EP3614071B1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP3614071B1
EP3614071B1 EP17906434.0A EP17906434A EP3614071B1 EP 3614071 B1 EP3614071 B1 EP 3614071B1 EP 17906434 A EP17906434 A EP 17906434A EP 3614071 B1 EP3614071 B1 EP 3614071B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
compressor
refrigeration cycle
circuit
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Active
Application number
EP17906434.0A
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English (en)
French (fr)
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EP3614071A4 (de
EP3614071A1 (de
Inventor
Kensaku HATANAKA
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP3614071A4 publication Critical patent/EP3614071A4/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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/07—Exceeding a certain pressure value in a refrigeration component or 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
    • F25B2500/00—Problems to be solved
    • F25B2500/26—Problems to be solved characterised by the startup of the refrigeration 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures

Definitions

  • the present invention relates to a refrigeration cycle apparatus including a plurality of refrigerant circuits.
  • Refrigeration cycle apparatuses have hitherto been proposed that include a low-stage circuit including a compressor, a cascade heat exchanger, a liquid receiving part, an expansion device, and an evaporator; and a high-stage circuit including a compressor, a condenser, an expansion device, a heat exchanger, and a cascade heat exchanger (for example, refer to Patent Literature 1).
  • the evaporator of the low-stage circuit is used for, for example, cooling a target space for air-conditioning.
  • refrigerant of the low-stage circuit is cooled by refrigerant of the high-stage circuit.
  • a heat exchanger is provided in the liquid receiving part. Therefore, the refrigerant of the low-stage circuit is cooled by refrigerant of the liquid receiving part.
  • a compressor of the low temperature circuit is often stopped by, for example, power failure.
  • the compressor of the low-stage circuit is stopped, the refrigerant of the low-stage circuit does not circulate. Then, while gas refrigerant of the low-stage circuit is not cooled by the evaporator of the low-stage circuit, the gas refrigerant of the low-stage circuit is often heated by outdoor air. As a result, the pressure of the gas refrigerant of the low-stage circuit may increase. If high pressure refrigerant such as carbon dioxide refrigerant is used in a large amount, the pressure of the gas refrigerant increases more remarkably. If the outdoor air temperature is high, as in the summer, for example, the pressure of the gas refrigerant increases more remarkably. Examples of means to prepare for such increase of the pressure of the gas refrigerant include improving the withstand pressure in a pipe in which the gas refrigerant flows. However, improving the withstand pressure leads to an increase in pipe cost.
  • EP1674806A1 is considered as the closest prior art and discloses a refrigeration cycle apparatus according to the preamble of claim 1.
  • This document discloses a subcooling unit including a refrigerant passage connected to liquid side communication pipes of a refrigerating apparatus.
  • subcooling refrigerant circulates in the subcooling refrigerant circuit to perform a refrigeration cycle, thereby cooling refrigerant of the refrigerating apparatus which flows in the refrigerant passage.
  • a controller of the subcooling unit receives the detection value of a suction pressure sensor and a refrigerant temperature sensor. The controller utilizes input signals from the sensors to control driving operation of the subcooling compressor on the basis of information obtained within the subcooling unit.
  • the operation of the subcooling compressor can be controlled without sending and receiving a singal to and from the refrigerating apparatus to which the subcooling unit is incorporated.
  • US2011072836A1 discloses a two-stage cascade refrigeration system having a first refrigeration stage and a second refrigeration stage.
  • the first refrigeration stage defines a first fluid circuit for circulating a first refrigerant, and has a first compressor, a condenser, and a first expansion device that is in fluid communication with the first fluid circuit.
  • the second refrigeration stage defines a second fluid circuit for circulating a second refrigerant, with the second refrigeration stage having a second compressor, a second expansion device, and an evaporator that is in fluid communication with the second fluid circuit.
  • a heat exchanger is in fluid communication with the first and second fluid circuits to exchange heat between the first and second refrigerants.
  • At least one of the first or second compressors is a variable speed compressor.
  • Patent Literature 1 Japanese Patent No. 5575191
  • the present invention has been made to solve the aforementioned problem in the conventional technology, and an object thereof is to provide a refrigeration cycle apparatus capable of suppressing increase of the pressure of refrigerant of a first refrigerant circuit (low-stage circuit) while suppressing power consumption.
  • the refrigeration cycle apparatus includes the aforementioned configuration, and therefore it is possible to suppress increase of the pressure of refrigerant of the first refrigerant circuit (low-stage circuit) while suppressing power consumption.
  • Fig. 1A illustrates a refrigerant circuit configuration and relevant components of a refrigeration cycle apparatus 100 according to Embodiment 1.
  • Fig. 1B is a schematic diagram of a first compressor 1 included in the refrigeration cycle apparatus 100 according to Embodiment 1.
  • Fig. 1C illustrates an installation example of the refrigeration cycle apparatus 100 according to Embodiment 1.
  • the refrigeration cycle apparatus 100 includes an indoor unit 101 and an outdoor unit 102. As illustrated in Fig. 1C , the indoor unit 101 is provided in a building Bd. The outdoor unit 102 is provided outside the building Bd. The indoor unit 101 and the outdoor unit 102 are connected through a refrigerant pipe 7C and a refrigerant pipe 11. Refrigerant of two-phase gas-liquid flows in the refrigerant pipe 7C. Gas refrigerant flows in the refrigerant pipe 11.
  • the refrigeration cycle apparatus 100 includes a first refrigerant circuit C1, and a second refrigerant circuit C2. That is, the refrigeration cycle apparatus 100 has a dual refrigeration cycle.
  • the first refrigerant circuit C1 corresponds to a first refrigeration cycle (low-stage refrigeration cycle)
  • the second refrigerant circuit C2 corresponds to a second refrigeration cycle (high-stage refrigeration cycle). Cooling capability of the second refrigerant circuit C2 is lower than cooling capability of the first refrigerant circuit C1.
  • the first refrigerant circuit C1 and the second refrigerant circuit C2 are independent refrigerant circuits.
  • First refrigerant that circulates in the first refrigerant circuit C1, and second refrigerant that circulates in the second refrigerant circuit C2 may be the same kind of refrigerant, or may be different kinds of refrigerants.
  • the first refrigerant is carbon dioxide refrigerant.
  • the carbon dioxide refrigerant is refrigerant having low global warming potential, and having small environmental load.
  • the carbon dioxide refrigerant has high working pressure.
  • the carbon dioxide refrigerant can be also used for the second refrigerant.
  • the refrigeration cycle apparatus 100 is equivalent to, for example, a refrigeration device configured to store stored goods and other goods, an air-conditioning device for cooling an air-conditioned space, or other devices. In Embodiment 1, the refrigeration cycle apparatus 100 will be described as a refrigeration device.
  • the refrigeration cycle apparatus 100 includes the controller Cnt.
  • the refrigeration cycle apparatus 100 includes a first fan 3A, a second fan 10A, and a fan 15A. Additionally, the refrigeration cycle apparatus 100 includes a condenser temperature sensor SE1, an evaporator temperature sensor SE2, and a pressure sensor SE3.
  • the first refrigerant circuit C1 includes the first compressor 1, the oil separator 2, a first heat exchanger 3, a first refrigerant flow passage of a second heat exchanger 4, a first expansion device 5, the liquid receiver 6, a valve 8, an expansion device 9, a third heat exchanger 10, and an accumulator 12. Additionally, the first refrigerant circuit C1 includes an oil return circuit C3.
  • the oil return circuit C3 includes a pipe Rp1 that connects the oil separator 2 and the first compressor 1, and an opening and closing device 13 provided in this pipe Rp1. Furthermore, the first refrigerant circuit C1 includes a refrigerant pipe 7A, a refrigerant pipe 7B, the refrigerant pipe 7C, and the refrigerant pipe 11.
  • the first refrigerant flows in the first refrigerant circuit C1.
  • the first refrigerant circuit C1 is configured such that the first refrigerant flows sequentially in the order of the first compressor 1, the oil separator 2, the first heat exchanger 3, the first refrigerant flow passage of the second heat exchanger 4, the first expansion device 5, the liquid receiver 6, the valve 8, the expansion device 9, the third heat exchanger 10, and the accumulator 12.
  • the refrigerant pipe 7A connects the second heat exchanger 4 and the first expansion device 5.
  • the refrigerant pipe 7B connects the first expansion device 5 and the liquid receiver 6.
  • the refrigerant pipe 7C connects the liquid receiver 6 and the valve 8.
  • the refrigerant pipe 11 connects the third heat exchanger 10 and the accumulator 12.
  • the refrigerant pipe 7C and the refrigerant pipe 11 each are a pipe for connecting the indoor unit 101 and the outdoor unit 102.
  • the first refrigerant circuit C1 has a function of cooling an object to be cooled by the refrigeration cycle apparatus 100.
  • the indoor unit 101 supplies cold air to a space SP provided with the indoor unit 101. Consequently, stored goods and the other goods in the space SP are cooled.
  • the space SP is a space in, for example, the building Bd that refrigerates and preserves the stored goods.
  • the second refrigerant circuit C2 includes a second compressor 14, a fourth heat exchanger 15, a second expansion device 16, and a second refrigerant flow passage of the second heat exchanger 4.
  • the second refrigerant flows in the second refrigerant circuit C2.
  • the second refrigerant circuit C2 is configured such that the second refrigerant flows in the order of the second compressor 14, the fourth heat exchanger 15, the second expansion device 16, and the second refrigerant flow passage of the second heat exchanger 4.
  • the second refrigerant circuit C2 has a function of super-cooling the first refrigerant circuit C1, and a function of cooling the first refrigerant in the first refrigerant circuit C1 when the first compressor 1 is stopped.
  • the first compressor 1 compresses the first refrigerant to increase the temperature and the pressure of the first refrigerant.
  • the first compressor 1 includes an airtight vessel 1A, a compression mechanism 1B, a stator 1C, a rotor 1D, a shaft 1E, a suction pipe 1F, and a discharge pipe 1G.
  • the compression mechanism 1B includes a fixed scroll and an orbiting scroll.
  • a compression chamber that compresses the first refrigerant is formed between the fixed scroll and the orbiting scroll.
  • the stator 1C is fixed in the airtight vessel 1A. Refrigerating machine oil is stored on a bottom of the airtight vessel 1A.
  • the refrigerating machine oil in the airtight vessel 1A is drawn into a flow passage (not illustrated) in the shaft 1E by rotation of the shaft 1E.
  • the refrigerating machine oil drawn into the flow passage in the shaft 1E is supplied to the compression mechanism 1B.
  • the suction pipe 1F, the discharge pipe 1G, and the pipe Rp1 of the oil return circuit C3 are connected to the airtight vessel 1A.
  • a suction part of the first compressor 1 corresponds to the suction pipe 1F, or a refrigerant pipe connected to the suction pipe 1F.
  • a discharge part of the first compressor 1 corresponds to the discharge pipe 1G, or a refrigerant pipe connected to the discharge pipe 1G.
  • Refrigerating machine oil stored in the oil separator 2 is returned from the pipe Rp1 to the airtight vessel 1A.
  • the second compressor 14 compresses the second refrigerant to increase the temperature and the pressure of the second refrigerant.
  • the oil separator 2 stores the refrigerating machine oil discharged together with the refrigerant from the first compressor 1.
  • the refrigerating machine oil stored in the oil separator 2 is returned to the first compressor 1 through the oil return circuit C3.
  • the oil return circuit C3 has one end being connected to the oil separator 2, and the other end connected to the first compressor 1.
  • the oil return circuit C3 connects the oil separator 2 and the first compressor 1, and the refrigerating machine oil stored in the oil separator 2 is returned to the first compressor 1.
  • the first heat exchanger 3 has one side being connected to the oil separator 2 through the refrigerant pipe, and the other side being connected to the second heat exchanger 4 through the refrigerant pipe.
  • the first heat exchanger 3 is provided with the first fan 3A. In the first heat exchanger 3, air and the first refrigerant exchange heat.
  • the second heat exchanger 4 includes the first refrigerant flow passage and the second refrigerant flow passage.
  • the second heat exchanger 4 is a cascade heat exchanger.
  • the second heat exchanger 4 is configured such that the first refrigerant that flows in the first refrigerant flow passage, and the second refrigerant that flows in the second refrigerant flow passage can exchange heat.
  • the first refrigerant flow passage of the second heat exchanger 4 has one side being connected to the first heat exchanger 3 through the refrigerant pipe, and the other side being connected to the first expansion device 5 through the refrigerant pipe 7A.
  • the second refrigerant flow passage of the second heat exchanger 4 has one side being connected to the second expansion device 16 through the refrigerant pipe, and the other side being connected to a suction part for refrigerant of the second compressor 14 through the refrigerant pipe.
  • the first expansion device 5 and the expansion device 9 may be each composed of a solenoid valve that can control the opening degree. Additionally, a capillary tube can be used in each of the first expansion device 5 and the expansion device 9.
  • the liquid receiver 6 has a function of storing liquid refrigerant. The liquid receiver 6 is provided on a downstream side relative to the condenser. That is, the liquid receiver 6 is provided on a downstream side relative to the first refrigerant flow passage of the second heat exchanger that functions as the condenser.
  • the valve 8 may be composed of, for example, a solenoid valve that can control opening and closing. The valve 8 is provided in the indoor unit 101.
  • the third heat exchanger 10 has one side being connected to the expansion device 9 through the refrigerant pipe, and the other side being connected to the accumulator 12 through the refrigerant pipe.
  • the third heat exchanger 10 is provided with the second fan 10A.
  • air and the first refrigerant exchange heat In the third heat exchanger 10, air and the first refrigerant exchange heat.
  • the air cooled in the third heat exchanger 10 is supplied to the space to be air-conditioned.
  • the fourth heat exchanger 15 has one side being connected to the second compressor 14 through the refrigerant pipe, and the other side being connected to the second expansion device 16 through the refrigerant pipe.
  • the fourth heat exchanger 15 is provided with the fan 15A.
  • the second expansion device 16 can be composed of a solenoid valve that can control the opening degree. Additionally, a capillary tube can be used in the second expansion device 16.
  • the refrigerant (the first refrigerant and the second refrigerant) and air exchange heat in the first heat exchanger 3 and the fourth heat exchanger 15
  • the first heat exchanger 3 and the fourth heat exchanger 15 are not limited to this embodiment.
  • refrigerant and heat medium other than air exchange heat may be used in the first heat exchanger 3 and the fourth heat exchanger 15. That is, a heat medium circuit independent of the first refrigerant circuit C1 and the second refrigerant circuit may be connected to the first heat exchanger 3 and the fourth heat exchanger 15.
  • water, brine, refrigerant, or other heat medium can be used as the heat medium.
  • the heat medium is water and brine
  • pumps that convey water and brine can be used in place of the first fan 3A and the fan 15A that supply air.
  • the heat medium is refrigerant
  • a compressor that compresses refrigerant can be used in place of the first fan 3A and the fan 15A that supply air.
  • Fig. 1D is a function block diagram of the controller Cnt of the refrigeration cycle apparatus 100 according to Embodiment 1. First control implemented by the refrigeration cycle apparatus 100, and a configuration of the controller Cnt, and the like will be described with reference to Fig. 1D .
  • the controller Cnt acquires information of the detected temperature of the condenser temperature sensor SE1, and information of the detected temperature of the evaporator temperature sensor SE2, and information of the detected pressure of the pressure sensor SE3.
  • the condenser temperature sensor SE1 corresponds to a first temperature sensor of the present invention
  • the evaporator temperature sensor SE2 corresponds to a second temperature sensor of the present invention.
  • the controller Cnt has a function of implementing the first control of starting operation of the second compressor 14 and opening the opening and closing device 13 in a case where the first compressor 1 and the second compressor 14 are stopped, and the pressure in a low pressure part of the first refrigerant circuit C1 is a reference value or more.
  • Examples of the case in which the first compressor 1 and the second compressor 14 stop include a case in which a user turns off a power source of the refrigeration cycle apparatus 100. In a season in which the outdoor air temperature is high, such as summer, the temperature of the refrigerant pipe 11 in which the first refrigerant being in a gas state is sealed tends to increase.
  • the pressure of the first refrigerant in the refrigerant pipe 11 increases to the reference value or more, and a possibility that the refrigerant pipe 11 is broken is increased. Additionally, even when the withstand pressure of the refrigerant pipe 11 is improved to prevent such breakage, pipe cost is increased. Therefore, in the case where the first compressor 1 and the second compressor 14 stop, and the pressure in the low pressure part of the first refrigerant circuit C1 is the reference value or more, even when the power source of the refrigeration cycle apparatus 100 is turned off, operation of the second compressor 14 is automatically started.
  • the controller Cnt also operates the fan 15A, and the second expansion device 16 has a predetermined opening degree.
  • second refrigerant in the second refrigerant circuit C2 cools first refrigerant in the first refrigerant circuit C1, and increase of the pressure of the first refrigerant is suppressed.
  • the second refrigerant in the second refrigerant circuit C2 cools the first refrigerant in the first refrigerant circuit C1
  • the first refrigerant naturally circulates in the first refrigerant circuit C1. That is, the capability of conveying the first refrigerant at this time is smaller than the capability of conveying the first refrigerant during operation of the first compressor 1. Therefore, when the first refrigerant is hard to pass through the first compressor 1, a flow rate of the first refrigerant is reduced.
  • the opening and closing device 13 is opened in synchronization with start of operation of the second compressor 14. Consequently, the first refrigerant is likely to pass through the first compressor 1, and it is possible to suppress reduction of the flow rate of the first refrigerant even when the first refrigerant naturally circulates.
  • the implementation condition and the configuration of the first control may be as follows.
  • the controller Cnt implements the first control in a state in which the first fan 3A and the second fan 10A are stopped.
  • a condition that the detected temperature of the first heat exchanger 3 is not lower than the detected temperature of the third heat exchanger 10 is a condition that a likelihood that the first refrigerant can be liquefied even when the first refrigerant passes through the first heat exchanger 3 in a state in which the first fan 3A is operated is low. For example, when the outdoor air temperature is high like summer, the temperature of the first heat exchanger 3 provided in the outdoor unit 102 is increased.
  • the refrigeration cycle apparatus 100 stops the first fan 3A to suppress power consumption. Additionally, the second fan 10A is brought into a stop state. This is because when the second fan 10A is operated, gasification of the first refrigerant is facilitated, and the pressure of the first refrigerant is increased.
  • implementation condition and the configuration of the first control may be as follows.
  • the controller Cnt implements second control of operating the first fan 3A and the second fan in a state of stopping the second compressor 14, without conducting the first control.
  • a condition that the detected temperature of the first heat exchanger 3 is lower than the detected temperature of the third heat exchanger 10 is a condition that there is a likelihood that the first refrigerant can be liquefied by making the first refrigerant pass through the first heat exchanger 3 in a state of operating the first fan 3A. For example, when the outdoor air temperature is low as in winter and night, the temperature of the first heat exchanger 3 provided in the outdoor unit 102 is reduced.
  • the first fan 3A when the first fan 3A is operated, and air is supplied to the first heat exchanger 3, the first refrigerant is liquefied, and it is possible to suppress increase of the pressure of the first refrigerant.
  • the second fan 10A is brought into a stop state. This is because when the second fan 10A is operated, gasification of the first refrigerant is facilitated, and the pressure of the first refrigerant is increased.
  • the refrigeration cycle apparatus 100 receives electric power supply from a different system, and performs various operations.
  • the controller Cnt includes a determination unit 90A, an operation control unit 90B, and a storage unit 90C.
  • the determination unit 90A has a function of determining whether or not the pressure in the low pressure part of the first refrigerant circuit C1 is the reference value or more.
  • the low pressure part of the first refrigerant circuit C1 means, for example, a downstream side of the expansion device 9, and an upstream side of the suction part of the first compressor 1. That is, the low pressure part of the first refrigerant circuit C1 means a portion in which refrigerant decompressed by the expansion device flows.
  • the determination unit 90A determines whether or not the pressure in the low pressure part of the first refrigerant circuit C1 is the reference value or more on the basis of the detected pressure in the pressure sensor SE3. This determination may be performed by using, for example, the outdoor air temperature in place of the pressure sensor SE3.
  • the determination unit 90A is configured to determine whether or not the detected temperature of the first heat exchanger 3 is not lower than the detected temperature of the third heat exchanger 10. Furthermore, the determination unit 90A is configured to determine whether or not the detected temperature of the first heat exchanger 3 is lower than the detected temperature of the third heat exchanger 10.
  • the operation control unit 90B controls the rotation speed of the first compressor 1 and the rotation speed of the second compressor 14.
  • the operation control unit 90B controls the opening degree of the first expansion device 5, the opening degree of the expansion device 9, and the opening degree of the second expansion device 16.
  • the operation control unit 90B controls the fan rotation speed of the first fan 3A, the fan rotation speed of the second fan 10A, and the fan rotation speed of the fan 15A. Additionally, the operation control unit 90B controls opening and closing of the valve 8, and opening and closing of the opening and closing device 13.
  • the operation control unit 90B performs the first control. In a case where the determination unit 90A determines that the detected temperature of the first heat exchanger 3 is not lower than the detected temperature of the third heat exchanger 10, the operation control unit 90B implements the first control in a state where the first fan 3A and the second fan 10A are stopped. In a case where the determination unit 90A determines that the detected temperature of the first heat exchanger 3 is lower than the detected temperature of the third heat exchanger 10, the operation control unit 90B implements the second control without implementing the first control.
  • Each functional part included in the controller Cnt is composed of an MPU (Micro Processing Unit) that executes a program stored in dedicated hardware, or a memory.
  • the controller Cnt is a dedicated hardware
  • the controller Cnt is equivalent to, for example, a single circuit, a combined circuit, an ASIC (application specific integrated circuit), an FPGA (field-programmable gate array), or combination thereof.
  • Each functional part implemented by the controller Cnt may be implemented by an individual hardware, or each functional part may be implemented by a single hardware.
  • each function to be performed by the controller Cnt is implemented by software, firmware, or combination of software and firmware. The software or the firmware is described as a program, and stored in a memory.
  • the MPU reads out and executes the program stored in the memory, so that each function of the controller Cnt is implemented.
  • the memory is, for example, a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, and an EEPROM.
  • Fig. 1E is a diagram for illustrating positional relation between the second heat exchanger 4 and the liquid receiver 6.
  • the Z direction in Fig. 1E is the gravity direction.
  • the liquid receiver 6 is disposed on a lower side relative to the second heat exchanger 4. Consequently, the first refrigerant liquefied by the second heat exchanger 4 promptly flows into the liquid receiver 6.
  • the first refrigerant naturally circulates. Therefore, the capability of conveying the first refrigerant is smaller than the conveying capability of the first refrigerant during operation of the first compressor 1. Therefore, in the refrigeration cycle apparatus 100, the liquid receiver 6 is disposed on the lower side relative to the second heat exchanger 4 such that the first refrigerant liquefied promptly flows into the liquid receiver 6.
  • the refrigerant pipe 7A and the refrigerant pipe 7B are configured such that the first refrigerant liquefied by the second heat exchanger 4 tends to flow into the liquid receiver 6. That is, the refrigerant pipe 7A and the refrigerant pipe 7B are not configured such that, for example, the first refrigerant flows from the lower side to the upper side when the first refrigerant flows from the second heat exchanger 4 to the liquid receiver 6.
  • the first refrigerant in the first refrigerant circuit C1 flows into the first heat exchanger 3 when the first refrigerant is discharged from the first compressor 1.
  • the first refrigerant that flows into the first heat exchanger 3 transfers heat to air supplied from the first fan 3A.
  • the first refrigerant that flows out from the first heat exchanger 3 flows into the second heat exchanger 4.
  • the first refrigerant in the second heat exchanger 4 is cooled by the second refrigerant.
  • the first refrigerant that flows out from the second heat exchanger 4 is decompressed by the first expansion device 5 to reduce the temperature and the pressure.
  • the first refrigerant that flows out from the first expansion device 5 flows into the third heat exchanger 10.
  • the first refrigerant that flows into the third heat exchanger 10 suctions heat from air supplied from the second fan 10A to cool the air.
  • the first refrigerant that flows out from the third heat exchanger 10 flows into the accumulator 12.
  • the first refrigerant that flows out from the accumulator 12 is suctioned into the first compressor 1.
  • the second refrigerant in the second refrigerant circuit C2 When the second refrigerant in the second refrigerant circuit C2 is discharged from the second compressor 14, the second refrigerant flows into the fourth heat exchanger 15.
  • the second refrigerant that flows into the fourth heat exchanger 15 transfers heat to air supplied from the fan 15A.
  • the second refrigerant that flows out from the fourth heat exchanger 15 is decompressed by the second expansion device 16 to reduce the temperature and the pressure.
  • the second refrigerant that flows out from the first expansion device 5 flows into the second heat exchanger 4 to cool the first refrigerant. Consequently, it is possible to give the degree of super-cooling to the first refrigerant.
  • the first compressor 1 In a case where the first compressor 1 is stopped, it is possible to suppress increase in the pressure of the first refrigerant.
  • the refrigerant that flows out from the second heat exchanger 4 is suctioned into the second compressor 14.
  • the controller Cnt starts operation of the second compressor 14.
  • the controller Cnt opens the opening and closing device 13.
  • the first refrigerant in the low pressure part of the first refrigerant circuit C1 has high pressure, and therefore the first refrigerant in the first refrigerant circuit C1 naturally circulates.
  • the first refrigerant flows into the airtight vessel 1A from the suction part of the first compressor 1.
  • the first refrigerant that flows into the airtight vessel 1A flows into the oil separator 2 through the pipe Rp1 and the opening and closing device 13.
  • the first refrigerant that flows into the oil separator 2 flows into the second heat exchanger 4 through the first heat exchanger 3.
  • the first refrigerant that flows into the second heat exchanger 4 is cooled by the second refrigerant in the second refrigerant circuit to be brought into a two-phase gas-liquid state.
  • the first refrigerant in the two-phase gas-liquid state flows into the liquid receiver 6 through the refrigerant pipe 7A and the first expansion device 5.
  • Liquid refrigerant in the first refrigerant is stored in the liquid receiver 6, and gas refrigerant in the first refrigerant flows into the third heat exchanger 10 through the refrigerant pipe 7C, the valve 8, and the expansion device 9.
  • the first refrigerant circulates in the first refrigerant circuit C1, so that the first refrigerant is cooled by second refrigerant in the second heat exchanger 4 to increase liquid refrigerant to be stored in the liquid receiver 6.
  • increase of the pressure of the first refrigerant in the first refrigerant circuit is suppressed.
  • Fig. 1F is a diagram for illustrating an effect of the refrigeration cycle apparatus 100 according to Embodiment 1.
  • a horizontal axis of a graph illustrated in Fig. 1F denotes the cooling capability of the refrigeration cycle apparatus, and a vertical axis denotes the pressure of the first refrigerant circuit.
  • a curved line L1 of the graph illustrated in Fig. 1F denotes the cooling capability of a conventional refrigeration cycle apparatus.
  • a curved line L2 of the graph illustrated in Fig. 1F denotes the cooling capability of the refrigeration cycle apparatus 100.
  • a curved line L3 of the graph illustrated in Fig. 1F denotes a reference value of the aforementioned pressure.
  • the pressure in the first refrigerant circuit is not lower than a reference value of the low pressure part.
  • the opening and closing device 13 is opened, and therefore the circulation amount (flow rate) of the first refrigerant in the first refrigerant circuit C1 is increased. Accordingly, the first refrigerant can be efficiently cooled by the second refrigerant, and it is possible to suppress increase of the rotation speed of the second compressor 14. That is, in the refrigeration cycle apparatus 100, it is possible to suppress increase of the pressure of the refrigerant in the first refrigerant circuit (low temperature circuit) while suppressing the power consumption.
  • Fig. 1G is a modification of the refrigeration cycle apparatus 100 according to Embodiment 1.
  • the refrigeration cycle apparatus 100 receives electric power supply from a different system in a case where power failure occurs is described as an example.
  • electric power used in a refrigeration cycle apparatus 100 is received from an electric storage part Bt in place of a different system.
  • the electric storage part Bt is a battery.
  • the refrigeration cycle apparatus 100 When power failure occurs, the refrigeration cycle apparatus 100 cannot be operated. For example, when a stop period of the refrigeration cycle apparatus 100 lasts for a long time in summer, a possibility is increased that the pressure in the low pressure part of the first refrigerant circuit C1 is increased. Therefore, in the modification of Embodiment 1, electric power supply from the electric storage part Bt can be received. That is, in the modification of Embodiment 1, the electric storage part Bt that supplies electric power to the second compressor 14 is provided. The electric storage part Bt supplies electric power to the outdoor unit 102, the indoor unit 101, and the controller Cnt.
  • Embodiment 2 will be described with reference to the drawings. Description of portions common to the aforementioned Embodiment 1 will be omitted, and different portions will be mainly described.
  • Fig. 2A is a diagram illustrating a configuration of a refrigeration cycle apparatus 200 according to Embodiment 2.
  • Fig. 2B is a function block diagram of a controller Cnt of the refrigeration cycle apparatus 200 according to Embodiment 2.
  • the refrigeration cycle apparatus 200 includes a bypass C4 in addition to an oil return circuit C3.
  • the bypass C4 includes a pipe Rp2 that connects a discharge part for first refrigerant of a first compressor 1, and a suction part for the first refrigerant of the first compressor 1, and an opening and closing device 13B provided in this pipe Rp2.
  • the pipe Rp2 of the bypass C4 bypasses the first compressor 1.
  • the pipe Rp2 of the bypass C4 includes one end being connected to the suction part for the first refrigerant of the first compressor 1, and the other end being connected to the discharge part for the first refrigerant of the first compressor 1.
  • the controller Cnt controls opening and closing of the opening and closing device 13B.
  • the opening and closing device 13 When the controller Cnt performs the first control, not only the opening and closing device 13 but also the opening and closing device 13B is opened. When the controller Cnt performs the first control, the opening and closing device 13 may not be opened, but the opening and closing device 13B may be opened.
  • the opening and closing device 13 corresponds to a first opening and closing device of the present invention
  • the opening and closing device 13B corresponds to a second opening and closing device of the present invention.
  • the refrigeration cycle apparatus 200 according to Embodiment 2 has the following effects in addition to effects similar to the effects of the refrigeration cycle apparatus 100 according to Embodiment 1.
  • the bypass C4 bypasses the first compressor 1. Therefore, the first refrigerant tends to pass through a flow passage of the bypass C4 than a flow passage from the suction part of the first compressor 1 to an inlet of the oil return circuit C3. That is, the refrigeration cycle apparatus 200 according to Embodiment 2 includes the bypass C4, and therefore the first refrigerant circuit C1 of the refrigeration cycle apparatus 200 according to Embodiment 2 is more likely to naturally circulate the first refrigerant.
  • the bypass C4 is further provided, in addition to the oil return circuit C3.
  • the controller Cnt opens not only the opening and closing device 13 but also the opening and closing device 13B. Consequently, it is possible to further increase the circulation amount (flow rate) of the first refrigerant in the first refrigerant circuit C1. Accordingly, the first refrigerant can be more efficiently cooled by the second refrigerant, and it is possible to suppress increase of the rotation speed of the second compressor 14. That is, in the refrigeration cycle apparatus 200, it is possible to suppress increase of the pressure of the refrigerant in the first refrigerant circuit (low temperature circuit) while further suppressing power consumption.
  • Fig. 2C is Modification 1 of the refrigeration cycle apparatus 200 according to Embodiment 2.
  • a bypass C4 may include one end being connected to a suction part for first refrigerant of a first compressor 1, and the other end being connected between an oil separator 2 and a first heat exchanger 3. Even a refrigeration cycle apparatus 200 of Modification 1 can attain an effect similar to the effects of Embodiment 1 and Embodiment 2.
  • Fig. 2D is Modification 2 of the refrigeration cycle apparatus 200 according to Embodiment 2.
  • bypass C4 may include one end connected to a suction part for first refrigerant of a first compressor 1, and the other end connected between a first heat exchanger 3 and a first refrigerant flow passage of a second heat exchanger 4. Even a refrigeration cycle apparatus 200 of Modification 2 can obtain an effect similar to the effects of Embodiment 1 and Embodiment 2.
  • Embodiment 1 is applicable to Embodiment 2, Modification 1 of Embodiment 2, and Modification 2 of Embodiment 2.

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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)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Claims (8)

  1. Kältekreislaufvorrichtung, umfassend:
    einen ersten Kältemittelkreislauf (C1), aufweisend einen ersten Verdichter (1), einen Ölabscheider (2), einen ersten Wärmetauscher (3), der als ein Kondensator arbeitet, einen ersten Kältemittelströmungsdurchlass eines zweiten Wärmetauschers (4), eine erste Expansionseinrichtung (5) und einen dritten Wärmetauscher (10), der als ein Verdampfer arbeitet, wobei der erste Kältemittelkreislauf (C1) einem ersten Kältemittel erlaubt, darin zu strömen;
    einen zweiten Kältemittelkreislauf (C2), aufweisend einen zweiten Verdichter (14), einen vierten Wärmetauscher (15), der als ein Kondensator arbeitet, eine zweite Expansionseinrichtung (16) und einen zweiten Kältemittelströmungsdurchlass des zweiten Wärmetauschers (4), wobei der zweite Kältemittelkreislauf (C2) einem zweiten Kältemittel erlaubt, darin zu strömen;
    einen Ölrückführungskreislauf (C3), der eine erste Öffnungsund Schließeinrichtung (13) umfasst, den Ölabscheider (2) und den ersten Verdichter (1) verbindet und das im Ölabscheider (2) gespeicherte Kältemaschinenöl zum ersten Verdichter (1) zurückführt, und
    eine Steuereinheit (Cnt), die eingerichtet ist, den ersten Verdichter (1), den zweiten Verdichter (14) und die erste Öffnungs- und Schließeinrichtung (13) zu steuern, wobei
    der erste Kältemittelkreislauf (C1) ein niedrigstufiger Kreislauf ist, und der zweite Kältemittelkreislauf (C2) ein hochstufiger Kreislauf ist; und
    wobei die Kältekreislaufvorrichtung dadurch gekennzeichnet ist, dass:
    die Steuereinheit (Cnt) eingerichtet ist, eine erste Steuerung eines Startbetriebs des zweiten Verdichters (14) und ein Öffnen der ersten Öffnungs- und Schließeinrichtung (13) durchzuführen, in einem Fall, in dem der erste Verdichter (1) und der zweite Verdichter (14) gestoppt sind und ein Druck in einem Niederdruckteil des ersten Kältemittelkreislaufs (C1) ein Referenzwert oder mehr ist.
  2. Kältekreislaufvorrichtung nach Anspruch 1, ferner umfassend:
    einen ersten Lüfter (3A), der dem ersten Wärmetauscher (3) Luft zuführt;
    einen ersten Temperatursensor (SE1), der im ersten Wärmetauscher (3) vorgesehen ist;
    einen zweiten Lüfter (10A), der dem dritten Wärmetauscher (10) Luft zuführt; und
    einen zweiten Temperatursensor (SE2), der im dritten Wärmetauscher (10) vorgesehen ist, wobei
    in einem Fall, in dem eine erfasste Temperatur des ersten Wärmetauschers (3) nicht niedriger ist als eine erfasste Temperatur des dritten Wärmetauschers (10), die Steuereinheit (Cnt) eingerichtet ist, die erste Steuerung in einem Zustand durchzuführen, in dem der erste Lüfter (3A) und der zweite Lüfter (10A) gestoppt sind.
  3. Kältekreislaufvorrichtung nach Anspruch 2, wobei
    die Steuereinheit (Cnt) eingerichtet ist, eine zweite Steuerung eines Betriebs des ersten Lüfters (3A) in einem Zustand durchzuführen, in dem der zweite Verdichter (14) und der zweite Lüfter (10A) gestoppt sind, ohne die erste Steuerung durchzuführen, in einem Fall, in dem die erfasste Temperatur des ersten Wärmetauschers (3) niedriger ist als die erfasste Temperatur des dritten Wärmetauschers (10).
  4. Kältekreislaufvorrichtung nach einem der Ansprüche 1 bis 3, wobei
    der erste Kältemittelkreislauf (C1) ferner einen Flüssigkeitssammler (6) umfasst, der auf einer stromabwärtigen Seite in einer Strömungsrichtung des ersten Kältemittels in Bezug auf den ersten Kältemittelströmungsdurchgang des zweiten Wärmetauschers (4) und auf einer stromaufwärtigen Seite in der Strömungsrichtung des ersten Kältemittels in Bezug auf den dritten Wärmetauscher (10) vorgesehen ist, und
    der Flüssigkeitssammler (6) auf einer unteren Seite in Bezug auf den zweiten Wärmetauscher (4) angeordnet ist.
  5. Kältekreislaufvorrichtung nach einem der Ansprüche 1 bis 4, ferner umfassend
    eine Umgehung (C4), die eine zweite Öffnungs- und Schließeinrichtung (13B) aufweist, und den ersten Verdichter (1) umgeht, wobei
    die zweite Öffnungs- und Schließeinrichtung (13B) in der ersten Steuerung auch geöffnet ist.
  6. Kältekreislaufvorrichtung nach einem der Ansprüche 1 bis 5, ferner umfassend
    ein Elektrikspeicherteil (Bt), das dem zweiten Verdichter (14) elektrische Energie zuführt.
  7. Kältekreislaufvorrichtung nach einem der Ansprüche 1 bis 6, ferner umfassend
    einen Drucksensor, der einen Druck im Niederdruckteil des ersten Kältemittelkreislaufs (C1) erfasst, wobei
    die Steuereinheit (Cnt) eingerichtet ist, die erste Steuerung durchzuführen, in einem Fall, in dem der erste Verdichter (1) und der zweite Verdichter (14) gestoppt sind und der erfasste Druck im Niederdruckteil des ersten Kältemittelkreislaufs (C1) der Referenzwert oder mehr ist.
  8. Kältekreislaufvorrichtung nach einem der Ansprüche 1 bis 7, wobei
    das erste Kältemittel des ersten Kältemittelströmungsdurchgangs durch das zweite Kältemittel gekühlt wird, wenn das zweite Kältemittel im zweiten Kältemittelströmungsdurchgang strömt.
EP17906434.0A 2017-04-17 2017-04-17 Kältekreislaufvorrichtung Active EP3614071B1 (de)

Applications Claiming Priority (1)

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PCT/JP2017/015474 WO2018193498A1 (ja) 2017-04-17 2017-04-17 冷凍サイクル装置

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EP3614071B1 true EP3614071B1 (de) 2021-12-22

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US20220097487A1 (en) * 2019-01-09 2022-03-31 Hanon Systems Thermal management system

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JP3166334B2 (ja) * 1992-07-15 2001-05-14 ダイキン工業株式会社 二元冷凍機
CN100342193C (zh) * 2002-09-26 2007-10-10 海尔集团公司 环保无氟超低温冷柜
CN100417875C (zh) * 2004-06-11 2008-09-10 大金工业株式会社 过冷却装置
JP4944828B2 (ja) * 2008-03-31 2012-06-06 サンデン株式会社 冷熱システム
JP5551882B2 (ja) * 2009-02-24 2014-07-16 ダイキン工業株式会社 ヒートポンプシステム
US8011191B2 (en) * 2009-09-30 2011-09-06 Thermo Fisher Scientific (Asheville) Llc Refrigeration system having a variable speed compressor
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Publication number Priority date Publication date Assignee Title
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JPWO2018193498A1 (ja) 2019-11-14
JP6758485B2 (ja) 2020-09-23
EP3614071A4 (de) 2020-03-11
ES2905756T3 (es) 2022-04-12
WO2018193498A1 (ja) 2018-10-25
EP3614071A1 (de) 2020-02-26
CN110494702A (zh) 2019-11-22
CN110494702B (zh) 2021-06-15

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