EP3936786B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3936786B1
EP3936786B1 EP19917871.6A EP19917871A EP3936786B1 EP 3936786 B1 EP3936786 B1 EP 3936786B1 EP 19917871 A EP19917871 A EP 19917871A EP 3936786 B1 EP3936786 B1 EP 3936786B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
flow path
circulation direction
controller
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Application number
EP19917871.6A
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English (en)
French (fr)
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EP3936786A4 (de
EP3936786A1 (de
Inventor
Tsuyoshi Sato
Takumi NISHIYAMA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3936786A4 publication Critical patent/EP3936786A4/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2313/031—Sensor arrangements
    • F25B2313/0315—Temperature sensors near the outdoor heat exchanger
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0403—Refrigeration circuit bypassing means for 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0409—Refrigeration circuit bypassing means for 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0417—Refrigeration circuit bypassing means for the subcooler
    • 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
    • F25B2700/21162—Temperatures of a condenser of the refrigerant at the inlet 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
    • F25B2700/2116—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
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator

Definitions

  • the present disclosure relates to a refrigeration cycle apparatus that circulates refrigerant.
  • Japanese Patent Laying-Open No. 2015-87065 discloses an air conditioner in which a part of refrigerant filled in a refrigerant circuit is stored in a plurality of receivers, and the remaining refrigerant is circulated in the refrigerant circuit.
  • the air conditioner by storing the refrigerant in a plurality of receivers, it is possible to adjust an amount of circulated refrigerant to an optimal amount in response to the operating condition, which makes it possible to efficiently perform the air conditioning operation.
  • Document PTL 2 describes an air conditioning system that includes: first and second utilization side heat exchangers and a heat source side heat exchanger respectively connected in series; a compressor connected between the first utilization side heat exchanger and the heat source side heat exchanger; an expansion valve connected between the first utilization side heat exchanger and the second utilization side heat exchanger; a pressure control device connected between the second utilization side heat exchanger and the heat source side heat exchanger; and a bypass valve connected between the expansion valve and the heat source side heat exchanger.
  • the bypass valve provides a variable amount of liquid refrigerant flowing from the expansion valve to the heat source side heat exchanger.
  • the pressure control device and the bypass valve cooperate with each other to keep a temperature of the compressor below a maximum allowable temperature predetermined for the compressor.
  • Document PTL 3 discloses a cooling apparatus that cools a charger for charging a storage battery upon reception of a supply of power from a power supply that includes: a compressor that circulates a refrigerant; a heat exchanger and a heat exchanger that perform heat exchange between the refrigerant and outside air; an expansion valve that reduces a pressure of the refrigerant; a heat exchanger that performs heat exchange between the refrigerant and air-conditioning air; a cooling unit provided on a path along which the refrigerant flows between the heat exchanger and the expansion valve to cool the charger using the refrigerant; a refrigerant passage through which the refrigerant flows between the compressor and the heat exchanger; a refrigerant passage through which the refrigerant flows between the cooling unit and the expansion valve; and a connecting passage connecting the refrigerant passage and the refrigerant passage.
  • Document PTL 4 describes a trigeminy supplies air source heat pump system, including first expansion valve, first heat exchanger, first water pump, cross valve, compressor, second water pump, second heat exchanger, second expansion valve and third heat exchanger, first heat exchanger one end is connected to the third heat exchanger, and the first heat exchanger other end is connected to first heat exchanger, and the first heat exchanger other end is connected to first water pump and cross valve respectively, the third heat exchanger, and second expansion valve one end is connected to the third heat exchanger, and the second expansion valve other end is connected to the cross valve, compressor one end is connected to the cross valve, and the compressor other end is connected to the second heat exchanger, and the second heat exchanger other end is connected to second water pump and cross valve respectively.
  • This trigeminy supplies air source heat pump system reasonable in design, simple structure can realize automatic defrosting after forced air cooling in winter heat exchanger frosts, convenient to use has improved the availability factor.
  • the air conditioner disclosed in PTL 1 in order to adjust the amount of refrigerant that is circulated in the air conditioner (the amount of circulated refrigerant), it is nesseary to dispose a plurality of receivers, which makes the air conditioner larger in size.
  • the present invention has been made in order to solve the above-described problems, and an object of the present invention is to improve the operation efficiency of a refrigeration cycle apparatus while preventing the refrigeration cycle apparatus from becoming larger in size.
  • the refrigeration cycle apparatus circulates refrigerant.
  • the refrigeration cycle apparatus includes, inter alia, a compressor, a first heat exchanger, a second heat exchanger, a third heat exchanger, a first expansion valve, and a first switch.
  • the first switch includes a first port, a second port, and a third port.
  • the first switch switches each of a first flow path and a second flow path between an open state and a closed state.
  • the first flow path communicates the first port and the second port.
  • the second flow path communicates the first port and the third port.
  • the refrigerant When the first flow path is open, the refrigerant is circulated in the first circulation direction through the compressor, the first heat exchanger, the first port, the second port, the second heat exchanger, the first expansion valve, and the third heat exchanger.
  • the second flow path When the second flow path is open, the refrigerant is circulated in the second circulation direction through the compressor, the first heat exchanger, the first port, the third port, the first expansion valve, and the third heat exchanger.
  • the circulation direction of the refrigerant is switched from the first circulation direction to the second circulation direction, a part of the refrigerant is stored in the second heat exchanger.
  • the refrigeration cycle apparatus when the circulation direction of the refrigerant is switched from the first circulation direction to the second circulation direction, a part of the refrigerant is stored in the second heat exchanger, and thereby, it is possible to improve the operation efficiency of the refrigeration cycle apparatus while preventing the refrigeration cycle apparatus from becoming larger in size.
  • Fig. 1 is a functional block diagram illustrating a configuration of an air conditioner 100 which serves as an example of a refrigeration cycle apparatus according to a first embodiment, that does no show all the features of claim 1 but will help to understand the invention as defined in claim 1.
  • the main flow of refrigerant is indicated by a thick line. The same applies to Figs. 4 , 7 to 10 and 14 to be described later.
  • the air conditioner 100 includes an outdoor unit 110 and an indoor unit 120.
  • the air conditioner 100 performs a cooling operation on an indoor space where the indoor unit 120 is installed.
  • the outdoor unit 110 includes a compressor 1, a heat exchanger 3a (a first heat exchanger), a heat exchanger 3b (a second heat exchanger), an expansion valve 4a (a first expansion valve), a switch 7 (a first switch), a controller 50, temperature sensors 11, 12, 13 and 14, and an outdoor fan (not shown).
  • the indoor unit 120 includes a heat exchanger 5 (a third heat exchanger) and an indoor fan (not shown).
  • the controller 50 may be included in the indoor unit 120, or may be provided separately from the outdoor unit 110 and the indoor unit 120.
  • an arrow G1 indicates the direction of gravity around the heat exchanger 3b. The same applies to Figs. 6 to 10 , 14 and 16 to be described later.
  • the switch 7 includes a port P1 (a first port), a port P2 (a second port), and a port P3 (a third port).
  • the switch 7 selectively establishes a flow path F1 (a first flow path) and a flow path F2 (a second flow path).
  • the flow path F1 communicates the ports P1 and P2.
  • the flow path F2 communicates the ports P1 and P3.
  • the refrigerant When the flow path F1 is established, the refrigerant is circulated in a circulation direction (a first circulation direction) through the compressor 1, the heat exchanger 3a, the port P1, the port P2, the heat exchanger 3b, the expansion valve 4a, and the heat exchanger 5.
  • a circulation direction a first circulation direction
  • both the heat exchanger 3a and the heat exchanger 3b function as a condenser
  • the heat exchanger 5 functions as an evaporator.
  • the refrigerant flows into the heat exchanger 3b from a port P4 (a fourth port), and flows out of the heat exchanger 3b from a port P5 (a fifth port).
  • Each of the heat exchangers 3a, 3b and 5 is provided with a fan.
  • the fan blows air to the corresponding heat exchanger so as to increase the heat exchanging efficiency between the refrigerant in the heat exchanger and the air.
  • the fan may be, for example, a linear flow fan, a propeller fan, a turbo fan, or a multiblade fan.
  • a plurality of fans may be provided for each heat exchanger, or a single fan may be provided for a plurality of heat exchangers.
  • the controller 50 obtains, from the temperature sensor 11 which is installed in a middle portion of the heat exchanger 3a, a temperature T11 of the refrigerant flowing in the heat exchanger 3a.
  • the controller 50 obtains, from the temperature sensor 12, a temperature T12 of the refrigerant flowing between the heat exchanger 3a and the switch 7.
  • the controller 50 obtains, from the temperature sensor 13, a temperature T13 of the refrigerant flowing between the heat exchanger 3b and the expansion valve 4a.
  • the controller 50 obtains, from the temperature sensor 14, a temperature T14 of the indoor space where the indoor unit 120 is installed.
  • the controller 50 controls the amount of refrigerant discharged from the compressor 1 per unit time by controlling the driving frequency of the compressor 1 according to a command value fc so as to bring the temperature T14 of the indoor space to a target temperature (which may be set by a user, for example).
  • the controller 50 uses the temperatures T 11 to T13 to calculate the degree of supercooling of the refrigerant flowing out of each heat exchanger which functions as a condenser.
  • the controller 50 controls the opening degree of the expansion valve 4a so as to maintain a pressure difference between a pressure of the refrigerant (high-pressure side refrigerant) which is discharged from the compressor 1 without being depressurized and a pressure of the refrigerant (low-pressure side refrigerant) which has been depressurized before it is sucked into the compressor 1 within a desired range.
  • Fig. 2 is a functional block diagram illustrating the configuration of the controller 50 of Fig. 1 .
  • the controller 50 includes a circuitry 51, a memory 52, and an input/output unit 53.
  • the circuitry 51 may be dedicated hardware, or may be a CPU (Central Processing Unit) that executes programs stored in the memory 52.
  • the circuitry 51 may be, for example, a single circuit, a composite circuit, a programmable processor, a parallelly programmable processor, an ASIC (Application Specific Integrated Circuit), an FGA (Field Programmable Gate Array), or a combination thereof.
  • ASIC Application Specific Integrated Circuit
  • FGA Field Programmable Gate Array
  • the function of the controller 50 may be realized by software, firmware, or a combination of software and firmware.
  • Software or firmware may be described as a program and stored in the memory 52.
  • the circuitry 51 reads a program stored in the memory and executes the program.
  • the memory 52 includes a nonvolatile or volatile semiconductor memory (for example, a RAM (Random Access Memory), a ROM (Read Only Memory), a flash memory, an EPROM (Erasable Programmable Read Only Memory), or an EEPROM (Electrically Erasable Programmable Read Only Memory)), a magnetic disk, a flexible disk, an optical disk, a compact disk, a mini disk, or a DVD (Digital Versatile Disc).
  • the CPU may be a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, a processor, or a DSP (Digital Signal Processor).
  • the operating state of the air conditioner 100 is classified into a high load operation and a low load operation according to the load of the compressor 1.
  • the driving frequency of the compressor 1 during the high load operation is higher than the driving frequency of the compressor 1 during the low load operation.
  • the operating state of the air conditioner 100 is determined from the command value fc sent to the compressor 1. For example, if the driving frequency of the compressor 1 represented by the command value fc is equal to or higher than a reference frequency, the operating state of the air conditioner 100 is determined as a high load operation; and if the driving frequency is lower than the reference frequency, the operating state of the air conditioner 100 is determined as a low load operation.
  • the command value fc may be changed in response to the temperatures T11 to T14.
  • several stepwise temperature ranges (For example, 0°C or more and less than 1°C, 1°C or more and less than 2°C, and 2°C or more and less than 3°C) may be set in advance, and the driving frequency of the compressor 1 may be changed in response to any of the temperature ranges which includes therein the temperature difference between the temperature T14 and the target temperature of the indoor space.
  • Fig. 3 is a diagram schematically illustrating a relationship between an amount of circulated refrigerant and a performance of the air conditioner 100 of Fig. 1 during a high load operation and a low load operation.
  • COP Coefficient of Performance
  • a curve C1 represents the relationship between an amount of circulated refrigerant and a performance of the air conditioner 100 during a high load operation.
  • a curve C2 represents the relationship between an amount of circulated refrigerant and a performance of the air conditioner 100 during a low load operation.
  • M10 represents the total amount of refrigerant sealed in the air conditioner 100. Since a part of the total amount of refrigerant M10 may dissolve in the refrigerator oil stored in the compressor 1, the amount of circulated refrigerant is smaller than the total amount of refrigerant M10.
  • the performance of the air conditioner 100 is maximum when the amount of circulated refrigerant is equal to M1.
  • the total amount of refrigerant M10 in the air conditioner 100 is determined in such a manner that the amount of circulated refrigerant obtained by subtracting the amount of refrigerant dissolved in the refrigerator oil or the like from the total amount of refrigerant M10 is equal to M1.
  • the performance of the air conditioner 100 is maximum when the amount of circulated refrigerant is equal to M2 (M2 ⁇ M1).
  • M2 ⁇ M1 the performance of the air conditioner 100 is not maximum.
  • the air conditioner 100 is started to perform the low load operation from the state as illustrated by a thick line in Fig. 1 , when it is determined that the amount of circulated refrigerant is excessive, the flow path F2 is established as illustrated by a thick line in Fig. 4 to separate the heat exchanger 3b from the circulation path of refrigerant. Since the degree of supercooling of the refrigerant flowing out of a heat exchanger that functions as a condenser increases as the amount of circulated refrigerant increases, whether or not the amount of circulated refrigerant is excessive is determined by the degree of supercooling.
  • the refrigerant is circulated in a circulation direction (a second circulation direction) through the compressor 1, the heat exchanger 3a, the port P1, the port P3, the expansion valve 4a, and the heat exchanger 5.
  • a circulation direction of the refrigerant is switched from the circulation direction of Fig. 1 to the circulation direction of Fig. 4 , a part of the refrigerant is stored in the heat exchanger 3b.
  • the heat exchanger 3b is designed in such a manner that the amount of refrigerant obtained by subtracting the amount of refrigerant stored in the heat exchanger 3b from the amount of circulated refrigerant M1 is equal to M2. Since the heat exchanger 3b in the air conditioner 100 may be used as a container for adjusting the amount of circulated refrigerant, there is no need to dispose another refrigerant container (such as a receiver) in addition to the heat exchanger 3b. According to the air conditioner 100, it is possible to improve the operation efficiency of the air conditioner 100 while preventing the air conditioner 100 from becoming larger in size.
  • a flow path F3 extending from the heat exchanger 3b to the expansion valve 4a is connected to a flow path F4 (a fourth flow path) extending from the port P3 at a connection portion N1 (a specific portion).
  • the connection portion N1 is preferably located at a position higher than the port P5. The height of the connection portion N1 may be the same as the height of the port P5.
  • Fig. 5 is a flowchart illustrating a process to be performed by the controller 50 of Fig. 1 on the switch 7 during a low load operation.
  • the process illustrated in Fig. 5 is called at regular intervals by a main routine (not shown) for performing a comprehensive control on the air conditioner 100.
  • a main routine not shown
  • each step may be simply referred to as "S".
  • the controller 50 determines whether or not the flow path F1 is established in S101. If it is determined that the flow path F1 is established (YES in S101), the controller 50 sets the degree of supercooling of the refrigerant flowing out of the heat exchanger 3b to "SC" in S102, and proceeds the process to S104. If it is determined that the flow path F1 is not established (NO in S101), the controller 50 sets the degree of supercooling of the refrigerant flowing out of the heat exchanger 3a to "SC" in S103, and proceeds the process to S104.
  • the controller 50 determines whether or not the degree of supercooling SC is greater than a reference value SC1. If it is determined that the degree of supercooling SC is greater than the reference value SC1 (YES in S104), the controller 50 proceeds the process to S107. If it is determined that the degree of supercooling SC is equal to or smaller than the reference value SC1 (NO in S104), the controller 50 determines whether or not the degree of supercooling SC is smaller than a reference value SC2 (SC2 ⁇ SC1) in S105. If it is determined that the degree of supercooling SC is equal to or greater than the reference value SC2 (NO in S105), the controller 50 returns the process to the main routine.
  • SC2 reference value SC2
  • the controller 50 establishes the flow path F1 in S106, and proceeds the process to S107.
  • the controller 50 establishes the flow path F2 in S107, and returns the process to the main routine.
  • the reference value SC1 and the reference value SC2 may be appropriately calculated by actual experiments or simulations.
  • the reference value SC1 and the reference value SC2 may be set as an upper limit (for example, 5°C) and a lower limit (for example, 3°C) of an allowable range (for example, 3°C or more and 5°C or less) of design values of the degree of supercooling SC, respectively.
  • connection portion N1 between the flow paths F3 and F4 is established at a position higher than the port P5.
  • a connection portion N1A between the flow paths F3 and F4 may be located at a position lower than the port P5.
  • the height of the portion N2 may be the same as the height of the port P5.
  • the refrigerant sealed in the air conditioner 100 includes, for example, a HFC (Hydro Fluoro Carbon) refrigerant, a HFO (Hydro Fluoro Olefin) refrigerant, a HC (Hydro Carbon) refrigerant, or a non-azeotropic mixture refrigerant (such as R454A).
  • a HFC refrigerant such as R290
  • a non-azeotropic mixture refrigerant such as R454A
  • the refrigeration cycle apparatus According to the refrigeration cycle apparatus according to the first embodiment, it is possible to improve the operation efficiency of the refrigeration cycle apparatus while preventing the refrigeration cycle apparatus from becoming larger in size.
  • the description has been carried out on a refrigeration cycle apparatus that performs a cooling operation on the indoor space where the indoor unit is disposed.
  • a refrigeration cycle apparatus that performs a heating operation and a cooling operation on the indoor space and performs a defrosting operation during the heating operation will be described.
  • Figs. 7 and 8 are functional block diagrams illustrating the configuration of an air conditioner 200 which serves as an example of a refrigeration cycle apparatus according to the second embodiment and a flow of refrigerant during a cooling operation and a defrosting operation.
  • the air conditioner 200 is different from the air conditioner 100 illustrated in Fig. 1 in that the air conditioner 200 further includes a four-way valve 2 (a second switch), an expansion valve 4b (a second expansion valve), temperature sensors 15 and 16, and a controller 50B instead of the controller 50.
  • the other components are the same, and the description thereof will not be repeated.
  • the expansion valve 4b that is fully opened is indicated by a dotted line. The same applies to Fig. 9 to be described later.
  • the expansion valve 4b is connected between the heat exchanger 3a and the port P1.
  • the controller 50B fully opens the expansion valve 4b so that both the heat exchanger 3a and the heat exchanger 3b function as a condenser.
  • the controller 50B controls the expansion valves 4a and 4b by adjusting the opening degrees of the expansion valves 4a and 4b so as to maintain the pressure difference between the high-pressure side refrigerant and the low-pressure side refrigerant within a desired range.
  • the expansion valve 4a or the expansion valve 4b may be fully opened.
  • the controller 50B controls the four-way valve 2 to switch the circulation direction of the refrigerant.
  • the process illustrated in Fig. 5 is performed.
  • Figs. 9 and 10 are functional block diagrams illustrating a configuration of an air conditioner 200 which serves as an example of a refrigeration cycle apparatus according to the second embodiment and a flow of refrigerant during a heating operation.
  • the refrigerant is circulated in a circulation direction (a third circulation direction) opposite to the circulation direction illustrated in Fig. 7 .
  • both the heat exchanger 3a and the heat exchanger 3b function as an evaporator.
  • the controller 50B fully opens the expansion valve 4b.
  • the controller 50B controls the expansion valves 4a and 4b by controlling the opening degrees of the expansion valves 4a and 4b so as to maintain the pressure difference between the high-pressure side refrigerant and the low-pressure side refrigerant within a desired range.
  • the controller 50B uses temperatures T15 and T16 to calculate the degree of supercooling of the refrigerant flowing out of the heat exchanger 5.
  • Fig. 11 is a flowchart illustrating a process to be performed by the controller 50B of Fig. 9 on the switch 7 during a low load operation.
  • the process illustrated in Fig. 11 is called at regular intervals by a main routine (not shown) for performing a comprehensive control on the air conditioner 200.
  • the controller 50B determines whether or not the degree of supercooling SC is greater than a reference value SC3 in S201. If it is determined that the degree of supercooling SC is greater than the reference value SC3 (YES in S201), the controller 50B proceeds the process to S204. If it is determined that the degree of supercooling SC is equal to or smaller than the reference value SC3 (NO in S201), the controller 50B determines whether or not the degree of supercooling SC is smaller than a reference value SC4 (SC4 ⁇ SC3) in S202. If it is determined that the degree of supercooling SC is equal to or greater than the reference value SC4 (NO in S202), the controller 50B returns the process to the main routine.
  • SC4 reference value SC4
  • the controller 50B establishes the flow path F1 in S203, and proceeds the process to S204.
  • the controller 50B establishes the flow path F2 in S204, and returns the process to the main routine.
  • the reference value SC3 and the reference value SC4 are appropriately calculated by actual experiments or simulations.
  • the reference value SC3 and the reference value SC4 may be set as an upper limit (for example, 3°C) and a lower limit (for example, 1°C) of an allowable range (for example, 1°C or more and 3°C or less) of design values of the degree of supercooling SC, respectively.
  • Fig. 12 is a flowchart illustrating an exemplary defrosting determination process to be performed by the controller 50B during the heating operation.
  • the controller 50B determines whether or not a condition for starting a defrosting operation on the heat exchanger 3b is satisfied in S211.
  • a condition for starting a defrosting operation on the heat exchanger 3b a condition in which the temperature T13 is lower than a reference temperature Ds1 (for example, - 3°C) may be given. If it is determined that the condition for starting a defrosting operation on the heat exchanger 3b is not satisfied (NO in S211), the controller 50B returns the process to the main routine.
  • a reference temperature Ds1 for example, - 3°C
  • the controller 50B determines whether or not a condition for starting a defrosting operation on the heat exchanger 3a is satisfied in S212.
  • a condition for starting a defrosting operation on the heat exchanger 3a a condition in which the temperature T11 is lower than a reference temperature Ds2 (for example, -3°C) may be given. If it is determined that the condition for starting a defrosting operation on the heat exchanger 3a is not satisfied (NO in S212), the controller 50B returns the process to the main routine. If it is determined that the condition for starting a defrosting operation on the heat exchanger 3a is satisfied (YES in S212), the controller 50B proceeds the process to S213.
  • the controller 50B establishes the flow path F1, and proceeds the process to S214.
  • the controller 50B fully opens the expansion valve 4b in S214, and proceeds the process to S215.
  • the controller 50B switches the circulation direction of the refrigerant to the circulation direction as illustrated in Fig. 7 , and returns the process to the main routine.
  • a reverse defrosting operation is started.
  • both the heat exchanger 3a and the heat exchanger 3b function as a condenser.
  • the heat exchangers 3a and 3b are defrosted by the condensation heat released from the refrigerant.
  • Fig. 13 is a flowchart illustrating a process to be performed by the controller 50B of Fig. 7 during the reverse defrosting operation.
  • the controller 50B determines whether or not a condition for finishing a defrosting operation on the heat exchanger 3a is satisfied in S221.
  • a condition for finishing a defrosting operation on the heat exchanger 3a a condition in which the temperature T11 is higher than a reference temperature Df1 (for example, 0°C) may be given. If it is determined that the condition for finishing a defrosting operation on the heat exchanger 3a is not satisfied (NO in S221), the controller 50B returns the process to the main routine. If it is determined that the condition for finishing a defrosting operation on the heat exchanger 3a is satisfied (YES in S221), the controller 50B switches the circulation direction of the refrigerant in S222, and proceeds the process to S223.
  • the controller 50B determines whether or not a condition for finishing a defrosting operation on the heat exchanger 3b is satisfied.
  • a condition for finishing a defrosting operation on the heat exchanger 3b a condition that the temperature T13 is higher than a reference temperature Df2 (for example, 0°C) may be given. If it is determined that the condition for finishing a defrosting operation on the heat exchanger 3b is satisfied (YES in S223), the controller 50B fully opens the expansion valve 4b in S224, and returns the process to the main routine.
  • the controller 50B controls the opening degree of the expansion valve 4a so as to maintain the pressure difference between the high-pressure side refrigerant and the low-pressure side refrigerant within a desired range. If it is determined that the condition for finishing a defrosting operation on the heat exchanger 3b is not satisfied (NO in S223), the controller 50B fully opens the expansion valve 4a in S225, and returns the process to the main routine.
  • Fig. 14 is a diagram illustrating a flow of refrigerant when the condition for finishing a defrosting operation on the heat exchanger 3a is satisfied but the condition for finishing a defrosting operation on the heat exchanger 3b is not satisfied (when S225 of Fig. 13 is performed).
  • the heat exchanger 3b since the expansion valve 4a is fully opened, the heat exchanger 3b functions as a condenser.
  • the heat exchanger 3b is defrosted by the condensation heat released from the refrigerant.
  • the heating of the heat exchanger 3b by the condensation heat released from the refrigerant is performed after the condition for finishing a defrosting operation on the heat exchanger 3b is satisfied.
  • the controller 50B controls the opening degree of the expansion valve 4b so as to maintain the pressure difference between the high-pressure side refrigerant and the low-pressure side refrigerant within a desired range.
  • the restarted heating operation may be either a high load operation or a low load operation.
  • Fig. 15 is a flowchart illustrating another exemplary defrosting determination process to be performed by the controller 50B during the heating operation.
  • the flowchart illustrated in Fig. 15 is different from the flowchart illustrated in Fig. 12 with the addition of S216 and a reverse order of S212 and S213.
  • the controller 50B if it is determined that the condition for starting a defrosting operation on the heat exchanger 3b is satisfied (YES in S211), the controller 50B establishes the flow path F1 in S213, and proceeds the process to S212. If it is determined that the condition for starting a defrosting operation on the heat exchanger 3a is not satisfied (NO in S212), the controller 50B fully opens the expansion valve 4a in S216, and returns the process to the main routine.
  • the flow of refrigerant in the air conditioner 200 after S216 is the same as the flow of refrigerant as illustrated in Fig. 14 .
  • the expansion valve 4b since the expansion valve 4b is connected between the heat exchangers 3b and 3a, the expansion valve 4a may be fully opened so as to allow the liquid refrigerant to flow into the heat exchanger 3b. Since it is possible to store the liquid refrigerant in the heat exchanger 3b, as compared with the case where the expansion valve 4b is not provided and the refrigerant in the gas-liquid two-phase state after depressurization by the expansion valve 4a is stored in the heat exchanger 3b, the heat exchanger 3b may be made smaller.
  • the defrosting operation may be performed on the heat exchanger 3b without stopping the heating operation, it is possible to prevent the temperature of the indoor space from being decreased by the reverse defrosting operation. Further, when the non-azeotropic mixture refrigerant is sealed as the refrigerant, due to the temperature gradient, frost is likely to be formed around the port P5 of the heat exchanger 3b. In the air conditioner 200, since the refrigerant having a relatively high temperature flows into the heat exchanger 3b during the heating operation, it is possible to prevent frost from being formed around the port P5 of the heat exchanger 3b. Further, the prevention of frost on the heat exchanger 3b makes it possible to prevent frost from being spread to the heat exchanger 3a.
  • the refrigeration cycle apparatus of the second embodiment it is possible to improve the operation efficiency of the refrigeration cycle apparatus during any of the cooling operation, the heating operation or the defrosting operation while preventing the refrigeration cycle apparatus from becoming larger in size.
  • the first switch may selectively establish the first flow path and the second flow path.
  • the description will be carried out on that the first switch may establish both the first flow path and the second flow path at an open state.
  • Fig. 16 is a functional block diagram illustrating the configuration of an air conditioner 300 which serves as an example of a refrigeration cycle apparatus according to the third embodiment.
  • the air conditioner 300 is different from the air conditioner 200 illustrated in Fig. 7 in that the switch 7 and the controller 50B in Fig. 7 are replaced by a three-way valve 7C and a controller 50C, respectively.
  • the other components are the same, and the description thereof will not be repeated.
  • the three-way valve 7C includes a port P31 (a first port), a port P32 (a second port), a port P33 (a third port), a flow path F31 (a first flow path), and a flow path F32 (a second flow path).
  • the flow path F31 communicates the ports P31 and P32.
  • the flow path F32 communicates the ports P31 and P33.
  • the three-way valve 7C may switch the flow paths F31 and F32 between an open state and a closed state.
  • Fig. 17 is a flowchart illustrating a process to be performed by the controller 50C of Fig. 16 on the three-way valve 7C during a low load cooling operation.
  • the process illustrated in Fig. 17 is called at regular intervals by a main routine (not shown) for performing a comprehensive control on the air conditioner 300.
  • the controller 50C determines whether or not the flow path F31 is open in S301. If it is determined that the flow path F31 is open (YES in S301), the controller 50C sets the degree of supercooling of the refrigerant flowing out of the heat exchanger 3b to "SC" in S302, and proceeds the process to S304. If it is determined that the flow path F31 is closed (NO in S301), the controller 50C sets the degree of supercooling of the refrigerant flowing out of the heat exchanger 3a to "SC" in S303, and proceeds the process to S304.
  • the controller 50C determines whether or not the degree of supercooling SC is greater than a reference value SC1. If it is determined that the degree of supercooling SC is greater than the reference value SC1 (YES in S304), the controller 50C proceeds the process to S307.
  • the controller 50C determines whether or not the degree of supercooling SC is smaller than a reference value SC2 in S305. If it is determined that the degree of supercooling SC is equal to or greater than the reference value SC2 (NO in S305), the controller 50C returns the process to the main routine. If it is determined that the degree of supercooling SC is smaller than the reference value SC2 (YES in S305), the controller 50C opens the flow path F31 in S306, and proceeds the process to S307.
  • step S307 the controller 50C opens the flow path F32, and proceeds the process to step S308.
  • step S308 the controller 50C closes the flow path F31, and returns the process to the main routine.
  • Fig. 18 is a flowchart illustrating a process to be performed by the controller 50C of Fig. 16 on the three-way valve 7C during the low load heating operation.
  • the process illustrated in Fig. 11 is called at regular intervals by a main routine (not shown) for performing a comprehensive control on the air conditioner 200.
  • the controller 50C determines whether or not the degree of supercooling SC is greater than a reference value SC3 in S311. If it is determined that the degree of supercooling SC is greater than the reference value SC3 (YES in S311), the controller 50C proceeds the process to S314. If it is determined that the degree of supercooling SC is equal to or smaller than the reference value SC3 (NO in S311), the controller 50C determines whether or not the degree of supercooling SC is smaller than a reference value SC4 (SC4 ⁇ SC3) in S312. If it is determined that the degree of supercooling SC is equal to or greater than the reference value SC4 (NO in S312), the controller 50C returns the process to the main routine. If it is determined that the degree of supercooling SC is smaller than the reference value SC4 (YES in S312), the controller 50C opens the flow path F31 in S313, and proceeds the process to S314.
  • step S314 the controller 50C opens the flow path F32, and proceeds the process to step S315.
  • step S315 the controller 50C closes the flow path F31, and returns the process to the main routine.
  • Fig. 19 is a flowchart illustrating an exemplary defrosting determination process to be performed by the controller 50C during the heating operation.
  • the flowchart illustrated in Fig. 19 is different from the flowchart illustrated in Fig. 12 in that S213 in Fig. 12 is replaced by S323, and S324 is performed between S323 and S214.
  • the controller 50C opens the flow path F31 in S323, closes the flow path F32 in S324, and proceeds the process to S214.
  • the controller 50C performs S214 and S215 similar to the second embodiment, and returns the process to the main routine.
  • Fig. 20 is a flowchart illustrating another exemplary defrosting determination process to be performed by the controller 50C during the heating operation.
  • the flowchart illustrated in Fig. 20 is obtained in such a manner that S213 of Fig. 15 is replaced by S323 of Fig. 19 , and S324 of Fig. 19 is performed between S323 and S212 in Fig. 20 .
  • the controller 50C performs the process illustrated in Fig. 14 .
  • the controller 50C opens the flow path F31 in S323, closes the flow path F32 in S324, and proceeds the process to S212.
  • the controller 50C performs S212 and S214 to S216 similar to the second embodiment, and returns the process to the main routine.
  • an electronic expansion valve may be connected to each of the flow paths F31 and F32. It is desirable that the amount of refrigerant flowing through each of the flow paths F31 and F32 per unit time be adjustable.
  • the refrigeration cycle apparatus of the third embodiment it is possible to improve the operation efficiency of a refrigeration cycle apparatus while preventing the refrigeration cycle apparatus from becoming larger in size.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (8)

  1. Kältekreislaufvorrichtung (200, 300) die Kältemittel zirkuliert, wobei die Kältekreislaufvorrichtung (200, 300) aufweist:
    einen Verdichter (1);
    einen ersten Wärmetauscher (3a);
    einen zweiten Wärmetauscher (3b);
    einen dritten Wärmetauscher (5);
    ein erstes Expansionsventil (4a);
    einen ersten Schalter (7), der eine erste Öffnung (P1), eine zweite Öffnung (P2) und eine dritte Öffnung (P3) aufweist,
    eine Steuereinheit (50B, 50C), die eingerichtet ist, den ersten Schalter (7) zu steuern; und
    ein zweites Expansionsventil (4b), das zwischen dem ersten Wärmetauscher (3a) und dem zweiten Wärmetauscher (3b) verbunden ist,
    der erste Schalter (7) jeden von einem ersten Strömungspfad (F1, F31) und einem zweiten Strömungspfad (F2, F32) zwischen einem offenen Zustand und einem geschlossenen Zustand umschaltet, wobei der erste Strömungspfad (F1, F31) die erste Öffnung (P1) und die zweite Öffnung (P2) miteinander kommunizierend verbindet, und der zweite Strömungspfad (F2, F32) die erste Öffnung (P1) und die dritte Öffnung (P3) miteinander kommunizierend verbindet,
    wenn der erste Strömungspfad (F1, F31) geöffnet ist, das Kältemittel in einer ersten Zirkulationsrichtung durch den Verdichter (1), den ersten Wärmetauscher (3a), die erste Öffnung (P1), die zweite Öffnung (P2), den zweiten Wärmetauscher (3b), das erste Expansionsventil (4a) und den dritten Wärmetauscher (5) zirkuliert wird,
    wenn der zweite Strömungspfad (F2, F32) geöffnet ist, das Kältemittel in einer zweiten Zirkulationsrichtung durch den Verdichter (1), den ersten Wärmetauscher (3a), die erste Öffnung (P1), die dritte Öffnung (P3), das erste Expansionsventil (4a) und den dritten Wärmetauscher (5) zirkuliert wird, und
    wenn die Zirkulationsrichtung des Kältemittels von der ersten Zirkulationsrichtung auf die zweite Zirkulationsrichtung umgeschaltet wird, ein Teil des Kältemittels in dem zweiten Wärmetauscher (3b) gespeichert wird,
    wobei die Steuereinheit (50B, 50C) eingerichtet ist, den ersten Strömungspfad (F1, F31) zu öffnen, wenn der Grad der Unterkühlung des in das erste Expansionsventil (4a) strömenden Kältemittels kleiner ist als ein Referenzwert (SC1),
    wobei die Kältekreislaufvorrichtung (200, 300) ferner einen zweiten Schalter (2) aufweist, der eingerichtet ist, die Zirkulationsrichtung des Kältemittels zwischen der ersten Zirkulationsrichtung und einer dritten Zirkulationsrichtung entgegengesetzt zur ersten Zirkulationsrichtung umzuschalten, und die Zirkulationsrichtung des Kältemittels zwischen der zweiten Zirkulationsrichtung und einer vierten Zirkulationsrichtung entgegengesetzt zur zweiten Zirkulationsrichtung umzuschalten,
    wenn die Zirkulationsrichtung des Kältemittels die erste Zirkulationsrichtung oder die zweite Zirkulationsrichtung ist, und wenn eine Bedingung für das Beenden eines Entfrostungsbetriebs an dem ersten Wärmetauscher (3a) erfüllt ist, und eine Bedingung für das Beenden eines Entfrostungsbetriebs an dem zweiten Wärmetauscher (3b) nicht erfüllt ist, die Steuereinheit (50B, 50C) eingerichtet ist, den ersten Strömungspfad (F1, F31) zu öffnen, um die Zirkulationsrichtung des Kältemittels auf die dritte Zirkulationsrichtung umzuschalten, und das erste Expansionsventil (4a) vollständig öffnet.
  2. Kältekreislaufvorrichtung (200) nach Anspruch 1, wobei
    der erste Schalter (7) eingerichtet ist, den ersten Strömungspfad (F1) und den zweiten Strömungspfad (F2) selektiv herzustellen.
  3. Kältekreislaufvorrichtung (200, 300) nach Anspruch 1 oder 2, wobei
    der zweite Wärmetauscher (3b) aufweist:
    eine vierte Öffnung (P4), durch die das Kältemittel in den zweiten Wärmetauscher (3b) in der ersten Zirkulationsrichtung einströmt; und
    eine fünfte Öffnung (P5), durch die das Kältemittel aus dem zweiten Wärmetauscher (3b) in der ersten Zirkulationsrichtung ausströmt,
    ein dritter Strömungspfad (F3), der sich von dem zweiten Wärmetauscher (3b) zu dem ersten Expansionsventil (4a) erstreckt, einen spezifischen Abschnitt (N1) aufweist, der sich an einer höheren Position als die fünfte Öffnung (P5) befindet.
  4. Kältekreislaufvorrichtung (200, 300) nach Anspruch 3, wobei
    ein vierter Strömungspfad (F4), der sich von der dritten Öffnung (P3) zum dritten Strömungspfad (F3) erstreckt, mit dem dritten Strömungspfad (F3) an dem spezifischen Abschnitt (N1) verbunden ist.
  5. Kältekreislaufvorrichtung (200, 300) nach Anspruch 1, wobei
    die Steuereinheit (50B, 50C) eingerichtet ist, den zweiten Strömungspfad (F2, F32) zu öffnen, wenn der Grad der Unterkühlung größer ist als der Referenzwert (SC1).
  6. Kältekreislaufvorrichtung (200, 300) nach einem der Ansprüche 1 bis 5, wobei
    wenn die Zirkulationsrichtung des Kältemittels die dritte Zirkulationsrichtung oder die vierte Zirkulationsrichtung ist, und wenn eine Bedingung für das Starten eines Entfrostungsbetriebs an dem zweiten Wärmetauscher (3b) erfüllt ist, und eine Bedingung für das Starten eines Entfrostungsbetriebs an dem ersten Wärmetauscher (3a) nicht erfüllt ist, die Steuereinheit (50B, 50C) eingerichtet ist, den ersten Strömungspfad (F1, F31) zu öffnen und das erste Expansionsventil (4a) vollständig zu öffnen.
  7. Kältekreislaufvorrichtung (200, 300) nach einem der Ansprüche 1 bis 6, wobei
    das Kältemittel ein HC-(Kohlenwasserstoff)-Kältemittel enthält.
  8. Kältekreislaufvorrichtung (200, 300) nach einem der Ansprüche 1 bis 7, wobei
    das Kältemittel ein nicht-azeotropes Kältemittelgemisch enthält.
EP19917871.6A 2019-03-06 2019-03-06 Kältekreislaufvorrichtung Active EP3936786B1 (de)

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ZA824646B (en) * 1981-07-09 1983-04-27 Ti Ltd Heat exchangers
JPS5860168U (ja) * 1981-10-16 1983-04-22 三洋電機株式会社 冷凍装置
JPH01116366U (de) * 1988-01-29 1989-08-04
JP2006317063A (ja) 2005-05-12 2006-11-24 Sharp Corp 空気調和機
JP2009041829A (ja) * 2007-08-08 2009-02-26 Panasonic Corp 空気調和装置
CN201335568Y (zh) * 2008-12-27 2009-10-28 广东美的电器股份有限公司 空调室外机的除霜系统
JP5755490B2 (ja) * 2011-04-18 2015-07-29 トヨタ自動車株式会社 冷却装置
WO2014097899A1 (ja) 2012-12-21 2014-06-26 富士フイルム株式会社 固体撮像装置
US9605885B2 (en) * 2013-03-14 2017-03-28 Mitsubishi Electric Corporation Air conditioning system including pressure control device and bypass valve
JP6017058B2 (ja) * 2013-10-24 2016-10-26 三菱電機株式会社 空気調和装置
JP6309739B2 (ja) 2013-10-31 2018-04-11 シャープ株式会社 空気調和機
JP6319334B2 (ja) * 2016-01-15 2018-05-09 ダイキン工業株式会社 冷凍装置
CN105758075A (zh) * 2016-04-01 2016-07-13 珠海格力电器股份有限公司 一种分段式制热除霜的空调系统及其制热除霜控制方法
CN206247522U (zh) * 2016-11-07 2017-06-13 宁波甬凌环境设备有限公司 一种三联供空气源热泵系统
JP2018087675A (ja) * 2016-11-30 2018-06-07 ダイキン工業株式会社 冷凍装置

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CN113518886A (zh) 2021-10-19
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JPWO2020179015A1 (ja) 2021-12-02
ES2961815T3 (es) 2024-03-14
CN113518886B (zh) 2022-11-11
JP7118239B2 (ja) 2022-08-15
EP3936786A1 (de) 2022-01-12

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