EP3587957B1 - Heat pump and method of controlling heat pump - Google Patents

Heat pump and method of controlling heat pump Download PDF

Info

Publication number
EP3587957B1
EP3587957B1 EP19182535.5A EP19182535A EP3587957B1 EP 3587957 B1 EP3587957 B1 EP 3587957B1 EP 19182535 A EP19182535 A EP 19182535A EP 3587957 B1 EP3587957 B1 EP 3587957B1
Authority
EP
European Patent Office
Prior art keywords
valve
low
heat exchanger
refrigerant
stage compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19182535.5A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3587957C0 (en
EP3587957A1 (en
Inventor
Takayuki Kobayashi
Masashi Maeno
Yohei Katsurayama
Hiroshi Nakayama
Yasuharu TOKUNAGA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kansai Electric Power Co Inc
Chubu Electric Power Co Inc
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Kansai Electric Power Co Inc
Chubu Electric Power Co Inc
Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kansai Electric Power Co Inc, Chubu Electric Power Co Inc, Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Kansai Electric Power Co Inc
Publication of EP3587957A1 publication Critical patent/EP3587957A1/en
Application granted granted Critical
Publication of EP3587957C0 publication Critical patent/EP3587957C0/en
Publication of EP3587957B1 publication Critical patent/EP3587957B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity 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
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02791—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using shut-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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary 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
    • 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
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a heat pump which is provided in a refrigerant circuit and a method of controlling a heat pump.
  • a refrigeration cycle that is, a heat pump
  • a refrigerant circuit through which a refrigerant is repeatedly compressed and expanded and circulates is provided.
  • a refrigerant may be compressed in two stages by a low-stage compressor which compresses the refrigerant and a high-stage compressor further compresses the refrigerant discharged from the low-stage compressor.
  • an evaporator which evaporates the refrigerant on an upstream side of the low-stage compressor is provided.
  • the evaporator is a heat exchanger which performs heat exchange between the refrigerant and a heat medium such as water or air.
  • Document US 2015/168037 A1 discloses a heat pump comprising a low-stage compressor which is configured to compress a refrigerant; a high-stage compressor which is configured to compress the refrigerant discharged from the low-stage compressor; a condenser which is configured to condense the refrigerant discharged from the high-stage compressor; an expansion unit which is configured to depressurize the refrigerant supplied from the condenser; an evaporator which is connected to the expansion unit and configured to evaporate the refrigerant supplied from the expansion unit; a four-way valve which is configured to select a first channel through which the refrigerant discharged from the high-stage compressor is introduced into the condenser and the refrigerant supplied from the evaporator is introduced into the low-stage compressor and a second channel through which the refrigerant discharged from the high-stage compressor is introduced into the evaporator and the refrigerant supplied from the condenser is introduced into the low-stage compressor; and a bypass flow path through which
  • the refrigerant supplied from the evaporator is introduced into the low-stage compressor, and thereafter, is introduced into the high-stage compressor.
  • the amount of heat exchange in the evaporator is not always constant, and may fluctuate due to environmental factors or the like. Accordingly, the temperature of the refrigerant which is introduced from the heat exchanger into the low-stage compressor is not constant, the refrigerant introduced into the low-stage compressor is not optimal for compression in the low-stage compressor, and thus, an efficient operation of the heat pump as a whole cannot be performed.
  • the present invention provides a heat pump and a method of controlling a heat pump capable of being effectively operated by introducing a refrigerant optimal for compression into a low-stage compressor and a high-stage compressor.
  • heat pump as defined in claim 1.
  • the amount of heat exchange in the evaporator fluctuates and the temperature of the refrigerant is changed, and thus, a state of the refrigerant toward the low-stage compressor and the high-stage compressor may not be optimal for compression in the low-stage compressor and the high-stage compressor.
  • the bypass flow path since the bypass flow path is provided, not only the refrigerant supplied from the evaporator can be introduced into the low-stage compressor, but also the refrigerant supplied from the evaporator can bypass the low-stage compressor and can be directly introduced into the high-stage compressor. Therefore, according to a state of the refrigerant flowing out from the evaporator, the channel of the refrigerant can be switched to a compressor capable of performing optimal compression.
  • the refrigerant which is supplied from the evaporator without passing through the four-way valve can be introduced into the low-stage compressor, or can be directly introduced into the high-stage compressor. Accordingly, even in the heat pump which has the four-way valve and in which the distribution channel of the refrigerant can be changed, an additional installation of the bypass flow path is easily performed such that the refrigerant supplied from the evaporator can be introduced into the compressor capable of performing optimum.
  • the channel of the refrigerant can be automatically switched such that the refrigerant is introduced into the compressor capable of performing the optimal compression according to the state of the refrigerant flowing out from the evaporator.
  • the bypass flow path has each bypass section which connects each of the first heat exchanger and the second heat exchanger and each compressor, and thus, the refrigerant can be directly introduced into any compressor from the first heat exchanger and the second heat exchanger. Therefore, optimal compression of the refrigerant can be performed according to various states of the refrigerant.
  • the heat pump may further include a flow path through which the second heat exchanger and the four-way valve are connected to each other, the second low-side bypass section and the second high-side bypass section may be provided to branch off from the flow path, and the heat pump may further include a check valve which is provided to be closer to the four-way valve side in the flow path than to a position at which the second low-side bypass section and the second high-side bypass section branch off from the flow path and allows only a flow of the refrigerant from the four-way valve toward the second heat exchanger.
  • the controller may select the second channel in the four-way valve and may operate the first valve, the second valve, the third valve, and the fourth valve to close the bypass flow path, and may introduce the refrigerant discharged from the high-stage compressor into the second heat exchanger via the check valve.
  • a defrost operation for removing frost attached to the second heat exchanger can be performed.
  • the refrigerant is compressed by the low-stage compressor and the high-stage compressor, and thereafter, the high-temperature and high-pressure refrigerant can be introduced into the second heat exchanger. Accordingly, the defrosting can be effectively performed at a short time in the second heat exchanger. As a result, it is possible to use the second heat exchanger in a wide operation range.
  • the heat pump may further include a valve device which is provided between the condenser and the expansion unit, and the controller may operate the valve device to stop a flow of the refrigerant from the condenser to the expansion unit, may select the second channel in the four-way valve, thereafter, may operate the first valve to open the first low-side bypass section, and may operate the second valve, the third valve, and the fourth valve to close the first high-side bypass section, the second low-side bypass section, and the second high-side bypass section.
  • a valve device which is provided between the condenser and the expansion unit
  • the controller may operate the valve device to stop a flow of the refrigerant from the condenser to the expansion unit, may select the second channel in the four-way valve, thereafter, may operate the first valve to open the first low-side bypass section, and may operate the second valve, the third valve, and the fourth valve to close the first high-side bypass section, the second low-side bypass section, and the second high-side bypass section.
  • the refrigerant discharged from the high-stage compressor is introduced into the second heat exchanger, and thus, the defrost operation for removing frost attached to the second heat exchanger can be performed.
  • the first low-side bypass section is opened by the first valve, and thus, after heat is absorbed to the refrigerant by the first heat exchanger to evaporate the refrigerant, the refrigerant is compressed by the low-stage compressor and the high-stage compressor, and thereafter, the high-temperature and high-pressure refrigerant can be introduced into the second heat exchanger. Accordingly, the defrosting can be effectively performed at a short time in the second heat exchanger. As a result, it is possible to use the second heat exchanger in a wide operation range.
  • the expansion unit may include a first expansion valve which is provided in an inlet of the first heat exchanger between the condenser and the first heat exchanger, and a second expansion valve which is disposed in parallel with the first expansion valve and is provided in an inlet of the second heat exchanger between the condenser and the second heat exchanger
  • the heat pump may further include: a hot gas circuit which is provided to allow a portion between the second heat exchanger and the second expansion valve to communicate with an inlet of the low-stage compressor; a fifth valve which is provided in the hot gas circuit; and a check valve which is provided in the hot gas circuit and allows only a flow of the refrigerant from the inlet of the second heat exchanger toward the inlet of the low-stage compressor
  • the controller may operate the second expansion valve to stop a flow of the refrigerant from the condenser to the second expansion valve and operate the fifth valve to open the hot gas circuit so as to introduce the refrigerant supplied from the second heat exchanger into the low-stage compressor via the
  • the controller By performing the hot gas operation, the refrigerant can circulate between the second heat exchanger, the low-stage compressor, and the high-stage compressor without passing through the condenser.
  • the controller may select the first channel in the four-way valve, in a case where a temperature of the refrigerant flowing out from the first heat exchanger is lower than a temperature of the refrigerant flowing out from the second heat exchanger, the controller may open the first low-side bypass section by the first valve, close the first high-side bypass section by the second valve, close the second low-side bypass section by the third valve, and open the second high-side bypass section by the fourth valve, and in a case where the temperature of the refrigerant flowing out from the first heat exchanger is higher than the temperature of the refrigerant flowing out from the second heat exchanger, the controller may close the first low-side bypass section by the first valve, open the first high-side bypass section by the second valve, open the second low-side bypass section by the third valve, and close the second high-side bypass section by the fourth valve.
  • the refrigerant supplied from the first heat exchanger can be introduced into the low-stage compressor, and the refrigerant supplied from the second heat exchanger can be directly introduced into the high-stage compressor.
  • the refrigerant supplied from the first heat exchanger can be directly introduced into the high-stage compressor, and the refrigerant supplied from the second heat exchanger can be introduced into the low-stage compressor. That is, each of the refrigerant supplied from the first heat exchanger and the refrigerant supplied from the second heat exchanger can be introduced into a compressor suitable for compression of the low-stage compressor and the high-stage compressor.
  • the controller may select the first channel in the four-way valve, in a case where a temperature of the refrigerant flowing out from the condenser, a temperature of the refrigerant flowing out from the first heat exchanger, and a temperature of the refrigerant flowing out from the second heat exchanger are equal to each other, the controller may close the first low-side bypass section by the first valve, open the first high-side bypass section by the second valve, close the second low-side bypass section by the third valve, and open the second high-side bypass section by the fourth valve.
  • the refrigerant supplied from the first heat exchanger can be directly introduced into the high-stage compressor and the refrigerant supplied from the second heat exchanger can be directly introduced into the high-stage compressor. That is, each of the refrigerant supplied from the first heat exchanger and the refrigerant supplied from the second heat exchanger can be introduced into a compressor suitable for compression of the low-stage compressor and the high-stage compressor.
  • the controller may select the first channel in the four-way valve, in a case where a temperature of the refrigerant flowing out from the first heat exchanger and a temperature of the refrigerant flowing out from the second heat exchanger are equal to each other and there is a temperature difference between the temperature of the refrigerant flowing out from the first heat exchanger and the temperature of the refrigerant flowing out from the second heat exchanger, and a temperature of the refrigerant flowing out from the condenser, the controller may open the first low-side bypass section by the first valve, close the first high-side bypass section by the second valve, open the second low-side bypass section by the third valve, and close the second high-side bypass section by the fourth valve.
  • the refrigerant supplied from the first heat exchanger can be introduced into the low-stage compressor and the refrigerant supplied from the second heat exchanger can be introduced into the low-stage compressor. That is, each of the refrigerant supplied from the first heat exchanger and the refrigerant supplied from the second heat exchanger can be introduced into a compressor suitable for compression of the low-stage compressor and the high-stage compressor.
  • the first channel is selected in the four-way valve, and thereafter, in a case where a temperature of the refrigerant flowing out from the first heat exchanger is lower than a temperature of the refrigerant flowing out from the second heat exchanger, the first low-side bypass section is opened by the first valve, the first high-side bypass section is closed by the second valve, the second low-side bypass section is closed by the third valve, and the second high-side bypass section is opened by the fourth valve, and in a case where the temperature of the refrigerant flowing out from the first heat exchanger is higher than the temperature of the refrigerant flowing out from the second heat exchanger, the first low-side bypass section is closed by the first valve, the first high-side bypass section is opened by the second valve, the second low-side bypass section is opened by the third valve, and the second high-side bypass section is closed by the fourth valve.
  • the first channel is selected in the four-way valve, and thereafter, in a case where a temperature of the refrigerant flowing out from the condenser, a temperature of the refrigerant flowing out from the first heat exchanger, and a temperature of the refrigerant flowing out from the second heat exchanger are equal to each other, the first low-side bypass section is closed by the first valve, the first high-side bypass section is opened by the second valve, the second low-side bypass section is closed by the third valve, and the second high-side bypass section is opened by the fourth valve.
  • the first channel is selected in the four-way valve, and thereafter, in a case where a temperature of the refrigerant flowing out from the first heat exchanger and a temperature flowing out from the second heat exchanger are equal to each other and there is a temperature difference between the temperature of the refrigerant flowing out from the first heat exchanger and the temperature of the refrigerant flowing out from the second heat exchanger, and a temperature of the refrigerant flowing out from the condenser, the first low-side bypass section is opened by the first valve, the first high-side bypass section is closed by the second valve, the second low-side bypass section is opened by the third valve, and the second high-side bypass section is closed by the fourth valve.
  • a heat pump 1 includes a refrigerant circuit 2 which is operated in a two-stage compression cycle.
  • the refrigerant circuit 2 has a low-stage compressor 3, a high-stage compressor 4, a condenser 5, an expansion unit 6, and an evaporator 7, and these components are connected to each other in this order by a pipe 10 (flow path).
  • a refrigerant such as carbon dioxide circulates through the refrigerant circuit 2.
  • the refrigerant is not particularly limited to the carbon dioxide.
  • the refrigerant circuit 2 has a four-way valve 11 which is provided between the high-stage compressor 4 and the condenser 5. Moreover, the refrigerant circuit 2 has a bypass flow path 12 through which the refrigerant supplied from the evaporator 7 can be introduced into the low-stage compressor 3 without passing through the four-way valve 11 or through which the refrigerant supplied from the evaporator 7 can be introduced into the high-stage compressor 4 without passing through the low-stage compressor 3. Moreover, the refrigerant circuit 2 has an on-off valve 13 which is provided in the bypass flow path 12 and opens and closes the bypass flow path 12 and a controller 14 which is configured to operate the on-off valve 13 and the four-way valve 11.
  • the low-stage compressor 3 sucks the refrigerant and compresses the refrigerant.
  • the low-stage compressor 3 has a low-stage side accumulator 3a which is configured to perform gas-liquid separation of the refrigerant, a low-stage compressor body 3b which is configured to compress a gas-phase refrigerant supplied from the low-stage side accumulator 3a, and a low-stage side oil separator 3c which removes lubricating oil in the refrigerant discharged from the low-stage compressor body 3b.
  • the high-stage compressor 4 is connected to the low-stage compressor 3 in series and further compresses the refrigerant discharged from the low-stage compressor 3 such that a pressure of the refrigerant increases. More specifically, in the present embodiment, the high-stage compressor 4 has a high-stage compressor body 4b which is configured to compress the refrigerant passing through the low-stage side oil separator 3c and a high-stage side oil separator 4c which removes the lubricating oil in the refrigerant discharged from the high-stage compressor body 4b.
  • the high-stage compressor body 4b is connected to the low-stage side oil separator 3c by an inter-stage pipe 10a.
  • the high-stage compressor body 4b further has a high-stage side accumulator 4a which is connected to an accumulator pipe 10c joining to a middle of the inter-stage pipe 10a and performs gas-liquid separation of the refrigerant flowing in from an upstream side.
  • the high-stage compressor body 4b compresses a gas-phase refrigerant supplied from the high-stage side accumulator 4a in addition to a gas-phase refrigerant supplied from the low-stage side oil separator 3c.
  • the condenser 5 performs heat exchange between a high-temperature and high-pressure refrigerant discharged from the high-stage compressor body 4b of the high-stage compressor 4 and a heat medium such as air or water, and thus, cools and condenses the refrigerant.
  • the condenser 5 is an indoor heat exchanger which is installed in a room.
  • the expansion unit 6 adiabatically expands the refrigerant supplied from the condenser 5 and depressurizes the refrigerant.
  • the expansion unit 6 has a plurality of (three in the present embodiment) expansion valves 6a, 6b, and 6c, corresponds to three heat exchangers of the evaporator 7 described later, and is provided on an upstream side (inlet side) of the evaporator 7.
  • a valve device 15 is provided in a connection pipe 10b between the expansion unit 6 and the condenser 5. The valve device 15 opens and closes a flow path of the connection pipe 10b.
  • a capillary tube or the like may be used instead of the expansion unit 6.
  • the evaporator 7 has a water heat exchanger (first heat exchanger) 31 and an air heat exchanger (second heat exchanger) 32 which is provided in parallel with the water heat exchanger 31.
  • the evaporator 7 is an outdoor heat exchanger which is installed outside a room.
  • the refrigerant which flows out from the condenser 5 and passes through the expansion valve (first expansion valve) 6c is introduced into the water heat exchanger 31, and heat exchange between the refrigerant and the water (first heat medium) is performed by the water heat exchanger 31.
  • the refrigerant which flows out from the condenser 5 and passes through the expansion valves (second expansion valve) 6a and 6b is introduced into the air heat exchanger 32, and heat exchange between the refrigerant and the air (second heat medium) is performed by the air heat exchanger 32.
  • the air heat exchanger 32 has a first air heat exchange unit 32a and a second air heat exchange unit 32b which are provided in parallel with each other.
  • the four-way valve 11 is a valve which has four ports A, B, C, and D.
  • the port D is connected to the high-stage side oil separator 4c by a discharge pipe 10d.
  • the port A and the condenser 5 are connected to each other by a condenser connection pipe 10e.
  • the port B is connected to the low-stage side accumulator 3a by an introduction pipe 10f.
  • the port C is connected to the first air heat exchange unit 32a and the second air heat exchange unit 32b of the air heat exchanger 32 by a heat exchange connection pipe 10g.
  • a check valve 16 which allows only a flow of the refrigerant from the four-way valve 11 toward the air heat exchanger 32 is provided.
  • the bypass flow path 12 has a water low-side bypass section (first low-side bypass section) 41 which connects the water heat exchanger 31 and the low-stage compressor 3 to each other, a water high-side bypass section (first high-side bypass section) 42 which connects the water heat exchanger 31 and the high-stage compressor 4 to each other without passing through the low-stage compressor 3, an air low-side bypass section (second low-side bypass section) 43 which connects the air heat exchanger 32 and the low-stage compressor 3 to each other, and an air high-side bypass section (second high-side bypass section) 44 which connects the air heat exchanger 32 and the high-stage compressor 4 to each other without passing through the low-stage compressor 3.
  • first low-side bypass section water high-side bypass section
  • first high-side bypass section first high-side bypass section
  • second low-side bypass section which connects the air heat exchanger 32 and the low-stage compressor 3 to each other
  • an air high-side bypass section (second high-side bypass section) 44 which connects the air heat exchanger 32 and the high
  • the water low-side bypass section 41 is a pipe which connects the water heat exchanger 31 and a middle of the introduction pipe 10f extending from the port B of the four-way valve 11 to each other.
  • the refrigerant can be introduced from the water heat exchanger 31 into the low-stage side accumulator 3a of the low-stage compressor 3 through the water low-side bypass section 41.
  • the water high-side bypass section 42 is a pipe 10 which is branched off from a middle of the water low-side bypass section 41 and connects the water heat exchanger 31 and the high-stage side accumulator 4a of the high-stage compressor 4.
  • the refrigerant can be directly introduced from the water heat exchanger 31 to the high-stage side accumulator 4a through the water high-side bypass section 42.
  • the air low-side bypass section 43 is a pipe which is branched off from a middle of the heat exchange connection pipe 10g and connects the air heat exchanger 32 and the low-stage side accumulator 3a to each other. Accordingly, the refrigerant can be introduced from the air heat exchanger 32 into the low-stage side accumulator 3a through the air low-side bypass section 43. Accordingly, the check valve 16 is provided to be closer to the four-way valve 11 side than to a position at which the air low-side bypass section 43 branches off from the heat exchange connection pipe 10g, that is, a connection location between the air low-side bypass section 43 and the heat exchange connection pipe 10g.
  • the air high-side bypass section 44 is a pipe which branches off from a middle of the heat exchange connection pipe 10g and connects the air heat exchanger 32 and the high-stage side accumulator 4a to each other. Accordingly, the refrigerant can be directly introduced from the air heat exchanger 32 into the high-stage side accumulator 4a through the air high-side bypass section 44.
  • the air high-side bypass section 44 branches off from the heat exchange connection pipe 10g on a side closer to the air heat exchanger 32 than to the air low-side bypass section 43.
  • the check valve 16 is provided to be closer to the four-way valve 11 side than to a position at which the air high-side bypass section 44 branches off from the heat exchange connection pipe 10g, that is, a connection location between the air high-side bypass section 44 and the heat exchange connection pipe 10g.
  • the on-off valve 13 has a first valve 21 which is provided in the water low-side bypass section 41, a second valve 22 which is provided in the water high-side bypass section 42, a third valve 23 which is provided in the air low-side bypass section 43, and a fourth valve 24 which is provided in the air high-side bypass section 44.
  • Each of the valves 21, 22, 23, and 24 is a two-way valve, and opens and close of a flow path of each of the bypass sections 41, 42, 43, and 44.
  • the controller 14 operates the expansion unit 6, the on-off valve 13, the four-way valve 11, and the valve device 15, and thus, changes a flow direction of the refrigerant in the refrigerant circuit 2.
  • the heat pump 1 of the present embodiment further includes a hot gas circuit 50.
  • the hot gas circuit 50 has an inter-heat exchanger pipe 51 which connects a portion between the first air heat exchange unit 32a and an expansion valve 6a and a portion between the second air heat exchange unit 32b and the expansion valve 6b to each other, and a hot gas pipe 52 which branches off from the inter-heat exchanger pipe 51 and is connected to the accumulator pipe 10c between the low-stage side accumulator 3a and the four-way valve 11.
  • the hot gas circuit 50 is provided such that the portion between the first air heat exchange unit 32a and the expansion valve 6a (and the portion between the second air heat exchange unit 32b and the expansion valve 6b) and an inlet of the low-stage compressor 3 can communicate with each other.
  • a fifth valve 25 and a check valve 27 are provided between a position at which the hot gas pipe 52 branches off from the inter-heat exchanger pipe 51 and the first air heat exchange unit 32a, and a sixth valve 26 and a check valve 27 are provided between a position at which the hot gas pipe 52 branches off the inter-heat exchanger pipe 51 and the second air heat exchanger 32b.
  • the fifth valve 25 and the sixth valve 26 are operated by the controller 14 and thus, opens or closes the flow path of the inter-heat exchanger pipe 51.
  • the check valve 27 causes the refrigerant to flow from the first air heat exchange unit 32a and the second air heat exchange unit 32b to the hot gas pipe 52 through the inter-heat exchanger pipe 51, and conversely, the check valve 27 prevents the refrigerant from flowing from the hot gas pipe 52 to the first air heat exchange unit 32a and the second air heat exchange unit 32b.
  • the sixth valve 26 may be substantially the same as the fifth valve 25.
  • the controller 14 operates the four-way valve 11 such that the port D and the port A communicate with each other.
  • the port B and the port C communicate with each other. Accordingly, the refrigerant discharged from the high-stage compressor 4 is introduced into the condenser 5, and the refrigerant supplied from the evaporator 7 is introduced into the low-stage compressor 3. In this state, a distribution channel of the refrigerant is referred to as a first channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to close the water low-side bypass section 41, close the water high-side bypass section 42, open the air low-side bypass section 43, and close the air high-side bypass section 44. Accordingly, the refrigerant supplied from the air heat exchanger 32 does not pass through the four-way valve 11, and the entire refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3. In addition, the refrigerant supplied from the air heat exchanger 32 is compressed by the low-stage compressor body 3b, and thereafter, the refrigerant is further compressed by the high-stage compressor body 4b, passes through the four-way valve 11, and is introduced into the condenser 5. In the operation pattern 1, the water heat exchanger 31 is not used.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the first channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to open the water low-side bypass section 41, close the water high-side bypass section 42, open the air low-side bypass section 43, and close the air high-side bypass section 44. Accordingly, the refrigerant supplied from the water heat exchanger 31 and the air heat exchanger 32 does not pass through the four-way valve 11, and the entire refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3. In addition, the refrigerant is compressed by the low-stage compressor body 3b, and thereafter, the refrigerant is further compressed by the high-stage compressor body 4b, passes through the four-way valve 11, and is introduced into the condenser 5.
  • the operation pattern 2 is performed in a case where a temperature of the refrigerant which flows out from the water heat exchanger 31 and a temperature of the refrigerant which flows out from the air heat exchanger 32 are equal to each other and there is a temperature difference equal to or more than a predetermined value between the temperature of the refrigerant which flows out from the water heat exchanger 31 and the temperature of the refrigerant which flows out from the air heat exchanger 32, and a temperature of the refrigerant which flows out from the condenser 5.
  • the "temperature of the refrigerant which flows out from the water heat exchanger 31" means a temperature of a refrigerant after the refrigerant flowing out from the first air heat exchange unit 32a and the refrigerant flowing out of the second air heat exchange unit 32b join each other.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the first channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to close the water low-side bypass section 41, open the water high-side bypass section 42, open the air low-side bypass section 43, and close the air high-side bypass section 44. Accordingly, the refrigerant supplied from the water heat exchanger 31 does not pass through the four-way valve 11 and the low-stage compressor 3, and the refrigerant is introduced into the high-stage side accumulator 4a of the high-stage compressor 4. In addition, the refrigerant supplied from the water heat exchanger 31 is compressed by the high-stage compressor body 4b, and thereafter, the refrigerant passes through the four-way valve 11 and is introduced into the condenser 5.
  • the refrigerant supplied from the air heat exchanger 32 does not pass through the four-way valve 11, and the entire refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3.
  • the refrigerant supplied from the air heat exchanger 32 is compressed by the low-stage compressor body 3b, and thereafter, the refrigerant is further compressed by the high-stage compressor body 4b, passes through the four-way valve 11, and is introduced into the condenser 5.
  • the operation pattern 3 is performed in a case where the temperature of the refrigerant which flows out from the water heat exchanger 31 is higher than the temperature of the refrigerant which flows out from the air heat exchanger 32.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the first channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to open the water low-side bypass section 41, close the water high-side bypass section 42, close the air low-side bypass section 43, and close the air high-side bypass section 44. Accordingly, the refrigerant supplied from the water heat exchanger 31 does not pass through the four-way valve 11, and the entire refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3. In addition, the refrigerant supplied from the water heat exchanger 31 is compressed by the low-stage compressor body 3b, and thereafter, the refrigerant is further compressed by the high-stage compressor body 4b, passes through the four-way valve 11, and is introduced into the condenser 5. In the operation pattern 4, the air heat exchanger 32 is not used.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the first channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to open the water low-side bypass section 41, close the water high-side bypass section 42, close the air low-side bypass section 43, and open the air high-side bypass section 44. Accordingly, the refrigerant supplied from the water heat exchanger 31 does not pass through the four-way valve 11, and the entire refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3. In addition, the refrigerant supplied from the water heat exchanger 31 is compressed by the low-stage compressor body 3b, and thereafter, the refrigerant is further compressed by the high-stage compressor body 4b, passes through the four-way valve 11, and is introduced into the condenser 5.
  • the refrigerant supplied from the air heat exchanger 32 does not pass through the four-way valve 11 and the low-stage compressor 3, and the refrigerant is introduced into the high-stage side accumulator 4a.
  • the refrigerant supplied from the air heat exchanger 32 is compressed by the high-stage compressor body 4b, and thereafter, the refrigerant passes through the four-way valve 11 and is introduced into the condenser 5.
  • the operation pattern 5 is performed in a case where the temperature of the refrigerant which flows out from the water heat exchanger 31 is lower than the temperature of the refrigerant which flows out from the air heat exchanger 32.
  • the controller 14 operates the four-way valve 11 such that the port D and the port C communicate with each other.
  • the port B and the port A communicate with each other. Accordingly, the refrigerant discharged from the high-stage compressor 4 is introduced into the evaporator 7, and the refrigerant supplied from the condenser 5 is introduced into the low-stage compressor 3. In this state, a distribution channel of the refrigerant is referred to as a second channel.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to close the water low-side bypass section 41, close the water high-side bypass section 42, close the air low-side bypass section 43, and close the air high-side bypass section 44.
  • a high-temperature and high pressure refrigerant supplied from the high-stage compressor 4 passes through the four-way valve 11, and is introduced into the air heat exchanger 32 through the heat exchange connection pipe 10g and the check valve 16.
  • the refrigerant passes through the air heat exchanger 32, and thus, defrosting of the air heat exchanger 32 is performed, and thus, the refrigerant flows into the expansion valves 6a and 6b which are provided in the first air heat exchange unit 32a and the second air heat exchange unit 32b. Thereafter, the refrigerant is introduced into the condenser 5, passes through the four-way valve 11, and is introduced into the low-stage side accumulator 3a of the low-stage compressor 3. In this case, the water heat exchanger 31 is not used.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the second channel.
  • the controller 14 operates the valve device 15 to close the connection pipe 10b.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to open the water low-side bypass section 41, close the water high-side bypass section 42, close the air low-side bypass section 43, and close the air high-side bypass section 44.
  • the high-temperature and high pressure refrigerant supplied from the high-stage compressor 4 passes through the four-way valve 11, and is introduced into the air heat exchanger 32 through the heat exchange connection pipe 10g.
  • the refrigerant passes through the air heat exchanger 32, and thus, defrosting of the air heat exchanger 32 is performed, and thus, the refrigerant flows into the expansion valves 6a and 6b which are provided in the first air heat exchange unit 32a and the second air heat exchange unit 32b. Thereafter, the refrigerant is introduced into the water heat exchanger 31 and is introduced into the low-stage side accumulator 3a of the low-stage compressor 3 through the water low-side bypass section 41. In this case, the condenser 5 is not used.
  • the controller 14 operates the four-way valve 11 to set the distribution channel of the refrigerant to the second channel.
  • the controller 14 operates the expansion valves 6a and 6b to close the connection pipe 10b.
  • the controller 14 operates the first valve 21 to the fourth valve 24 to close the water low-side bypass section 41, close the water high-side bypass section 42, close the air low-side bypass section 43, and close the air high-side bypass section 44.
  • the controller 14 operates the fifth valve 25 and the sixth valve 26 to open the inter-heat exchanger pipe 51.
  • the high-temperature and high pressure refrigerant supplied from the high-stage compressor 4 passes through the four-way valve 11, and is introduced into the air heat exchanger 32 through the heat exchange connection pipe 10g.
  • the refrigerant passes through the air heat exchanger 32, and thus, defrosting of the air heat exchanger 32 is performed, and thus, the refrigerant flows into the inter-heat exchanger pipe 51. Thereafter, the refrigerant is introduced into the low-stage side accumulator 3a of the low-stage compressor 3 through the hot gas pipe 52. In this case, the air heat exchanger 32 and the water heat exchanger 31 are not used.
  • an amount of heat exchange in the evaporator 7 fluctuates and the temperature of the refrigerant is changed, and thus, a state of the refrigerant toward the low-stage compressor 3 and the high-stage compressor 4 may not be optimal for compression in the low-stage compressor 3 and the high-stage compressor 4.
  • the evaporator 7 has the air heat exchanger 32 including the first air heat exchange unit 32a and the second air heat exchange unit 32b, and the water heat exchanger 31. Accordingly, in each case, the temperature of air or water, which is a medium for performing the heat exchange, fluctuates due to a change of an environment, and thus, the amount of heat exchange of the refrigerant is likely to fluctuate largely.
  • the bypass flow path 12 since the bypass flow path 12 is provided, not only the refrigerant supplied from the evaporator 7 can be introduced into the low-stage compressor 3, but also the refrigerant supplied from the evaporator 7 can bypass the low-stage compressor 3 and can be directly introduced into the high-stage compressor 4. Therefore, according to a state of the refrigerant flowing out from the evaporator 7, the channel of the refrigerant can be switched to a compressor capable of performing optimal compression. Accordingly, it is possible to improve the operation efficiency of the heat pump 1.
  • bypass flow path 12 since the bypass flow path 12 is provided, the refrigerant which is supplied from the evaporator 7 without passing through the four-way valve 11 can be introduced into the low-stage compressor 3, or can be directly introduced into the high-stage compressor 4. Accordingly, even in the heat pump which has the four-way valve 11 and in which the distribution channel of the refrigerant can be changed, an additional installation of the bypass flow path 12 is easily performed such that the refrigerant supplied from the evaporator 7 can be introduced into the compressor capable of performing optimum.
  • the channel of the refrigerant can be automatically switched such that the refrigerant is introduced into the compressor capable of performing the optimal compression according to the state of the refrigerant flowing out from the evaporator 7.
  • the check valve 16 is provided in the heat exchange connection pipe 10g, when the refrigerant passes through the bypass flow path 12 without passing through the four-way valve 11 from the air heat exchanger 32 and is introduced into each of the compressors 3 and 4, the entire refrigerant supplied from the air heat exchanger 32 can flow to the bypass flow path 12 (the air low-side bypass section 43 and the air high-side bypass section 44). Accordingly, the bypass flow path 12 can be fully functional.
  • the defrost operation pattern 1 and the defrost operation pattern 2 can be selected by the controller 14.
  • the defrost operation patterns 1 and 2 the defrosting can be effectively performed at a short time in the air heat exchanger 32.
  • the hot gas operation pattern can be also selected by the controller 14. By performing the hot gas operation, the refrigerant can circulate between the air heat exchanger 32, the low-stage compressor 3, and the high-stage compressor 4 without passing through the condenser 5.
  • the water low-side bypass section 41 may be closed by the first valve 21
  • the water high-side bypass section 42 may be opened by the second valve 22
  • the air low-side bypass section 43 may be closed by the third valve 23
  • the air high-side bypass section 44 may be opened by the fourth valve 24.
  • the refrigerant supplied from the water heat exchanger 31 can be directly introduced into the high-stage compressor 4 and the refrigerant supplied from the air heat exchanger 32 can be directly introduced into the high-stage compressor 4. That is, each of the refrigerant supplied from the water heat exchanger 31 and the refrigerant supplied from the air heat exchanger 32 can be introduced into a compressor suitable for compression of the low-stage compressor 3 and the high-stage compressor 4.
  • controller 14 may not necessarily be provided. In this case, each valve may be operated manually. However, such an embodiment does not fall under the scope of the appended claims.
  • the evaporator 7 is not limited to the combination of the water heat exchanger 31 and the air heat exchanger 32 described above, and the number of heat exchangers is not limited to the above-described case.
  • the evaporator 7 may not have the air heat exchanger 32 and may have two water heat exchangers in parallel. However, such an embodiment does not fall under the scope of the appended claims.
  • various valves may be provided in addition to the above-described various valves.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
EP19182535.5A 2018-06-28 2019-06-26 Heat pump and method of controlling heat pump Active EP3587957B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2018123707A JP7097762B2 (ja) 2018-06-28 2018-06-28 ヒートポンプ、ヒートポンプの制御方法

Publications (3)

Publication Number Publication Date
EP3587957A1 EP3587957A1 (en) 2020-01-01
EP3587957C0 EP3587957C0 (en) 2023-08-30
EP3587957B1 true EP3587957B1 (en) 2023-08-30

Family

ID=67070740

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19182535.5A Active EP3587957B1 (en) 2018-06-28 2019-06-26 Heat pump and method of controlling heat pump

Country Status (3)

Country Link
EP (1) EP3587957B1 (ja)
JP (1) JP7097762B2 (ja)
ES (1) ES2956745T3 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7137094B1 (ja) * 2021-03-29 2022-09-14 ダイキン工業株式会社 熱源ユニットおよび冷凍装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58158273U (ja) * 1982-04-16 1983-10-21 三菱重工業株式会社 冷凍サイクル
JP3407866B2 (ja) * 1998-12-16 2003-05-19 松下電器産業株式会社 空気調和装置
JP4380834B2 (ja) * 1999-03-31 2009-12-09 三洋電機株式会社 ガスヒートポンプエアコン
JP5516712B2 (ja) * 2012-05-28 2014-06-11 ダイキン工業株式会社 冷凍装置
JP2014029237A (ja) * 2012-07-31 2014-02-13 Mitsubishi Heavy Ind Ltd ２段圧縮ヒートポンプシステム
WO2014038059A1 (ja) * 2012-09-07 2014-03-13 三菱電機株式会社 空気調和装置
JP6548890B2 (ja) 2014-10-31 2019-07-24 三菱重工サーマルシステムズ株式会社 冷凍サイクルの制御装置、冷凍サイクル、及び冷凍サイクルの制御方法
JP6020549B2 (ja) * 2014-12-26 2016-11-02 ダイキン工業株式会社 蓄熱式空気調和機

Also Published As

Publication number Publication date
EP3587957C0 (en) 2023-08-30
JP7097762B2 (ja) 2022-07-08
EP3587957A1 (en) 2020-01-01
JP2020003151A (ja) 2020-01-09
ES2956745T3 (es) 2023-12-27

Similar Documents

Publication Publication Date Title
KR100188860B1 (ko) 냉동장치
US8302413B2 (en) Air conditioner
US10006647B2 (en) Air conditioning system with distributor for a plurality of indoor units
US6883346B2 (en) Freezer
US20130104576A1 (en) Air conditioner and method of controlling the same
US20080028773A1 (en) Air conditioner and controlling method thereof
US11022354B2 (en) Air conditioner
JP6160725B1 (ja) 冷凍装置
EP3144606B1 (en) Air conditioner
US11112140B2 (en) Air conditioning apparatus
US11680740B2 (en) Gas-liquid separator and air conditioner having the same
KR101161381B1 (ko) 냉동 사이클 장치
EP3708924A1 (en) Heat pump
EP3587957B1 (en) Heat pump and method of controlling heat pump
JP2001235245A (ja) 冷凍装置
JP2008267653A (ja) 冷凍装置
JP2001235246A (ja) 冷凍装置
CN111919073B (zh) 制冷装置
KR101151529B1 (ko) 냉매시스템
KR20210096521A (ko) 공기 조화 장치
JP2012017951A (ja) 冷凍サイクル装置
EP3480533A1 (en) Refrigeration device
US6640567B2 (en) Air conditioning system with low compression load
EP3705809A1 (en) Heat pump
WO2013073070A1 (ja) 冷凍サイクル装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20200629

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20211118

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

RIC1 Information provided on ipc code assigned before grant

Ipc: F25B 25/00 20060101ALN20230214BHEP

Ipc: F25B 13/00 20060101ALN20230214BHEP

Ipc: F25B 9/00 20060101ALN20230214BHEP

Ipc: F25B 49/02 20060101ALI20230214BHEP

Ipc: F25B 47/02 20060101ALI20230214BHEP

Ipc: F25B 41/00 20060101ALI20230214BHEP

Ipc: F25B 5/02 20060101ALI20230214BHEP

Ipc: F25B 1/10 20060101AFI20230214BHEP

INTG Intention to grant announced

Effective date: 20230316

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

RAP3 Party data changed (applicant data changed or rights of an application transferred)

Owner name: THE KANSAI ELECTRIC POWER CO., INC.

Owner name: CHUBU ELECTRIC POWER CO., INC.

Owner name: MITSUBISHI HEAVY INDUSTRIES THERMAL SYSTEMS, LTD.

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602019035953

Country of ref document: DE

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

U01 Request for unitary effect filed

Effective date: 20230830

U07 Unitary effect registered

Designated state(s): AT BE BG DE DK EE FI FR IT LT LU LV MT NL PT SE SI

Effective date: 20230905

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2956745

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20231227

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231230

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231130

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231230

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20231201

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20230830

U20 Renewal fee paid [unitary effect]

Year of fee payment: 6

Effective date: 20240509

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT