EP4053470A1 - Kältekreislaufvorrichtung - Google Patents

Kältekreislaufvorrichtung Download PDF

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Publication number
EP4053470A1
EP4053470A1 EP19950515.7A EP19950515A EP4053470A1 EP 4053470 A1 EP4053470 A1 EP 4053470A1 EP 19950515 A EP19950515 A EP 19950515A EP 4053470 A1 EP4053470 A1 EP 4053470A1
Authority
EP
European Patent Office
Prior art keywords
port
expansion valve
heat exchanger
refrigeration cycle
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP19950515.7A
Other languages
English (en)
French (fr)
Other versions
EP4053470A4 (de
Inventor
Tomotaka Ishikawa
Yusuke Arii
Motoshi HAYASAKA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of EP4053470A1 publication Critical patent/EP4053470A1/de
Publication of EP4053470A4 publication Critical patent/EP4053470A4/de
Pending legal-status Critical Current

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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
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • 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
    • 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
    • F25B2400/13—Economisers
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a refrigeration cycle apparatus which includes a receiver for storing a refrigerant.
  • Patent Literature 1 discloses an outdoor unit for heat-pump water heater, which includes an intermediate pressure receiver into which a refrigerant, decompressed by an expansion valve, flows.
  • a refrigerant having a pressure (an intermediate pressure) smaller than a refrigerant discharged from a compressor and greater than a refrigerant drawn into the compressor flows into the intermediate pressure receiver disclosed in Patent Literature 1.
  • variations in operating load required from the refrigeration cycle apparatus may cause abrupt reduction in pressure and temperature of the refrigerant discharged from the compressor.
  • the abrupt reduction in pressure and temperature of the refrigerant deteriorates the reliability of the refrigeration cycle apparatus.
  • the present invention is made in view of the problem as described above, and an object of the present invention is to provide a refrigeration cycle apparatus having improved reliability.
  • a refrigerant circulates in order from a compressor, a first heat exchanger, a second heat exchanger, a first expansion valve, and a third heat exchanger.
  • the refrigeration cycle apparatus includes a receiver, a second expansion valve, a first flow passage, a second flow passage, a vent tube, and a third expansion valve.
  • the receiver has a first port, a second port, and a third port.
  • the third port is located higher than the second port.
  • the second expansion valve is connected to the second port.
  • the first flow passage connects the second expansion valve to the compressor via the second heat exchanger.
  • the second flow passage connects the first heat exchanger to the second heat exchanger.
  • the vent tube connects the third port to a portion of the first flow passage between the second expansion valve and the second heat exchanger.
  • the third expansion valve is connected between the second flow passage and the first port.
  • the third expansion valve is connected between the second flow passage and the first port, thereby achieving the refrigeration cycle apparatus having improved reliability.
  • Fig. 1 is a functional block diagram showing a configuration of a refrigeration cycle apparatus 100 according to an embodiment.
  • Examples of the refrigeration cycle apparatus 100 include a refrigerator, an air-conditioner, and a showcase.
  • the refrigeration cycle apparatus 100 includes a compressor 1, a condenser 2 (a first heat exchanger), a heat inter changer (HIC) 3 (a second heat exchanger), an evaporator 4 (a third heat exchanger), an expansion valve 5 (a first expansion valve), an expansion valve 6 (a second expansion valve), an expansion valve 7 (a third expansion valve), a receiver 8, a vent tube 9, a controller 10, temperature sensors Sa1, Sa2, and Sa3, and pressure sensors Sb1 and Sb2.
  • the expansion valves 5 to 7 each include an electronic linear expansion valve (LEV), for example.
  • the vent tube 9 includes a capillary tube, for example.
  • the compressor 1 includes a discharge port P11, an intake port P12, and an injection port P13.
  • the compressor 1 is, for example, a high-pressure shell compressor, and stores, within the compressor 1, a lubricant for a compression mechanism.
  • a refrigerant circulates in the order of the discharge port P11, the condenser 2, the HIC 3, the expansion valve 5, the evaporator 4, and the intake port P12.
  • the receiver 8 has a port P71 (a first port), a port P72 (a second port), and a port P73 (a third port).
  • the ports P71 and P73 are formed on the top surface of the receiver.
  • the port P72 is formed on the bottom surface of the receiver 8 opposite the top surface.
  • the port P73 is located higher than the port P72.
  • the ports P71 to P73 may be formed on side surfaces of the receiver 8.
  • the expansion valve 6 is connected to the port P72.
  • the expansion valve 6 is connected by an injection flow passage FP1 (the first flow passage) to the injection port P13 via the HIC 3.
  • the vent tube 9 connects the port P73 to a portion of the injection flow passage FP1 between the expansion valve 6 and the HIC 3.
  • the condenser 2 and the HIC 3 are connected by a flow passage FP2 (a second flow passage).
  • the expansion valve 7 is connected between the flow passage FP2 and the port P71.
  • a portion of the refrigerant flowing out of the condenser 2 is guided to the expansion valve 7, decompressed by the expansion valve 7, and then flows out of the port P71 into the receiver 8.
  • An amount of refrigerant per unit time flowing into the receiver 8 through the port P71 is controlled by the valve travel of the expansion valve 7.
  • the refrigerant flowing out of the receiver 8 is decompressed and then drawn into the compressor 1 through the injection port P13.
  • the pressure of the refrigerant flowing into the receiver 8 is an intermediate pressure.
  • the receiver 8 is also capable of storing a supercritical refrigerant, such as carbon dioxide, in the form of liquid.
  • a supercritical refrigerant flowing out of the receiver 8 is supercooled.
  • the performance of the refrigeration cycle apparatus 100 can be improved by using a supercritical refrigerant.
  • a refrigerant in a liquid form (a liquid refrigerant) is stored into the receiver 8 at the bottom of the receiver 8
  • a refrigerant in a gas form (a gas refrigerant) is collected above the liquid level of the liquid refrigerant within the receiver 8.
  • a saturated liquid of the refrigerant flows out of the receiver 8 through the port P72.
  • the saturated liquid is decompressed by the expansion valve 6.
  • the gas refrigerant flowing out of the receiver 8 through the port P73 is guided by the vent tube 9 to the injection flow passage FP1.
  • the valve travel of the expansion valve 6 controls an amount of refrigerant flowing out of the receiver 8 through the port P72 per unit time. In other words, the valve travel of the expansion valve 6 adjusts the proportion of the gas refrigerant to the amount of liquid refrigerant within the refrigerant flowing into the HIC 3.
  • the greater the ratio of the amount of gas refrigerant to the refrigerant drawn into the compressor 1 through the injection port P13 the greater the reduction in temperature Td can be suppressed.
  • the greater ratio of the amount of liquid refrigerant to the refrigerant drawn into the compressor 1 through the injection port P13 the greater the reduction in pressure Pd can be suppressed. Therefore, adjusting the ratio enables adjustment of the distribution in which the effects of suppressing the reductions in pressure Pd and temperature Td are yielded.
  • the refrigerant flowing out of the receiver 8 is guided by the injection flow passage FP1 to the injection port P13 via the HIC 3.
  • the refrigerant from the condenser 2 is cooled by the refrigerant from the receiver 8.
  • the refrigerant is guided to the receiver 8 before being cooled by the HIC 3, thereby increasing the ratio (vapor quality) of gas refrigerant to the refrigerant flowing into the receiver 8 to about 0.5.
  • the proportion of the amount of gas refrigerant to the amount of liquid refrigerant within the refrigerant flowing out of the receiver 8 into the HIC 3 can be readily adjusted.
  • the controller 10 obtains from the temperature sensor Sa1 and the pressure sensor Sb1 the temperature Td and the pressure Pd, respectively, of the refrigerant discharged from the compressor 1.
  • the controller 10 obtains from the temperature sensor Sa2 and the pressure sensor Sb2 a temperature Ts and a pressure Ps, respectively, of the refrigerant drawn into the compressor 1.
  • the controller 10 obtains from the temperature sensor Sa3 a temperature T1 of the refrigerant flowing out of the condenser 2.
  • the controller 10 controls the drive frequency of the compressor 1 to control the amount of refrigerant discharged from the compressor 1 per unit time.
  • the controller 10 control the valve travels of the expansion valves 5 to 7.
  • the controller 10 controls the compressor 1 and the expansion valves 5 to 7 so that the temperature Td and a degree of supercooling of the refrigerant flowing out of the condenser 2 are respectively target values, for example.
  • the temperature Td has a target value of 100 degrees Celsius
  • the degree of supercooling has a target value of 5K.
  • Fig. 2 is a functional block diagram showing a configuration of the controller 10 of Fig. 1 .
  • the controller 10 includes a circuitry 11, a memory 12, and an input/output unit 13.
  • the circuitry 11 may be dedicated hardware, or a central processing unit (CPU) which executes programs stored in the memory 12. If the circuitry 11 is dedicated hardware, the circuitry 11 corresponds to, for example, a single circuit, a complex circuit, a programmed processor, a parallel programmed processor, an application specific integrated circuit (ASIC), a field programmable gate array (FPGA), or a combination thereof.
  • ASIC application specific integrated circuit
  • FPGA field programmable gate array
  • the circuitry 11 includes a non-volatile or volatile semiconductor memory (e.g., a random access memory (RAM), a read only memory (ROM), a flash memory, an erasable programmable read only memory (EPROM), or an electrically erasable programmable read only memory (EEPROM)), and a magnetic disk, a flexible disk, an optical disk, a compact disc, a mini disc, or a digital versatile disc (DVD).
  • RAM random access memory
  • ROM read only memory
  • EPROM erasable programmable read only memory
  • EEPROM electrically erasable programmable read only memory
  • the CPU is also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, a processor, or a digital signal processor (DSP).
  • DSP digital signal processor
  • Fig. 3 is a flowchart showing a flow of a process performed by the controller 10 of Fig. 1 .
  • the process illustrated in Fig. 3 is called at constant time intervals from the main routine that performs integrated processing on the refrigeration cycle apparatus 100. In the following description, the steps will be simply described as "S.”
  • the controller 10 determines whether the pressure Pd is less than a reference pressure Pref.
  • the reference pressure Pref is a lower limit for the pressure Pd that can ensure a desired compression ratio (Pd/Ps).
  • the reference pressure Pref can be calculated, as appropriate, by simulation, or experiment using actual apparatus.
  • the controller 10 determines whether the pressure Pd is greater than or equal to the reference pressure Pref (NO in S101). If the pressure Pd is greater than or equal to the reference pressure Pref (NO in S101), the controller 10, in S102, controls normal operation, and returns the process to the main routine. If the pressure Pd is less than the reference pressure Pref (YES in S101), the controller 10 reduces the valve travel of the expansion valve 7 in S103, and passes the process to S104.
  • the controller 10 determines whether a degree of superheat SH of the refrigerant discharged from the compressor 1 is greater than a reference value ⁇ .
  • the reference value ⁇ is used to determine whether the superheat of the refrigerant is sufficiently small so as to be regarded as 0K.
  • the reference value ⁇ can be calculated, as appropriate, by simulation, or experiment using actual apparatus.
  • the controller 10, in S105 increases the valve travel of the expansion valve 6, and returns the process to the main routine. If the degree of superheat SH is less than or equal to the reference value ⁇ (NO in S104), the controller 10, in S106, reduces the valve travel of the expansion valve 6, and returns the process to the main routine.
  • both the reduction in pressure Pd and the reduction in temperature Td can be suppressed. Suppressing the reduction in pressure Pd can prevent the pressure Pd from falling out of a range that the compressor 1 permits. Ensuring desired compression ratio can stabilize the performance of the refrigeration cycle apparatus 100. Moreover, suppressing the reduction in temperature Td allows the degree of superheat SH of the refrigerant discharged from the compressor 1 to be kept within a desired range. A situation is prevented in which a liquid refrigerant is drawn into the compressor 1 and the lubricant is diluted by the liquid refrigerant. Thus, the compression mechanism of the compressor 1 can be prevented from being worn out.
  • the refrigeration cycle apparatus of the embodiment As described above, according to the refrigeration cycle apparatus of the embodiment, the refrigeration cycle apparatus having improved reliability is achieved.

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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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP19950515.7A 2019-11-01 2019-11-01 Kältekreislaufvorrichtung Pending EP4053470A4 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/043094 WO2021084743A1 (ja) 2019-11-01 2019-11-01 冷凍サイクル装置

Publications (2)

Publication Number Publication Date
EP4053470A1 true EP4053470A1 (de) 2022-09-07
EP4053470A4 EP4053470A4 (de) 2022-11-16

Family

ID=75716103

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19950515.7A Pending EP4053470A4 (de) 2019-11-01 2019-11-01 Kältekreislaufvorrichtung

Country Status (4)

Country Link
EP (1) EP4053470A4 (de)
JP (2) JPWO2021084743A1 (de)
CN (2) CN117329723A (de)
WO (1) WO2021084743A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024102371A1 (en) * 2022-11-07 2024-05-16 Johnson Controls Tyco IP Holdings LLP Energy efficient heat pump systems and methods

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113071289B (zh) * 2021-04-28 2024-05-10 蔚来汽车科技(安徽)有限公司 一种电动汽车座舱加热系统及其控制方法

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03294750A (ja) * 1990-04-11 1991-12-25 Mitsubishi Electric Corp 冷凍装置
JP4687710B2 (ja) * 2007-12-27 2011-05-25 三菱電機株式会社 冷凍装置
JP5433158B2 (ja) * 2008-03-24 2014-03-05 日立アプライアンス株式会社 冷凍サイクル装置
JP4931848B2 (ja) 2008-03-31 2012-05-16 三菱電機株式会社 ヒートポンプ式給湯用室外機
JP2010127531A (ja) * 2008-11-27 2010-06-10 Mitsubishi Electric Corp 冷凍空調装置
JP5683075B2 (ja) * 2009-02-13 2015-03-11 三菱重工業株式会社 インジェクション管
JP6467682B2 (ja) * 2015-01-09 2019-02-13 パナソニックＩｐマネジメント株式会社 冷凍装置
JP6479203B2 (ja) * 2015-10-20 2019-03-06 三菱電機株式会社 冷凍サイクル装置
JP6680600B2 (ja) * 2016-04-14 2020-04-15 サンデン・オートモーティブクライメイトシステム株式会社 車両用空気調和装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024102371A1 (en) * 2022-11-07 2024-05-16 Johnson Controls Tyco IP Holdings LLP Energy efficient heat pump systems and methods

Also Published As

Publication number Publication date
CN114585866A (zh) 2022-06-03
JPWO2021084743A1 (de) 2021-05-06
WO2021084743A1 (ja) 2021-05-06
JP2024023437A (ja) 2024-02-21
EP4053470A4 (de) 2022-11-16
CN117329723A (zh) 2024-01-02

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