cycle apparatus capable of suppressing liquid back even in a transient state of the refrigeration cycle.
- the refrigeration cycle apparatus of the present invention includes a compressor, a first heat exchanger, a second heat exchanger connected in series with the first heat exchanger, and having a capacity smaller than that of the first heat exchanger, A first pressure reducing device connected between the first heat exchanger and the second heat exchanger, and a refrigerant discharged from the compressor in the cooling mode and the defrosting mode in the first heat exchanger.
- a flow path switching device for forming a second flow path, and forming a second flow path for flowing the refrigerant discharged from the compressor in the heating mode to the second heat exchanger; the first heat exchanger; and the first pressure reduction
- a refrigerant tank circuit branched from the apparatus and connected between the first pressure reducing device and the second heat exchanger, and provided in parallel with the first pressure reducing device;
- a refrigerant tank and a valve for opening and closing a flow path between the refrigerant tank and the second heat exchanger are connected in series.
- liquid back to the compressor can be suppressed when the defrost mode is switched to the heating mode.
- FIG. 1 It is a circuit block diagram of the refrigerating-cycle apparatus which concerns on Embodiment 1, and has shown the state of the air_conditioning
- 2 is a hardware configuration diagram of the refrigeration cycle apparatus according to Embodiment 1.
- FIG. 4 It is a flowchart explaining the flow of the defrost mode which concerns on Embodiment 1.
- FIG. 4 is a timing chart for explaining the operation of the actuator in the defrost mode according to Embodiment 1. It is a figure explaining the state of the high pressure saturation temperature of the defrost mode which concerns on Embodiment 1, and the suction side superheat degree of a compressor.
- FIG. 10 is a timing chart for explaining the operation of the actuator in the defrosting mode according to the third embodiment.
- FIG. 6 is a hardware configuration diagram of a refrigeration cycle apparatus according to modifications of Embodiments 1 to 3.
- FIG. 6 is a diagram illustrating a refrigerant recovery operation of a refrigerant tank according to modified examples of the first to third embodiments.
- FIG. 6 is a diagram for explaining a configuration example 1 of a refrigerant tank according to a modification of the first to third embodiments.
- FIG. 10 is a diagram for explaining a configuration example 2 of a refrigerant tank according to a modification of the first to third embodiments.
- FIG. 10 is a diagram for explaining a configuration example 3 of a refrigerant tank according to a modification of the first to third embodiments.
- FIG. 6 is a circuit configuration diagram of a refrigeration cycle apparatus according to modifications of Embodiments 1 to 3.
- FIG. 1 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, and shows a state of a cooling mode.
- FIG. 2 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, and shows a state of the heating mode.
- the refrigeration cycle apparatus 1 includes a compressor 2, a flow path switching device 3 provided on the discharge side of the compressor 2, a first heat exchanger 4, and a first pressure reducing device.
- Embodiment 1 functions as a part of a chilling unit in which water in the water circuit 16 heated or cooled by the second heat exchanger 6 is used for indoor air conditioning or the like.
- Compressor 2 sucks and compresses low-pressure refrigerant and discharges it as high-pressure refrigerant.
- the compressor 2 is an inverter compressor, for example, having a variable refrigerant discharge capacity.
- the refrigerant circulation amount in the refrigeration cycle apparatus 1 is controlled by adjusting the discharge capacity of the compressor 2.
- the first decompression device 5 decompresses the high-pressure refrigerant.
- a device including a valve body whose opening degree can be adjusted for example, an electronically controlled expansion valve can be used.
- the flow path switching device 3 connects the discharge side of the compressor 2 to the first heat exchanger 4 and connects the suction side of the compressor 2 to the second heat exchanger 6 so that the refrigerant discharged from the compressor 2
- the first flow path through the first heat exchanger 4 and the discharge side of the compressor 2 is connected to the second heat exchanger 6 and the suction side of the compressor 2 is connected to the first heat exchanger 4
- coolant discharged from the compressor 2 to the 2nd heat exchanger 6 is selectively performed.
- the flow path switching device 3 is a device that has a valve body provided in a pipe through which the refrigerant flows, and switches the flow path of the refrigerant as described above by switching the open / close state of the valve body.
- the first heat exchanger 4 is a refrigerant-air heat exchanger having a flow path through which refrigerant flows. In the first heat exchanger 4, heat is exchanged between the refrigerant flowing through the flow path and the air outside the flow path.
- a blower 11 is provided in the vicinity of the first heat exchanger 4, and heat exchange in the first heat exchanger 4 is promoted by the air from the blower 11.
- the blower 11 is a blower having a variable rotational speed, for example, and the heat absorption amount of the refrigerant in the first heat exchanger 4 is adjusted by adjusting the rotational speed of the blower 11.
- the second heat exchanger 6 is a refrigerant-water heat exchanger having a flow path through which refrigerant flows and a flow path through which water in the water circuit 16 flows. In the second heat exchanger 6, heat exchange is performed between the refrigerant and water.
- the refrigeration cycle apparatus 1 can be operated by switching between cooling and heating.
- the flow path switching device 3 connects the discharge side of the compressor 2 to the first heat exchanger 4 to form a first flow path through which the refrigerant discharged from the compressor 2 flows to the first heat exchanger 4.
- the first heat exchanger 4 functions as a condenser and the second heat exchanger 6 functions as an evaporator.
- the flow path switching device 3 connects the discharge side of the compressor 2 to the second heat exchanger 6 to form a second flow path for flowing the refrigerant discharged from the compressor 2 to the second heat exchanger 6.
- the first heat exchanger 4 functions as an evaporator and the second heat exchanger 6 functions as a condenser.
- the 1st heat exchanger 4 functions as a heat source side heat exchanger
- the 2nd heat exchanger 6 functions as a utilization side heat exchanger. Considering the load required in the cooling mode and the heating mode, the heat exchange capacity of the first heat exchanger 4 is larger than the heat exchange capacity of the second heat exchanger 6.
- the accumulator 7 is a container that stores refrigerant therein, and is installed on the suction side of the compressor 2.
- a pipe through which the refrigerant flows is connected to the upper part of the accumulator 7, and a pipe from which the refrigerant flows out is connected to the lower part, and the refrigerant is gas-liquid separated in the accumulator 7. The gas refrigerant separated from the gas and liquid is sucked into the compressor 2.
- the suction part of the compressor 2 is provided with a suction pressure sensor 8 for detecting the pressure of the refrigerant sucked into the compressor 2, that is, the low-pressure side refrigerant.
- the suction pressure sensor 8 is provided at a position where the pressure of the refrigerant on the low pressure side can be detected, and the position of the suction pressure sensor 8 illustrated is an example.
- the discharge part of the compressor 2 is provided with a discharge pressure sensor 9 for detecting the pressure of the refrigerant discharged from the compressor 2, that is, the high-pressure side refrigerant.
- the discharge pressure sensor 9 is provided at a position where the pressure of the refrigerant on the high-pressure side can be detected, and the position of the discharge pressure sensor 9 illustrated is an example.
- the suction portion of the compressor 2 is provided with a suction temperature sensor 10 that detects the temperature of the refrigerant sucked into the compressor 2, that is, the low-pressure side refrigerant.
- the suction temperature sensor 10 is provided at a position where the temperature of the refrigerant on the low pressure side can be detected, and the position of the suction temperature sensor 10 shown in the figure is an example.
- the suction temperature sensor 10 is provided, for example, in a pipe below the shell of the compressor 2 or on the inlet side of the accumulator 7.
- the refrigeration cycle apparatus 1 is provided with a refrigerant tank circuit 12.
- the refrigerant tank circuit 12 is a circuit that connects between the first heat exchanger 4 and the first pressure reducing device 5 and between the first pressure reducing device 5 and the second heat exchanger 6, It is a circuit provided in parallel with the device 5.
- a second decompression device 13, a refrigerant tank 14, and a valve 15 are connected in series to the refrigerant tank circuit 12 in order from the side closer to the first heat exchanger 4.
- the compressor 2, the first heat exchanger 4, the first pressure reducing device 5, and the second heat exchanger 6 are connected except for the refrigerant tank circuit 12.
- Such a circuit may be referred to as a main circuit.
- the second decompression device 13 decompresses the high-pressure refrigerant.
- a device including a valve body whose opening degree can be adjusted, for example, an electronically controlled expansion valve can be used.
- the refrigerant tank 14 is a container that stores refrigerant therein.
- the valve 15 has a valve body provided in a pipe constituting the refrigerant tank circuit 12, and switches between a conduction state and a non-conduction state of the refrigerant by switching an open / close state of the valve body.
- FIG. 3 is a hardware configuration diagram of the refrigeration cycle apparatus according to the first embodiment.
- the refrigeration cycle apparatus 1 includes a control device 20 that performs overall control, and information detected by the suction pressure sensor 8, the discharge pressure sensor 9, and the suction temperature sensor 10 is input to the control device 20.
- the control device 20 controls operations of the compressor 2, the flow path switching device 3, the first pressure reducing device 5, the second pressure reducing device 13, the valve 15, and the blower 11.
- the control device 20 includes a high-pressure saturation temperature detection unit 21, a superheat degree detection unit 22, and a refrigerant tank liquid amount detection unit 23 as functional blocks.
- the control device 20 has a memory 24.
- the high-pressure saturation temperature detection unit 21 calculates the high-pressure refrigerant on the discharge side of the compressor 2 from the conversion table of the pressure of the high-pressure refrigerant detected by the discharge pressure sensor 9 and the saturation temperature stored in the memory 24 under various pressures.
- the high-pressure saturation temperature that is the saturation temperature of is detected.
- the superheat degree detection unit 22 uses the conversion table of the refrigerant pressure on the suction side of the compressor 2 detected by the suction pressure sensor 8 and the saturation temperature under various pressures stored in the memory 24 to calculate the refrigerant on the suction side. Detect saturation temperature. Further, the superheat degree detection unit 22 detects the superheat degree of the suction part of the compressor 2 by obtaining a difference between the detected saturation temperature and the refrigerant temperature of the suction part of the compressor 2 detected by the suction temperature sensor 10. To do.
- the refrigerant tank liquid amount detection unit 23 includes a superheat degree of the suction portion of the compressor 2 detected by the superheat degree detection unit 22, and a reference superheat degree when the refrigerant tank 14 stored in the memory 24 is full. Based on the above, the amount of liquid in the refrigerant tank 14 is detected.
- the control device 20 is configured by a CPU (also referred to as a central processing unit, a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, or a processor) that executes a program stored in the memory 24.
- a CPU also referred to as a central processing unit, a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, or a processor
- each function executed by the control device 20 is realized by software, firmware, or a combination of software and firmware.
- Software and firmware are described as programs and stored in the memory 24.
- the CPU implements each function of the control device 20 by reading and executing the program stored in the memory 24.
- the memory 24 is a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
- the low-temperature and low-pressure refrigerant exchanges heat with the water flowing through the water circuit 16 in the second heat exchanger 6, rises in temperature, and flows out from the second heat exchanger 6.
- the refrigerant that has flowed out of the second heat exchanger 6 flows into the accumulator 7 via the flow path switching device 3 and is separated into gas and liquid in the accumulator 7.
- the gas refrigerant in the accumulator 7 is sucked into the compressor 2.
- the water flowing through the water circuit 16 is cooled by the refrigerant flowing through the second heat exchanger 6 that is the use side heat exchanger, and the cooled water is used for indoor cooling.
- the optimum refrigerant amount at the rated operation in the cooling mode is larger than the optimum refrigerant amount at the rated operation in the heating mode. For this reason, in the cooling mode, no refrigerant is stored in the refrigerant tank 14, and the entire amount of refrigerant circulates in the refrigeration cycle apparatus 1. In the cooling mode, the second pressure reducing device 13 and the valve 15 are fully closed or nearly fully closed, and the refrigerant does not flow into and out of the refrigerant tank circuit 12.
- the high-temperature and high-pressure refrigerant discharged from the compressor 2 flows into the second heat exchanger 6 via the flow path switching device 3.
- the high-temperature and high-pressure refrigerant exchanges heat with the water flowing through the water circuit 16 in the second heat exchanger 6, drops in temperature, and flows out from the second heat exchanger 6.
- the refrigerant that has flowed out of the second heat exchanger 6 is depressurized by the first pressure reducing device 5 and flows into the first heat exchanger 4 as a low-temperature and low-pressure refrigerant.
- the low-temperature and low-pressure refrigerant exchanges heat with the air blown from the blower 11 in the first heat exchanger 4, rises in temperature, and flows out of the first heat exchanger 4.
- the refrigerant that has flowed out of the first heat exchanger 4 flows into the accumulator 7 via the flow path switching device 3 and is separated into gas and liquid in the accumulator 7.
- the gas refrigerant in the accumulator 7 is sucked into the compressor 2.
- the water flowing through the water circuit 16 is heated by the refrigerant flowing through the second heat exchanger 6 that is the use side heat exchanger, and the heated water is used for indoor heating.
- the second decompression device 13 In the heating mode, the second decompression device 13 is in a fully closed state or nearly closed, and the valve 15 is in a fully open state.
- the optimum refrigerant amount at the rated operation in the heating mode is smaller than the optimum refrigerant amount at the rated operation in the cooling mode. For this reason, surplus refrigerant when operating in the heating mode is stored in the refrigerant tank 14, and the amount of refrigerant circulating in the main circuit in the heating mode is smaller than the amount of refrigerant circulating in the main circuit in the cooling mode.
- the control device 20 controls the degree of superheat of the first decompression device 5. More specifically, the superheat degree detection unit 22 of the control device 20 detects the superheat degree of the refrigerant on the outlet side of the heat exchanger that functions as a condenser, that is, the suction side of the compressor 2, and the control device 20 The opening degree of the first pressure reducing device 5 is controlled so that the detected degree of superheat approaches the target value.
- the refrigeration cycle apparatus 1 When operating in the heating mode, frost may adhere to the outer surface of the pipe of the first heat exchanger 4 functioning as an evaporator. Therefore, the refrigeration cycle apparatus 1 is defrosted to dissolve the attached frost. Operate in mode.
- the flow path switching device 3 connects the discharge side of the compressor 2 to the first heat exchanger 4 and converts the high-temperature refrigerant discharged from the compressor 2 into the first heat exchanger. 4 is used to melt frost with the heat of the refrigerant.
- this defrost mode since the low-temperature refrigerant flows into the second heat exchanger 6 that is the use side heat exchanger, it is desirable to end the defrost mode in as short a time as possible.
- the refrigerant in the refrigerant tank 14 is discharged from the refrigerant tank 14 and circulated to increase the defrosting capability.
- FIG. 4 is a flowchart for explaining the flow of the defrosting mode according to the first embodiment.
- the control device 20 performs a refrigerant discharge operation in which one of the second decompression device 13 and the valve 15 is opened to release the refrigerant in the refrigerant tank 14 (S1). During this refrigerant discharge operation, the refrigerant discharged from the compressor 2 is passed through the first heat exchanger 4.
- the control device 20 determines that the defrosting is completed, and opens both the second decompression device 13 and the valve 15 to collect the refrigerant in the refrigerant tank 14. A refrigerant recovery operation is performed (S3).
- the control device 20 ends the defrost mode and returns to the heating mode.
- the defrosting mode will be further described.
- FIG. 5 is a timing chart for explaining the operation of the actuator in the defrosting mode according to the first embodiment.
- the state of the “flow path switching device” in FIG. 5 indicates which of the first heat exchanger 4 and the second heat exchanger 6 the discharge part of the compressor 2 is connected to.
- FIG. 6 is a diagram for explaining a state of the high-pressure saturation temperature in the defrost mode and the suction side superheat degree of the compressor according to the first embodiment.
- the horizontal axis of the graph in FIG. 6 indicates the elapsed time.
- FIG. 7 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, showing a state of the first refrigerant discharge operation in the defrost mode.
- FIG. 1 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, showing a state of the first refrigerant discharge operation in the defrost mode.
- FIG. 8 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, showing a state of the second refrigerant discharge operation in the defrost mode.
- FIG. 9 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 1, and shows the state of the refrigerant recovery operation in the defrost mode. The operation in the defrosting mode of the first embodiment will be described along FIG. 5 with reference to FIGS. 6 to 9 as appropriate.
- the compressor 2 when in the heating mode, the compressor 2 operates at a capacity determined based on the air conditioning load, and the flow path switching device 3 connects the discharge side of the compressor 2 to the first heat exchanger 4.
- the first decompression device 5 has an opening degree with superheat control.
- the second decompression device 13 of the refrigerant tank circuit 12 is in a fully closed state or nearly fully closed, and the valve 15 is in an open state.
- the second decompression device 13 and the valve 15 are not limited to the example of FIG. 5 as long as the refrigerant tank 14 can be maintained in a full liquid state in the heating mode.
- the refrigeration cycle apparatus 1 in the heating mode is as shown in FIG.
- the defrost mode When the defrost mode is started, first, the first refrigerant discharge operation is performed.
- the flow path switching device 3 connects the discharge side of the compressor 2 to the second heat exchanger 6, and the second pressure reducing device 13 is controlled to be in an open state and the valve 15 is controlled to be in a closed state.
- the opening degree of the second decompression device 13 may be fully open, or may be slightly lower than the fully open position in order to suppress liquid back to the compressor 2.
- the 1st decompression device 5 controls superheat degree also during defrost mode.
- the compressor 2 has an increased operating capacity in order to increase the defrosting capability.
- the capability control of the compressor 2 is not limited.
- the high and low pressures are reversed in accordance with the flow path switching of the flow path switching device 3, so that the high pressure saturation temperature is low.
- the low-pressure saturation temperature also decreases as the high-pressure saturation temperature decreases, the water temperature of the water circuit 16 that flows through the second heat exchanger 6 is high due to the action of the heating mode before the start of the defrosting mode, so that a low differential pressure state is established. .
- the degree of superheat of the suction portion of the compressor 2 is large.
- the refrigerant tank 14 is connected to the high pressure side of the main circuit by closing the valve 15 of the refrigerant tank circuit 12 and opening the second decompression device 13.
- the main circuit is immediately after the low pressure and the high pressure are reversed, and the refrigerant tank 14 connected to the high pressure side in the heating mode until immediately before is in a relatively high pressure state. Released.
- the suction side superheat degree of the compressor 2 rapidly decreases.
- the high-pressure saturation temperature rises to the frost melting temperature (0 ° C.) with the progress of the first refrigerant discharge operation.
- the refrigerant stored in the refrigerant tank 14 also circulates through the main circuit, so that the defrosting capability increases.
- the control device 20 has completed the discharge of the refrigerant in the refrigerant tank 14. Determination is made, and the first refrigerant discharge operation is terminated. As shown in FIG. 5, when the first refrigerant discharge operation is completed, the second decompression device 13 is closed.
- the second pressure reducing device 13 is controlled to be in a closed state and the valve 15 is controlled to be in an open state.
- the compressor 2 maintains a high operating capacity, but in the present invention, the capacity control of the compressor 2 is not limited. Further, the superheat degree control of the first decompression device 5 is continued.
- the refrigerant tank 14 is connected to the low pressure side of the main circuit by opening the valve 15 of the refrigerant tank circuit 12 and closing the second decompression device 13. Due to the pressure difference between the refrigerant tank 14 and the downstream side of the valve 15 (downstream side of the first decompression device 5), the refrigerant remaining in the refrigerant tank 14 is released.
- the melting of the frost attached to the first heat exchanger 4 proceeds, and the high-pressure saturation temperature rises as shown in FIG. Then, as indicated by a point G in FIG. 6, when the high-pressure saturation temperature reaches a threshold value T1 that is a defrosting end determination threshold value, the control device 20 determines that the defrosting is completed and ends the defrosting continuous operation. To do.
- the second pressure reducing device 13 and the valve 15 are controlled to be in the open state.
- the flow path switching device 3 is maintained in a state where the discharge side of the compressor 2 is connected to the second heat exchanger 6.
- the first pressure reducing device 5 is continuously superheated.
- the compressor 2 has a relatively reduced operating capacity.
- the refrigerant flowing from the first heat exchanger 4 branches on the upstream side of the first pressure reducing device 5. Then, the pressure is reduced by the second pressure reducing device 13 to become a liquid refrigerant, and is stored in the refrigerant tank 14.
- the circulating refrigerant mainly gas refrigerant flows out of the refrigerant tank 14 and flows toward the second heat exchanger 6 through the valve 15.
- the circulation speed of the refrigerant is reduced and the refrigerant is easily stored in the refrigerant tank 14.
- the liquid refrigerant flows into the downstream side of the second heat exchanger 6, and the suction side superheat degree of the compressor 2 decreases as indicated by a point H in FIG. Begin to.
- the suction-side superheat degree of the compressor 2 decreases to the threshold value SH3 that is the recovery end determination threshold value as indicated by a point I in FIG. 6, the control device 20 causes the refrigerant tank 14 to become full. The refrigerant recovery operation is terminated.
- the amount of refrigerant circulating in the main circuit is increased, and the defrosting capability can be increased.
- the time for the defrosting operation can be shortened.
- the heating mode when returning from the defrosting mode to the heating mode, the heating mode is started after the refrigerant is collected in the refrigerant tank 14.
- the amount of refrigerant circulating in the main circuit when starting the heating mode liquid back can be suppressed. Therefore, even if the accumulator 7 is reduced in size, a failure due to the liquid back of the compressor 2 can be avoided.
- the configuration example in which the accumulator 7 is provided has been described.
- the liquid back to the downstream side of the evaporator is suppressed as described above. It can also be set as the structure which does not provide.
- the refrigerant tank circuit 12 is connected in parallel with the first pressure reducing device 5, the refrigerant that becomes redundant in the heating mode is stored in the refrigerant tank 14, and the main of the refrigeration cycle apparatus 1 is stored. Do not circulate in the circuit. Thereby, the liquid back
- Embodiment 2 demonstrates the example which performs only a 1st refrigerant
- the configuration of the refrigeration cycle apparatus 1 in the second embodiment is the same as that in the first embodiment, and only the operation in the defrosting mode is different. Therefore, the difference from the first embodiment will be mainly described.
- FIG. 10 is a timing chart for explaining the operation of the actuator in the defrosting mode according to the second embodiment.
- the state of the “flow path switching device” in FIG. 10 indicates whether the discharge side of the compressor 2 is connected to the first heat exchanger 4 or the second heat exchanger 6.
- the defrosting mode of Embodiment 2 only the first refrigerant discharge operation is performed. That is, when the heating mode is switched to the defrosting mode, the second decompression device 13 is opened and the valve 15 is closed. In this way, as shown in FIG.
- the refrigerant tank 14 is connected to the high-pressure side of the main circuit, the refrigerant in the refrigerant tank 14 is released, and the amount of refrigerant circulating in the refrigeration cycle apparatus 1 is increased.
- the defrosting capability in the defrosting mode can be increased.
- Embodiment 3 FIG.
- Embodiment 1 although the example which performs both a 1st refrigerant
- the configuration of the refrigeration cycle apparatus 1 in the second embodiment is the same as that in the first embodiment, and only the operation in the defrosting mode is different. Therefore, the difference from the first embodiment will be mainly described.
- FIG. 11 is a timing chart for explaining the operation of the actuator in the defrosting mode according to the third embodiment.
- the state of the “flow path switching device” in FIG. 11 indicates which of the first heat exchanger 4 and the second heat exchanger 6 the discharge side of the compressor 2 is connected to.
- FIG. 11 in the defrost mode of Embodiment 3, only a 2nd refrigerant
- the refrigerant tank 14 is connected to the low pressure side of the main circuit, the refrigerant in the refrigerant tank 14 is released, and the amount of refrigerant circulating in the refrigeration cycle apparatus 1 is increased.
- the defrosting capability in the defrosting mode can be increased.
- Example of refrigerant tank liquid amount detection As a means for detecting the amount of liquid refrigerant in the refrigerant tank 14, in addition to detection based on the suction side superheat degree of the compressor 2, there are the following means.
- FIG. 12 is a hardware configuration diagram of a refrigeration cycle apparatus according to modifications of the first to third embodiments.
- the refrigeration cycle apparatus according to the modified example includes a liquid amount detection device 17, and the refrigerant tank liquid amount detection unit 23 of the control device 20 is configured to store the liquid in the refrigerant tank 14 based on information input from the liquid amount detection device 17. Detect the amount of refrigerant.
- the refrigerant tank liquid amount detection unit 23 is an elapsed time of the refrigerant recovery operation (either the first refrigerant recovery operation or the second refrigerant recovery operation or both) based on the measurement time input from the liquid amount detection device 17 that is a timer.
- the elapsed time of the refrigerant recovery operation reaches the threshold value, it is determined that the refrigerant tank 14 is full.
- the threshold value for the elapsed time of the refrigerant recovery operation can be obtained in advance by experiments or the like.
- FIG. 13 is a diagram for explaining the refrigerant recovery operation of the refrigerant tank according to the modified examples of the first to third embodiments.
- the vertical axis in FIG. 13 is the high-pressure saturation temperature, and the horizontal axis is the elapsed time.
- the control device 20 temporarily closes the valve 15 with the second decompression device 13 open.
- the control device 20 opens the valve 15.
- valve 15 When the valve 15 is opened, the gas refrigerant in the refrigerant tank 14 is released, the refrigerant is stored in the refrigerant tank 14, and the high-pressure saturation temperature is lowered as the liquid refrigerant is collected in the refrigerant tank 14. Go. When the high-pressure saturation temperature decreases to the threshold value T2b, the control device 20 closes the valve 15 again. As described above, the control device 20 repeats switching of opening and closing of the valve 15 based on the high-pressure saturation temperature.
- the liquid level in the refrigerant tank 14 gradually rises. Then, the time t during which the high-pressure saturation temperature rises from the threshold value T2b to the threshold value T2a becomes shorter as the refrigerant recovery operation time elapses.
- the refrigerant tank liquid level detector 23 counts the time t when the high-pressure saturation temperature rises from the threshold value T2b to the threshold value T2a with the valve 15 closed, based on the time input from the liquid level detector 17 as a timer. To do.
- the refrigerant recovery operation can be performed while enhancing the effect of suppressing the liquid back by detecting the liquid amount in the refrigerant tank 14 while switching the open / close state of the valve 15.
- the refrigerant recovery operation is started when the valve 15 is closed, but the refrigerant recovery operation may be started when the valve 15 is open, and then the open / close state of the valve 15 may be switched.
- liquid level detection device 17 is a liquid level sensor that detects a liquid level.
- a specific example of the liquid level sensor is a float sensor that is provided inside the refrigerant tank 14 and detects the liquid level of the liquid refrigerant in the refrigerant tank 14.
- Another specific example of the liquid level detection center includes a vibrator that transmits ultrasonic waves and includes a receiving unit that receives the transmitted ultrasonic waves, and the inside of the refrigerant tank 14 is based on the time from transmission of ultrasonic waves to reception. It is an ultrasonic sensor which detects the liquid level of the liquid refrigerant.
- liquid level sensor is a temperature sensor such as a thermal resistance detector installed in the height direction on the side surface of the refrigerant tank 14, and the liquid level sensor is based on the difference between detection values of the multiple temperature sensors. Is detected.
- a liquid level sensor is not limited to what was enumerated here.
- the refrigerant tank liquid level detector 23 determines whether or not the refrigerant tank 14 is full based on the noise value (dB) input from the liquid level detector 17 that is a sound collection sensor. . Specifically, when the refrigerant recovery operation is started, almost no liquid refrigerant is stored in the refrigerant tank 14, so that the refrigerant passing through the valve 15 is a gas refrigerant. As the refrigerant recovery operation time elapses, liquid refrigerant accumulates in the refrigerant tank 14, and when the refrigerant tank 14 becomes full, the liquid refrigerant flowing out of the refrigerant tank 14 passes through the valve 15.
- the refrigerant tank liquid level detection unit 23 can determine that the refrigerant tank 14 is full when the noise value (dB) input from the liquid level detection device 17 that is a sound collection sensor decreases to a threshold value. it can.
- valve 15 is a bidirectional that is provided on a pipe connecting the pipe between the first pressure reducing device 5 and the second heat exchanger 6 and the upper part of the refrigerant tank 14. It is a solenoid valve.
- valve 15 is an electronic device that is provided on a pipe connecting the pipe between the first pressure reducing device 5 and the second heat exchanger 6 and the upper part of the refrigerant tank 14 and whose opening degree can be adjusted. Controlled expansion valve.
- Another specific example of the valve 15 includes a one-way solenoid valve and a check valve on a pipe connecting the pipe between the first pressure reducing device 5 and the second heat exchanger 6 and the upper part of the refrigerant tank 14. This is a valve unit provided in parallel.
- FIGS. 14A to 14C are diagrams illustrating a configuration example of the refrigerant tank according to the modified example of the first to third embodiments.
- the lower part of the refrigerant tank 14 and the second decompression device 13 are connected by a first pipe
- the upper part of the refrigerant tank 14 and the valve 15 are connected by a second pipe.
- a first pipe and a second pipe are provided on the top of the refrigerant tank 14, the first pipe is connected to the second pressure reducing device 13, and the second pipe is connected to the valve 15. Yes.
- This configuration example has a function of separating the refrigerant flowing into the refrigerant tank 14 from the second pipe provided in the upper part of the refrigerant tank 14 by using gravity.
- the first pipe inserted in the side surface of the refrigerant tank 14 is connected to the second pressure reducing device 13, and the second pipe inserted into the refrigerant tank 14 from the upper part of the refrigerant tank 14 is valved. 15 is connected.
- the inner surface of the refrigerant tank 14 is cylindrical or tapered.
- the refrigerant flowing from the first pipe inserted into the refrigerant tank 14 from the side surface of the refrigerant tank 14 is swung along the inner surface of the refrigerant tank 14 to be gas-liquid separated and generated in the refrigerant tank 14.
- the gas refrigerant is discharged from the second pipe inserted in the center of the swirling flow.
- the second heat exchanger 6 shown in the first to third embodiments is a refrigerant-water heat in which heat is exchanged between the refrigerant in the refrigeration cycle apparatus 1 and the water in the water circuit 16. It was an exchanger.
- a refrigerant-refrigerant heat exchanger that exchanges heat between the refrigerant in the refrigeration cycle apparatus 1 and the refrigerant in another refrigeration cycle apparatus may be used.
- a refrigerant-air heat exchanger in which heat is exchanged between the refrigerant in the refrigeration cycle apparatus 1 and air may be used.
- FIG. 15 is a circuit configuration diagram of a refrigeration cycle apparatus according to a modification of the first to third embodiments.
- FIG. 15 shows a configuration example of a system including a plurality of systems of refrigeration cycle apparatuses, and the configuration of refrigeration cycle apparatuses of different systems is shown with a suffix A.
- the second decompression devices 13 and 13A provided in the refrigerant tank circuits 12 and 12A can be controlled in synchronization by the same control device 20 sharing a control board.
- the valves 15 and 15A can also be controlled synchronously by the same control device 20 sharing the control board.
- the control board by sharing the control board with the plurality of second pressure reducing devices 13 and 13A or the plurality of valves 15 and 15A, the number of ports of the control board can be reduced.
- the refrigeration cycle apparatus 1 of Embodiments 1 to 3 is connected in series with the compressor 2, the first heat exchanger 4, and the first heat exchanger 4, and the first heat exchanger 4
- the second heat exchanger 6 having a smaller capacity
- the first pressure reducing device 5 connected between the first heat exchanger 4 and the second heat exchanger 6, and the compressor 2 in the cooling mode and the defrosting mode.
- the switching device 3 is branched from the first heat exchanger 4 and the first pressure reducing device 5 and connected between the first pressure reducing device 5 and the second heat exchanger 6, and in parallel with the first pressure reducing device 5.
- the refrigerant tank circuit 12 is provided with a second pressure reducing device 13, a refrigerant tank 14, and a flow path between the refrigerant tank 14 and the second heat exchanger 6.
- the first pressure reducing device 5 adjusts the flow rate of the refrigerant so that the superheat degree of the refrigerant on the suction side of the compressor 2 approaches the target value, and the control device 20 controls the flow path switching device so as to form the first flow path. 3, opens one of the second decompression device 13 and the valve 15 and closes the other, performs a refrigerant discharge operation, and maintains a state where the first flow path is formed after the refrigerant discharge operation.
- the refrigerant recovery operation is performed to open the device 13 and the valve 15.
- the control device 20 opens the second pressure reducing device 13 and closes the valve 15 to transfer the refrigerant in the refrigerant tank 14 to the first heat exchanger 4 and the first heat exchanger 4. You may be comprised so that it may flow in between the decompression devices 5.
- the control device 20 closes the second pressure reducing device 13 and opens the valve 15, and causes the refrigerant in the refrigerant tank 14 to pass through the valve 15 to the first pressure reducing device. 5 may be configured to flow between the second heat exchanger 6 and the second heat exchanger 6.
- the control device 20 opens the second pressure reducing device 13 and closes the valve 15, and transfers the refrigerant in the refrigerant tank 14 to the first heat exchanger 4 and the first pressure reduction. Then, the second pressure reducing device 13 is closed and the valve 15 is opened, and the refrigerant in the refrigerant tank 14 is supplied to the first pressure reducing device 5 and the second heat exchanger 6 via the valve 15. It may be configured to flow in between.
- control device 20 closes the second pressure reducing device 13 and opens the valve 15, and passes the refrigerant in the refrigerant tank 14 through the valve 15 to the first pressure reducing device 5 and the second heat exchanger 6. And then the second decompressor 13 is opened and the valve 15 is closed so that the refrigerant in the refrigerant tank 14 flows between the first heat exchanger 4 and the first decompressor 5. It may be configured.
- the refrigerant in the refrigerant tank 14, which is surplus refrigerant in the heating mode, can be discharged from the refrigerant tank 14 and circulated in the main circuit in the defrosting mode. For this reason, a defrost capability can be increased and a defrost mode can be completed in a short time.
- the refrigerant released from the refrigerant tank 14 can be collected again in the refrigerant tank 14. For this reason, the amount of refrigerant circulating in the main circuit is reduced, and when returning from the defrosting mode to the heating mode, liquid back from the second heat exchanger 6 functioning as an evaporator in the heating mode can be suppressed. it can. For this reason, even if the accumulator 7 is not provided or the accumulator 7 is reduced in size, the failure of the compressor 2 can be suppressed.
- the refrigeration cycle apparatus 1 includes a high-pressure saturation temperature detection unit that detects the saturation temperature of the refrigerant on the discharge side of the compressor 2, and the control device 20 increases the detection temperature of the high-pressure saturation temperature detection unit to the defrosting end determination threshold value. Then, the refrigerant recovery operation may be started.
- the defrosting mode can be terminated in a time following the frost formation amount of the first heat exchanger 4.
- control device 20 may end the refrigerant discharge operation when the superheat degree on the suction side of the compressor 2 decreases to the liquid discharge end determination threshold value.
- the refrigerant discharge operation can be terminated following the refrigerant amount in the refrigerant tank 14.
- control device 20 detects the refrigerant amount in the refrigerant tank 14 based on the degree of superheat on the suction side of the compressor 2, and ends the refrigerant recovery operation based on the detection result of the refrigerant amount in the refrigerant tank 14. May be.
- the refrigerant recovery operation can be terminated following the amount of refrigerant in the refrigerant tank 14. Since the amount of refrigerant in the refrigerant tank 14 is detected based on the degree of superheat on the suction side of the compressor 2 used when controlling various actuators of the refrigeration cycle apparatus 1, it is added to detect the amount of refrigerant in the refrigerant tank 14. It is not necessary to provide the components.
- the refrigeration cycle apparatus 1 includes a liquid amount detection device 17 that detects the amount of liquid in the refrigerant tank 14, and the control device 20 uses the detection result of the refrigerant amount in the refrigerant tank 14 based on the detection value of the liquid amount detection device 17. Based on this, the refrigerant recovery operation may be terminated.
- the liquid amount detection device 17 may include a timer, and the control device 20 may detect the refrigerant amount in the refrigerant tank 14 based on the measurement time of the timer.
- the liquid amount detection device 17 includes a liquid level sensor that detects the liquid level of the refrigerant tank 14, and the control device 20 detects the refrigerant amount in the refrigerant tank 14 based on the detection value detected by the liquid level sensor. Also good.
- the liquid amount detection device 17 may include a sound collection sensor attached to the valve 15, and the control device 20 may detect the amount of refrigerant in the refrigerant tank 14 based on the noise value detected by the sound collection sensor.
- the refrigerant recovery operation can be terminated following the amount of refrigerant in the refrigerant tank 14. Moreover, since the refrigerant
- control device 20 removes the second pressure reducing device 13 and the valve 15 while keeping the state where the first flow path is formed after the refrigerant discharge operation and before the refrigerant recovery operation in the defrost mode. You may perform frost continuation operation.
- the defrosting speed can be increased.
- Refrigeration cycle device 2 Compressor, 3 Channel switching device, 4 First heat exchanger, 5 First decompression device, 6 Second heat exchanger, 7 Accumulator, 8 Suction pressure sensor, 9 Discharge pressure sensor, 10 Suction Temperature sensor, 11 blower, 12 refrigerant tank circuit, 12A refrigerant tank circuit, 13 second decompression device, 13A second decompression device, 14 refrigerant tank, 15 valve, 15A valve, 16 water circuit, 17 fluid quantity detection device, 20 control Device, 21 high pressure saturation temperature detection unit, 22 superheat degree detection unit, 23 refrigerant tank liquid level detection unit, 24 memory.
Abstract
Description
[冷凍サイクル装置の構成]
図1は、実施の形態1に係る冷凍サイクル装置の回路構成図であり、冷房モードの状態を示している。図2は、実施の形態1に係る冷凍サイクル装置の回路構成図であり、暖房モードの状態を示している。図1、図2では、冷媒の流れる経路を太線で示すとともに、冷媒の流れる方向を矢印で示している。図1、図2に示すように、冷凍サイクル装置1は、圧縮機2と、圧縮機2の吐出側に設けられた流路切替装置3と、第一熱交換器4と、第一減圧装置5と、第二熱交換器6と、アキュムレータ7とが配管で接続された冷凍回路を有する。この冷凍回路の内部には、二酸化炭素やR410A等の相変化を伴う冷媒が循環する。実施の形態1で例示する冷凍サイクル装置1は、第二熱交換器6で加熱または冷却された水回路16の水が室内の空調等に利用される、チリングユニットの一部として機能する。
図3は、実施の形態1に係る冷凍サイクル装置のハードウェア構成図である。冷凍サイクル装置1は、全体の制御を司る制御装置20を備え、吸入圧力センサ8、吐出圧力センサ9、及び吸入温度センサ10の検出した情報が、制御装置20に入力される。制御装置20は、圧縮機2、流路切替装置3、第一減圧装置5、第二減圧装置13、弁15、及び送風機11の動作を制御する。
図1を参照して、冷房モードのときの冷媒の流れを説明する。圧縮機2から吐出された高温高圧の冷媒は、流路切替装置3を介して第一熱交換器4に流入する。高温高圧の冷媒は、第一熱交換器4において送風機11から送風される空気と熱交換し、温度低下して第一熱交換器4から流出する。第一熱交換器4から流出した冷媒は、第一減圧装置5で減圧され、低温低圧の冷媒となって第二熱交換器6に流入する。低温低圧の冷媒は、第二熱交換器6において水回路16を流れる水と熱交換し、温度上昇して第二熱交換器6から流出する。第二熱交換器6を流出した冷媒は、流路切替装置3を介してアキュムレータ7に流入し、アキュムレータ7内において気液分離される。アキュムレータ7内のガス冷媒は、圧縮機2に吸入される。
図2を参照して、暖房モードのときの冷媒の流れを説明する。圧縮機2から吐出された高温高圧の冷媒は、流路切替装置3を介して第二熱交換器6に流入する。高温高圧の冷媒は、第二熱交換器6において水回路16を流れる水と熱交換し、温度低下して第二熱交換器6から流出する。第二熱交換器6から流出した冷媒は、第一減圧装置5で減圧され、低温低圧の冷媒となって第一熱交換器4に流入する。低温低圧の冷媒は、第一熱交換器4において送風機11から送風される空気と熱交換し、温度上昇して第一熱交換器4から流出する。第一熱交換器4を流出した冷媒は、流路切替装置3を介してアキュムレータ7に流入し、アキュムレータ7内において気液分離される。アキュムレータ7内のガス冷媒は、圧縮機2に吸入される。
暖房モードで運転している際には、蒸発器として機能する第一熱交換器4の配管の外面に霜が付着することがあるため、付着した霜を溶かすために冷凍サイクル装置1は除霜モードで運転を行う。除霜モードのときには、冷房モードと同様に、流路切替装置3は圧縮機2の吐出側を第一熱交換器4に接続し、圧縮機2から吐出された高温冷媒を第一熱交換器4に流して冷媒の熱で霜を溶かす。この除霜モードでは、利用側熱交換器である第二熱交換器6に低温の冷媒が流入するため、なるべく短時間で除霜モードを終了させることが望ましい。
除霜モードを開始すると、まず、第一冷媒放出運転を行う。第一冷媒放出運転では、流路切替装置3は圧縮機2の吐出側を第二熱交換器6に接続し、第二減圧装置13は開状態、弁15は閉状態に制御される。第二減圧装置13の開度は、全開としてもよいし、また圧縮機2への液バックを抑制するために全開よりもやや低い開度としてもよい。なお、第一減圧装置5は、除霜モードの間も過熱度制御される。圧縮機2は、図5の例では、除霜能力を上げるために運転容量を高めているが、本発明においては圧縮機2の能力制御は限定されない。
ここで、前述のように第一冷媒放出運転で冷媒タンク14はメイン回路の高圧側に冷媒を放出するため、低圧側に冷媒を放出する場合と比べて液バックは抑制されるが、冷媒タンク14内と高圧側とが均圧すると、冷媒タンク14内に冷媒が残留しうる。そこで、さらに除霜能力を高めるため、冷媒タンク14内に残留する冷媒を放出するための第二冷媒放出運転を実行する。
冷媒タンク14からの冷媒の放出が終了すると、除霜継続運転が実行される。図5に示すように、除霜継続運転では、第二減圧装置13及び弁15は閉状態に制御される。圧縮機2及び第一減圧装置5は、それまでと同様の制御が継続される。
除霜モードでは冷媒タンク14内の冷媒を循環させて除霜能力を向上させたが、暖房モードに復帰するときには暖房モードで余剰となる冷媒を冷媒タンク14に回収する冷媒回収運転を行う。
図5に示すように、除霜モードが終了すると、暖房モードを再開する。具体的には、圧縮機2は要求される負荷に応じて能力制御される。除霜モードのときに利用側熱交換器である第二熱交換器6が冷却されていたため、一般には暖房モードを再開したときには圧縮機2は運転能力が高い状態で運転される。流路切替装置3は、圧縮機2の吐出側を第二熱交換器6に接続する。第一減圧装置5は、過熱度制御が継続される。冷媒タンク回路12の第二減圧装置13は、全閉または全閉に近い状態の開度であり、弁15は開状態である。
実施の形態1では、除霜モードにおいて第一冷媒放出運転と第二冷媒放出運転の両方を行う例を説明したが、実施の形態2では、第一冷媒放出運転のみを行う例を説明する。実施の形態2は、冷凍サイクル装置1の構成は実施の形態1と同様であり、除霜モードの動作のみが異なるため、実施の形態1との相違点を中心に説明する。
実施の形態1では、除霜モードにおいて第一冷媒放出運転と第二冷媒放出運転の両方を行う例を説明したが、実施の形態3では、第二冷媒放出運転のみを行う例を説明する。実施の形態2は、冷凍サイクル装置1の構成は実施の形態1と同様であり、除霜モードの動作のみが異なるため、実施の形態1との相違点を中心に説明する。
実施の形態1~3で説明した冷凍サイクル装置1の構成及び制御について、変形例を以下に説明する。
冷媒タンク14内の液冷媒量を検出する手段としては、圧縮機2の吸入側過熱度に基づいて検出するほか、以下のような手段がある。
液量検出装置17の一例は、タイマである。冷媒タンク液量検出部23は、タイマである液量検出装置17から入力される計測時間に基づいて冷媒回収運転(第一冷媒回収運転と第二冷媒回収運転のいずれかまたは両方)の経過時間をカウントし、冷媒回収運転の経過時間が閾値に到達すると、冷媒タンク14内が満液状態になったと判断する。冷媒回収運転の経過時間の閾値は、予め実験等により求めておくことができる。
液量検出装置17の他の一例は、液面レベルを検知する液面センサである。液面センサの具体例は、冷媒タンク14の内部に設けられ、冷媒タンク14内の液冷媒の液面を検出するフロートセンサである。液面検知センタの他の具体例は、超音波を発信する振動子を有するとともに発信した超音波を受信する受信部を備え、超音波の発信から受信までの時間に基づいて、冷媒タンク14内の液冷媒の液面を検出する超音波センサである。液面センサの他の具体例は、冷媒タンク14の側面に高さ方向に複数設置された熱抵抗検知器等の温度センサであって、複数の温度センサの検出値の差に基づいて液面を検出する。なお、液面センサの具体例は、ここに列挙したものに限定されない。
液量検出装置17の他の一例は、弁15に設けられた集音センサである。冷媒タンク液量検出部23は、集音センサである液量検出装置17から入力される騒音値(dB)の値に基づいて、冷媒タンク14内が満液状態であるか否かを判断する。具体的には、冷媒回収運転を開始した時点では、冷媒タンク14内には液冷媒がほとんど貯まっていないので、弁15を通過する冷媒はガス冷媒である。冷媒回収運転の時間経過に伴い、冷媒タンク14内に液冷媒が貯まり、冷媒タンク14が満液状態になると、冷媒タンク14から流出した液冷媒が弁15を通過するようになる。ここで、弁15をガス冷媒が通過するときと、液冷媒が通過するときとでは、騒音値(dB)の値が異なり、液冷媒が通過するときのほうが騒音値(dB)が低い。したがって、冷媒タンク液量検出部23は、集音センサである液量検出装置17から入力される騒音値(dB)が閾値まで低下すると、冷媒タンク14が満液状態になったと判断することができる。
弁15の具体例は、第一減圧装置5と第二熱交換器6との間の配管と、冷媒タンク14の上部とを結ぶ配管上に設けられた、双方向電磁弁である。弁15の他の具体例は、第一減圧装置5と第二熱交換器6との間の配管と、冷媒タンク14の上部とを結ぶ配管上に設けられた、開度を調整可能な電子制御式膨張弁である。弁15の他の具体例は、第一減圧装置5と第二熱交換器6との間の配管と、冷媒タンク14の上部とを結ぶ配管上に、一方向電磁弁と逆止弁とを並列に設けた弁ユニットである。
図14A~図14Cは、実施の形態1~3の変形例に係る冷媒タンクの構成例を説明する図である。図14Aに示す例は、冷媒タンク14の下部と第二減圧装置13とを第一の配管で接続し、冷媒タンク14の上部と弁15とを第二の配管で接続している。
実施の形態1~3で示した第二熱交換器6は、冷凍サイクル装置1内の冷媒と水回路16内の水とが熱交換する冷媒-水熱交換器であった。その他の第二熱交換器6の例として、冷凍サイクル装置1内の冷媒と、別の冷凍サイクル装置の冷媒とが熱交換する冷媒-冷媒熱交換器を用いてもよい。また、第二熱交換器6の他の例として、冷凍サイクル装置1内の冷媒と空気とが熱交換する冷媒-空気熱交換器を用いてもよい。
図15は、実施の形態1~3の変形例に係る冷凍サイクル装置の回路構成図である。図15では、複数系統の冷凍サイクル装置を備えたシステムの構成例を示しており、系統の異なる冷凍サイクル装置の構成には添え字Aを付けて示している。複数系統の冷凍サイクル装置を設けたシステムでは、冷媒タンク回路12、12Aに設けられた第二減圧装置13、13Aを、制御基板を共有する同じ制御装置20で同期して制御することができる。また、弁15、15Aについても、制御基板を共有する同じ制御装置20で同期して制御することができる。このように制御基板を複数の第二減圧装置13、13Aまたは複数の弁15、15Aで共有することで、制御基板のポート数を削減することができる。
Claims (13)
- 圧縮機と、
第一熱交換器と、
前記第一熱交換器と直列に接続され、前記第一熱交換器よりも容量が小さい第二熱交換器と、
前記第一熱交換器と前記第二熱交換器との間に接続された第一減圧装置と、
冷房モード及び除霜モードで前記圧縮機から吐出された冷媒を前記第一熱交換器に流す第一流路を形成し、暖房モードで前記圧縮機から吐出された冷媒を前記第二熱交換器に流す第二流路を形成する流路切替装置と、
前記第一熱交換器と前記第一減圧装置との間から分岐して前記第一減圧装置と前記第二熱交換器との間に接続され、前記第一減圧装置と並列に設けられた冷媒タンク回路であって、第二減圧装置と、冷媒タンクと、前記冷媒タンクと前記第二熱交換器との間の流路を開閉する弁とが直列に接続された冷媒タンク回路と、
前記流路切替装置、前記第二減圧装置、及び前記弁を制御する制御装置と、を備え、
前記除霜モードを開始する際、
前記第一減圧装置は、前記圧縮機の吸入側の冷媒の過熱度を目標値に近づけるように冷媒の流量を調整し、
前記制御装置は、
前記第一流路を形成するように前記流路切替装置を制御し、
前記第二減圧装置と前記弁のうち一方を開き他方を閉じる、冷媒放出運転を行い、
前記冷媒放出運転の後に、前記第一流路が形成された状態を維持したまま、前記第二減圧装置及び前記弁を開く冷媒回収運転を行うように構成されている
冷凍サイクル装置。 - 前記制御装置は、前記冷媒放出運転において、
前記第二減圧装置を開きかつ前記弁を閉じて、前記冷媒タンク内の冷媒を前記第一熱交換器と前記第一減圧装置との間に流入させるように構成されている
請求項1記載の冷凍サイクル装置。 - 前記制御装置は、前記冷媒放出運転において、
前記第二減圧装置を閉じかつ前記弁を開いて、前記冷媒タンク内の冷媒を前記弁を介して前記第一減圧装置と前記第二熱交換器との間に流入させるように構成されている
請求項1記載の冷凍サイクル装置。 - 前記制御装置は、前記冷媒放出運転において、
前記第二減圧装置を開きかつ前記弁を閉じ、前記冷媒タンク内の冷媒を前記第一熱交換器と前記第一減圧装置との間に流入させ、その後、
前記第二減圧装置を閉じかつ前記弁を開いて、前記冷媒タンク内の冷媒を前記弁を介して前記第一減圧装置と前記第二熱交換器との間に流入させるように構成されている
請求項1記載の冷凍サイクル装置。 - 前記制御装置は、前記冷媒放出運転において、
前記第二減圧装置を閉じかつ前記弁を開いて、前記冷媒タンク内の冷媒を前記弁を介して前記第一減圧装置と前記第二熱交換器との間に流入させ、その後、
前記第二減圧装置を開きかつ前記弁を閉じて、前記冷媒タンク内の冷媒を前記第一熱交換器と前記第一減圧装置との間に流入させるように構成されている
請求項1記載の冷凍サイクル装置。 - 前記圧縮機の吐出側の冷媒の飽和温度を検出する高圧飽和温度検出部を備え、
前記制御装置は、
前記高圧飽和温度検出部の検出温度が除霜終了判定閾値まで上昇すると、前記冷媒回収運転を開始する
請求項1~請求項5のいずれか一項に記載の冷凍サイクル装置。 - 前記制御装置は、
前記圧縮機の吸入側の過熱度が液放出終了判定閾値まで低下すると、前記冷媒放出運転を終了する
請求項1~請求項6のいずれか一項に記載の冷凍サイクル装置。 - 前記制御装置は、
前記圧縮機の吸入側の過熱度に基づいて前記冷媒タンク内の冷媒量を検出し、前記冷媒タンク内の冷媒量の検出結果に基づいて、前記冷媒回収運転を終了する
請求項1~請求項7のいずれか一項に記載の冷凍サイクル装置。 - 前記冷媒タンクの液量を検知する液量検出装置を備え、
前記制御装置は、
前記液量検出装置の検出値に基づく前記冷媒タンク内の冷媒量の検出結果に基づいて、前記冷媒回収運転を終了する
請求項1~請求項7のいずれか一項に記載の冷凍サイクル装置。 - 前記液量検出装置は、タイマを備え、
前記制御装置は、前記タイマの計測時間に基づいて前記冷媒タンク内の冷媒量を検出する
請求項9記載の冷凍サイクル装置。 - 前記液量検出装置は、前記冷媒タンクの液面レベルを検知する液面センサを備え、
前記制御装置は、前記液面センサが検出した検出値に基づいて前記冷媒タンク内の冷媒量を検出する
請求項9記載の冷凍サイクル装置。 - 前記液量検出装置は、前記弁に取り付けられた集音センサを備え、
前記制御装置は、前記集音センサが検出した騒音値に基づいて前記冷媒タンク内の冷媒量を検出する
請求項9記載の冷凍サイクル装置。 - 前記制御装置は、前記除霜モードにおいて前記冷媒放出運転の後であって前記冷媒回収運転の前に、
前記第一流路が形成された状態を維持したまま、
前記第二減圧装置及び前記弁を閉じる除霜継続運転を行う
請求項1~請求項12のいずれか一項に記載の冷凍サイクル装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2017537041A JP6463491B2 (ja) | 2015-08-28 | 2015-08-28 | 冷凍サイクル装置 |
CN201580082560.9A CN107923680B (zh) | 2015-08-28 | 2015-08-28 | 制冷循环装置 |
PCT/JP2015/074365 WO2017037771A1 (ja) | 2015-08-28 | 2015-08-28 | 冷凍サイクル装置 |
US15/750,937 US10563894B2 (en) | 2015-08-28 | 2015-08-28 | Refrigeration cycle apparatus |
EP15902897.6A EP3343133A4 (en) | 2015-08-28 | 2015-08-28 | Refrigeration cycle device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2015/074365 WO2017037771A1 (ja) | 2015-08-28 | 2015-08-28 | 冷凍サイクル装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017037771A1 true WO2017037771A1 (ja) | 2017-03-09 |
Family
ID=58187105
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/074365 WO2017037771A1 (ja) | 2015-08-28 | 2015-08-28 | 冷凍サイクル装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US10563894B2 (ja) |
EP (1) | EP3343133A4 (ja) |
JP (1) | JP6463491B2 (ja) |
CN (1) | CN107923680B (ja) |
WO (1) | WO2017037771A1 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107869864A (zh) * | 2017-06-09 | 2018-04-03 | 南京平日制冷科技有限公司 | 一种降压除霜系统 |
JPWO2017061010A1 (ja) * | 2015-10-08 | 2018-06-07 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2022075358A1 (ja) * | 2020-10-06 | 2022-04-14 | 三菱重工サーマルシステムズ株式会社 | 熱源機及びその制御方法 |
WO2024004958A1 (ja) * | 2022-07-01 | 2024-01-04 | ダイキン工業株式会社 | 冷媒量測定システム及び冷媒使用システム |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU2016304989B2 (en) * | 2015-08-11 | 2022-05-12 | Trane International Inc. | Refrigerant recovery and repurposing |
CN115200270A (zh) * | 2022-06-28 | 2022-10-18 | 广东美的制冷设备有限公司 | 空调器、空调器的控制方法、气液分离器、运行控制装置 |
KR20240026394A (ko) * | 2022-08-19 | 2024-02-28 | 삼성전자주식회사 | 공기 조화기 및 그 제어 방법 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0626688A (ja) * | 1992-07-09 | 1994-02-04 | Daikin Ind Ltd | 空気調和装置の運転制御装置 |
JPH11248266A (ja) * | 1998-03-05 | 1999-09-14 | Mitsubishi Electric Corp | 空気調和機及び凝縮器 |
JP2009236447A (ja) * | 2008-03-28 | 2009-10-15 | Daikin Ind Ltd | 冷凍装置 |
JP2010101570A (ja) * | 2008-10-24 | 2010-05-06 | Panasonic Corp | 空気調和機 |
WO2011010473A1 (ja) * | 2009-07-22 | 2011-01-27 | 三菱電機株式会社 | ヒートポンプ装置 |
JP2014119145A (ja) * | 2012-12-14 | 2014-06-30 | Sharp Corp | 空気調和機 |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3950175A (en) | 1973-11-05 | 1976-04-13 | Corning Glass Works | Pore size control in cordierite ceramic |
JPH08313069A (ja) * | 1995-05-19 | 1996-11-29 | Fujitsu General Ltd | 空気調和機 |
JPH10267434A (ja) * | 1997-03-24 | 1998-10-09 | Sanyo Electric Co Ltd | 空気調和機および空調方法 |
JP4115017B2 (ja) * | 1998-11-16 | 2008-07-09 | 三洋電機株式会社 | 冷凍空調装置 |
JP2002156166A (ja) * | 2000-11-20 | 2002-05-31 | Fujitsu General Ltd | 多室形空気調和機 |
JP4001149B2 (ja) | 2005-04-18 | 2007-10-31 | ダイキン工業株式会社 | 空気調和機 |
JP5401563B2 (ja) | 2010-02-15 | 2014-01-29 | 東芝キヤリア株式会社 | チリングユニット |
JP2012202606A (ja) | 2011-03-25 | 2012-10-22 | Topre Corp | 冷媒の回収方法 |
JP6068121B2 (ja) | 2012-12-14 | 2017-01-25 | シャープ株式会社 | 空気調和機 |
US20150267951A1 (en) * | 2014-03-21 | 2015-09-24 | Lennox Industries Inc. | Variable refrigerant charge control |
JP6545252B2 (ja) * | 2015-03-04 | 2019-07-17 | 三菱電機株式会社 | 冷凍サイクル装置 |
WO2017061009A1 (ja) * | 2015-10-08 | 2017-04-13 | 三菱電機株式会社 | 冷凍サイクル装置 |
CN108139118B (zh) * | 2015-10-08 | 2021-07-23 | 三菱电机株式会社 | 制冷循环装置 |
-
2015
- 2015-08-28 US US15/750,937 patent/US10563894B2/en active Active
- 2015-08-28 CN CN201580082560.9A patent/CN107923680B/zh active Active
- 2015-08-28 EP EP15902897.6A patent/EP3343133A4/en active Pending
- 2015-08-28 WO PCT/JP2015/074365 patent/WO2017037771A1/ja active Application Filing
- 2015-08-28 JP JP2017537041A patent/JP6463491B2/ja active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0626688A (ja) * | 1992-07-09 | 1994-02-04 | Daikin Ind Ltd | 空気調和装置の運転制御装置 |
JPH11248266A (ja) * | 1998-03-05 | 1999-09-14 | Mitsubishi Electric Corp | 空気調和機及び凝縮器 |
JP2009236447A (ja) * | 2008-03-28 | 2009-10-15 | Daikin Ind Ltd | 冷凍装置 |
JP2010101570A (ja) * | 2008-10-24 | 2010-05-06 | Panasonic Corp | 空気調和機 |
WO2011010473A1 (ja) * | 2009-07-22 | 2011-01-27 | 三菱電機株式会社 | ヒートポンプ装置 |
JP2014119145A (ja) * | 2012-12-14 | 2014-06-30 | Sharp Corp | 空気調和機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3343133A4 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPWO2017061010A1 (ja) * | 2015-10-08 | 2018-06-07 | 三菱電機株式会社 | 冷凍サイクル装置 |
CN107869864A (zh) * | 2017-06-09 | 2018-04-03 | 南京平日制冷科技有限公司 | 一种降压除霜系统 |
WO2022075358A1 (ja) * | 2020-10-06 | 2022-04-14 | 三菱重工サーマルシステムズ株式会社 | 熱源機及びその制御方法 |
JP2022061250A (ja) * | 2020-10-06 | 2022-04-18 | 三菱重工サーマルシステムズ株式会社 | 熱源機及びその制御方法 |
JP7225178B2 (ja) | 2020-10-06 | 2023-02-20 | 三菱重工サーマルシステムズ株式会社 | 熱源機及びその制御方法 |
WO2024004958A1 (ja) * | 2022-07-01 | 2024-01-04 | ダイキン工業株式会社 | 冷媒量測定システム及び冷媒使用システム |
Also Published As
Publication number | Publication date |
---|---|
US10563894B2 (en) | 2020-02-18 |
US20180231286A1 (en) | 2018-08-16 |
CN107923680A (zh) | 2018-04-17 |
EP3343133A4 (en) | 2018-09-12 |
JP6463491B2 (ja) | 2019-02-06 |
JPWO2017037771A1 (ja) | 2018-04-12 |
CN107923680B (zh) | 2020-06-30 |
EP3343133A1 (en) | 2018-07-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6463491B2 (ja) | 冷凍サイクル装置 | |
US9631826B2 (en) | Combined air-conditioning and hot-water supply system | |
JP6580149B2 (ja) | 冷凍サイクル装置 | |
EP3693680B1 (en) | Refrigeration cycle apparatus | |
US20110314848A1 (en) | Combined air-conditioning and hot-water supply system | |
US11384965B2 (en) | Refrigeration cycle apparatus performing a refrigerant circulation operation using a liquid pump | |
JP4804396B2 (ja) | 冷凍空調装置 | |
JP4905018B2 (ja) | 冷凍装置 | |
JP2007139244A (ja) | 冷凍装置 | |
WO2013065233A1 (ja) | 冷凍サイクル装置およびそれを備えた空気調和機 | |
JP6057871B2 (ja) | ヒートポンプシステム、及び、ヒートポンプ式給湯器 | |
JP4462436B2 (ja) | 冷凍装置 | |
JP6372307B2 (ja) | ヒートポンプ装置 | |
JP6926460B2 (ja) | 冷凍装置 | |
JP2009293887A (ja) | 冷凍装置 | |
JP6641791B2 (ja) | エンジン駆動式空気調和装置 | |
JP2013002678A (ja) | コンデンシングユニットセット及び冷凍装置 | |
JP4023385B2 (ja) | 冷凍装置 | |
JP2014119144A (ja) | 空気調和機 | |
JP2003222412A (ja) | 冷凍装置 | |
JP2013036682A (ja) | 冷凍装置 | |
JP2015172453A (ja) | 温水生成装置 | |
JP2013011367A (ja) | コンデンシングユニットセット、及びこのユニットセットを備えた冷凍装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15902897 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2017537041 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15750937 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2015902897 Country of ref document: EP |