WO2017221382A1 - Dispositif de réfrigération binaire - Google Patents

Dispositif de réfrigération binaire Download PDF

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Publication number
WO2017221382A1
WO2017221382A1 PCT/JP2016/068697 JP2016068697W WO2017221382A1 WO 2017221382 A1 WO2017221382 A1 WO 2017221382A1 JP 2016068697 W JP2016068697 W JP 2016068697W WO 2017221382 A1 WO2017221382 A1 WO 2017221382A1
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Prior art keywords
low
refrigerant
side refrigerant
expansion valve
condenser
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PCT/JP2016/068697
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English (en)
Japanese (ja)
Inventor
智也 藤本
智隆 石川
悠介 有井
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to GB1818273.3A priority Critical patent/GB2565472B/en
Priority to PCT/JP2016/068697 priority patent/WO2017221382A1/fr
Priority to JP2018523237A priority patent/JP6664478B2/ja
Publication of WO2017221382A1 publication Critical patent/WO2017221382A1/fr

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    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B40/06—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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • 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
    • 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
    • F25B2400/0419—Refrigeration circuit bypassing means for the superheater
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • 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
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2501—Bypass valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the present invention relates to a binary refrigeration apparatus, and more particularly to a binary refrigeration apparatus having an auxiliary radiator on the low-source refrigeration cycle side.
  • a high-source refrigeration cycle that is a refrigeration cycle device for circulating a high-temperature side refrigerant
  • a low-source that is a refrigeration cycle device for circulating a cold-temperature side refrigerant
  • a binary refrigeration apparatus having a refrigeration cycle is used.
  • a binary refrigeration system for example, a cascade condenser configured so that heat exchange can be performed between a low-source side condenser in a low-source refrigeration cycle and a high-side evaporator in a high-source refrigeration cycle, The original refrigeration cycle and the high refrigeration cycle are connected.
  • an auxiliary radiator is installed in front of the cascade condenser, and the refrigerant discharged from the low-temperature side compressor is radiated by the auxiliary radiator to be cooled, thereby improving the operation efficiency.
  • the present invention has been made in view of the above-described problems in the prior art, and provides a binary refrigeration apparatus capable of improving the heat exchange amount in an auxiliary radiator while improving the refrigeration capacity in a high-source refrigeration cycle.
  • the purpose is to provide.
  • the binary refrigeration apparatus of the present invention is a high-side refrigerant that connects a high-side compressor, a high-side condenser, a high-side expansion valve, and a high-side evaporator through piping and circulates the high-side refrigerant.
  • a high-source refrigeration cycle that forms a circuit, and a low-side compressor, auxiliary radiator, low-side condenser, low-side expansion valve, and low-side evaporator are connected by piping to circulate the low-side refrigerant.
  • a low original refrigeration cycle that forms a low original refrigerant circuit, the high original evaporator and the low original condenser, the high original refrigerant flowing through the high original refrigerant circuit, and the low original
  • a two-stage refrigeration apparatus comprising a first cascade condenser that exchanges heat with the low-side refrigerant flowing in the side-side refrigerant circuit, from the downstream of the high-side condenser in the high-source refrigeration cycle
  • a branch circuit that branches and returns to the upstream side of the high-side expansion valve; and the branch circuit provided in the branch circuit. Operation of each device provided in the second cascade condenser that exchanges heat between the flowing high-side refrigerant and the low-side refrigerant flowing out of the low-side evaporator, and the binary refrigeration apparatus And a control device for controlling.
  • the low-source side refrigerant discharged from the low-side compressor is provided with superheat to the low-side refrigerant using the second cascade condenser.
  • the discharge temperature By increasing the discharge temperature, the amount of heat exchange in the auxiliary radiator can be improved, and the high-side enthalpy can be increased to improve the high-side refrigeration capacity.
  • FIG. 3 is a block diagram illustrating an example of a configuration of a binary refrigeration apparatus according to Embodiment 1.
  • FIG. It is a block diagram which shows an example of a structure of the binary refrigeration apparatus which concerns on Embodiment 2.
  • FIG. 6 is a block diagram illustrating an example of a configuration of a binary refrigeration apparatus according to Embodiment 3.
  • FIG. It is a block diagram which shows an example of a structure of the binary refrigeration apparatus which concerns on Embodiment 4.
  • Embodiment 1 FIG.
  • the binary refrigeration apparatus according to Embodiment 1 of the present invention will be described.
  • FIG. 1 is a block diagram illustrating an example of the configuration of the binary refrigeration apparatus 1 according to the first embodiment.
  • the binary refrigeration apparatus 1 includes a low original refrigeration cycle 10, a high original refrigeration cycle 20, and a control device 40.
  • the low-source refrigeration cycle 10 and the high-source refrigeration cycle 20 constitute a refrigerant circuit that circulates the refrigerant independently of each other.
  • a low-source side condenser 13 in a low-source refrigeration cycle 10 to be described later, and a high-side evaporator 24 in a high-source refrigeration cycle 20 are coupled so as to exchange heat between the refrigerants passing through the first cascade capacitor 30.
  • FIG. 1 shows the direction through which a refrigerant
  • the expression of elevation including temperature, pressure, etc. is not particularly defined in relation to absolute values, but is relatively determined by the state, operation, etc. of the system, device, etc.
  • the low-side compressor 11 sucks low-temperature and low-pressure low-side refrigerant, compresses the refrigerant, and discharges it in a high-temperature and high-pressure state.
  • the low-source side compressor 11 for example, an inverter compressor that can control the rotation speed by an inverter circuit or the like and can control the capacity can be used.
  • the auxiliary radiator 12 performs heat exchange between the low-side refrigerant discharged from the low-side compressor 11 and the outside air such as outdoor air.
  • the auxiliary radiator 12 is a heat exchanger that heats the outside air by releasing heat from the low-side refrigerant to the outside air.
  • the auxiliary radiator 12 functions as a gas cooler, for example, and exchanges heat with outside air, water, brine, and the like.
  • the low-side condenser 13 condenses and liquefies the low-side refrigerant that has passed through the auxiliary radiator 12 to form a liquid refrigerant.
  • the low-side condenser 13 is configured by a heat transfer tube or the like through which the low-side refrigerant flowing through the low-source refrigeration cycle 10 passes, and the low-side refrigerant is high It is assumed that heat exchange is performed with the refrigerant flowing through the refrigeration cycle 20.
  • the low-side expansion valve 14 expands by reducing the pressure by adjusting the flow rate of the low-side refrigerant that has passed through the low-side condenser 13.
  • a flow rate control means such as an electronic expansion valve, a capillary such as a capillary, a refrigerant flow rate adjustment means such as a temperature-sensitive expansion valve, or the like can be used.
  • the low-side evaporator 15 performs heat exchange between the low-side refrigerant decompressed by the low-side expansion valve 14 and room air such as air in a freezing room that is a cooling target. It is evaporated into a gaseous refrigerant.
  • the object to be cooled is cooled directly or indirectly by heat exchange with the low-source refrigerant.
  • the high-source refrigeration cycle 20 includes a high-side compressor 21, a high-side condenser 22, a high-side expansion valve 23, and a high-side evaporator 24.
  • the high-source refrigeration cycle 20 forms a high-side refrigerant circuit in which the high-side refrigerant circulates by sequentially connecting these devices in a ring shape through refrigerant piping.
  • a branch circuit 20a in which refrigerant piping branches is formed between the high-source side condenser 22 and the high-source side expansion valve 23.
  • the branch circuit 20 a is formed so as to branch from the downstream side of the high-side condenser 22 and return to the upstream side of the high-side expansion valve 23.
  • the branch circuit 20 a is provided with a second cascade capacitor 26.
  • the high-end compressor 21 sucks low-temperature and low-pressure high-end refrigerant, compresses the refrigerant, and discharges it in a high-temperature and high-pressure state.
  • the high-end compressor 21 for example, an inverter compressor or the like whose capacity can be controlled by controlling the rotation speed by an inverter circuit or the like can be used.
  • the high-side expansion valve 23 is a decompression device, a throttling device, or the like, and expands by reducing the pressure by adjusting the flow rate of the high-side refrigerant that has passed through the high-side condenser 22.
  • a flow rate control unit such as an electronic expansion valve, a capillary tube such as a capillary, a refrigerant flow rate adjustment unit such as a temperature-sensitive expansion valve, or the like can be used.
  • the high original side evaporator 24 performs heat exchange between the high original side refrigerant decompressed by the high original side expansion valve 23 and the low original side refrigerant that has passed through the auxiliary radiator 12 of the low original refrigeration cycle 10.
  • the high-side refrigerant is evaporated to form a low-temperature gaseous refrigerant.
  • the high-side evaporator 24 is configured by a heat transfer tube or the like through which the high-side refrigerant flowing through the high-source refrigeration cycle 20 passes in the first cascade condenser 30, and the high-side refrigerant is low It is assumed that heat exchange is performed with the low-source refrigerant flowing through the refrigeration cycle 10.
  • the second cascade condenser 26 is a medium-high-pressure liquid high-side refrigerant condensed and liquefied by the high-side condenser 22 and a low-temperature low-pressure gaseous low-side refrigerant that is sucked into the low-side compressor 11.
  • Exchange heat it is assumed that the temperature of the high-side refrigerant condensed and liquefied by the high-side condenser 22 is higher than the temperature of the low-side refrigerant sucked into the low-side compressor 11.
  • the high-side refrigerant becomes a liquid refrigerant to which a degree of supercooling is given, and flows into the high-side expansion valve 23 via the branch circuit 20a.
  • the low-source side refrigerant becomes a gas refrigerant to which the degree of superheat is imparted, and is sucked into the low-source side compressor 11.
  • the first cascade condenser 30 is an inter-refrigerant heat exchanger that exchanges heat between the low-source side refrigerant flowing through the low-end side condenser 13 and the high-end side refrigerant flowing through the high-end side evaporator 24.
  • the first cascade capacitor 30 functions as the low-side condenser 13 and also functions as the high-side evaporator 24.
  • the control device 40 includes, for example, software executed on an arithmetic device such as a microcomputer or a CPU (Central Processing Unit), hardware such as a circuit device that realizes various functions, and the like. Control driving.
  • the control apparatus 40 is based on the operation information of the binary refrigeration apparatus 1 based on the information received from various detection means, and the operation content instruct
  • the outside temperature sensor 41 is connected to the control device 40.
  • the outside air temperature sensor 41 is provided for detecting the temperature of outside air such as outdoor air.
  • the outside air temperature sensor 41 supplies the detected outside air temperature to the control device 40.
  • the refrigerant circuit will be opened locally.
  • the refrigerant pipes are brazed at a plurality of locations on site by a contractor. Therefore, refrigerant leakage may occur from the brazed part.
  • the length of the refrigerant piping connected to the low-source side refrigeration equipment assumed to be placed outdoors is For example, it may reach about 100 m.
  • the number of places where pipes are connected on site increases further, so that the possibility of refrigerant leakage from the pipe connection part is further increased.
  • the length of the refrigerant pipe may be 100 m or more. Therefore, the possibility of refrigerant leakage is further increased.
  • the refrigerant pipes constructed locally will be placed in various environmental locations.
  • a refrigerated warehouse it may be placed in a corrosive environment due to corrosive gas generated from stored items.
  • Corrosion of copper in a corrosive atmosphere is generally considered to be ant colony corrosion by carboxylic acid such as acetic acid, stress corrosion cracking by ammonia or the like, corrosion by acid such as sulfurous acid gas, and the like.
  • sulfur-based gases such as hydrogen sulfide are used outdoors such as near hot springs and around food factories that produce processed products such as eggs. It is conceivable that corrosion of copper pipes due to sulfur-based substances occurs even in places where such a phenomenon occurs.
  • carbon dioxide (CO 2 ) having a small global warming potential (GWP) indicating an influence on global warming is used as the low-source refrigerant circulating in the low-source refrigeration cycle 10.
  • GWP global warming potential
  • a mixed refrigerant containing CO 2 is used.
  • HFC hydrofluorocarbon
  • R32, R404A, R407C, R410A, and HFC134a propane, isobutane, and the like
  • a refrigerant having a high global warming potential or a mixed refrigerant containing any of these may be used.
  • the low-source side refrigerant circulating in the low-source refrigeration cycle 10 and the high-source side refrigerant circulating in the high-source refrigeration cycle 20 it is more preferable to use a refrigerant that has higher efficiency than the low-source-side refrigerant circulating in the low-source refrigeration cycle 10.
  • the high-side compressor 21 sucks and compresses the high-side refrigerant and discharges it in a high-temperature and high-pressure state.
  • the discharged high-side refrigerant flows into the high-side condenser 22.
  • the high-side condenser 22 performs heat exchange between the outside air supplied by driving the fan 25 and the high-side refrigerant, and condenses and liquefies the high-side refrigerant.
  • the high-side refrigerant that has been condensed and liquefied passes through the high-side expansion valve 23.
  • the high-side expansion valve 23 depressurizes the high-side refrigerant that has been condensed and liquefied.
  • the reduced high-side refrigerant flows into the high-side evaporator 24.
  • the high-side evaporator 24 performs heat exchange between the high-side refrigerant depressurized by the first cascade condenser 30 and the low-side refrigerant passing through the low-side condenser 13, so that the high-side refrigerant is Is evaporated and gasified.
  • the high-side refrigerant that has been vaporized and gasified is sucked into the high-side compressor 21.
  • the high-side refrigerant condensed and liquefied by the high-side condenser 22 flows through the branch circuit 20a and also flows into the second cascade capacitor 26.
  • the second cascade capacitor 26 exchanges heat between the high-side refrigerant condensed and liquefied and the low-side refrigerant evaporated by the low-side evaporator 15 to increase the degree of supercooling in the high-side refrigerant.
  • the supercooling degree is given to the high-source-side refrigerant, the enthalpy in the high-source-side refrigerant circuit becomes larger than when the supercooling degree is not given.
  • the high-side refrigerant provided with the degree of supercooling flows through the branch circuit 20 a and passes through the high-side expansion valve 23.
  • the low-side compressor 11 sucks and compresses the low-side refrigerant and discharges it in a high-temperature and high-pressure state.
  • the discharged low-source-side refrigerant flows into the auxiliary radiator 12.
  • the auxiliary radiator 12 performs heat exchange between the outside air and the low-source side refrigerant.
  • the low-side refrigerant that has passed through the auxiliary radiator 12 flows into the low-side condenser 13.
  • the low-side condenser 13 performs heat exchange between the low-side refrigerant that has flowed in and the high-side refrigerant that passes through the high-side evaporator 24 by the first cascade condenser 30. To condense. The low-side refrigerant that has been condensed and liquefied passes through the low-side expansion valve 14. The low-side expansion valve 14 depressurizes the condensed low-side refrigerant. The reduced low-side refrigerant flows into the low-side evaporator 15.
  • the low-side evaporator 15 performs heat exchange between the reduced-low side refrigerant and the object to be cooled, and evaporates and gasifies the low-side refrigerant.
  • the low-source-side refrigerant that has been vaporized gas passes through the second cascade condenser 26.
  • the second cascade condenser 26 performs heat exchange between the low-source refrigerant that has been vaporized and the high-generator refrigerant that has been condensed and liquefied, and imparts superheat to the low-source refrigerant.
  • the low-source-side refrigerant to which the degree of superheat is imparted is sucked into the low-source-side compressor 11.
  • the low-side refrigerant indicating the discharge temperature of the low-side refrigerant discharged from the low-side compressor 11 is shown.
  • the discharge temperature is higher than when the superheat degree is not given.
  • the temperature difference between the temperature of the outside air and the low-side refrigerant discharge temperature becomes high.
  • the high-side compressor 21, the high-side condenser 22, the high-side expansion valve 23, and the high-side evaporator 24 are connected by piping.
  • a low-side refrigeration cycle 10 forming a low-side refrigerant circuit that circulates the low-side refrigerant and a high-side evaporator 24 and a low-side condenser 13.
  • a first cascade condenser 30 that exchanges heat between the high-end refrigerant flowing through the high-end refrigerant circuit and the low-end refrigerant flowing through the low-end refrigerant circuit.
  • the binary refrigeration apparatus 1 is provided in the branch circuit 20a that branches from the downstream of the high-side condenser 22 in the high-source refrigeration cycle 20 and returns to the upstream of the high-side expansion valve 23, and the branch circuit 20a.
  • a second cascade condenser 26 that exchanges heat between the high-end refrigerant flowing through the circuit 20a and the low-end refrigerant flowing out of the low-end evaporator 15, and each device provided in the binary refrigeration apparatus 1 And a control device 40 for controlling the operation.
  • the high original refrigerant flowing through the branch circuit 20a and the low original refrigerant flowing out of the low original evaporator 15 perform heat exchange, whereby the high original refrigerant Since the temperature is higher than the temperature of the low-source side refrigerant, the degree of supercooling is given to the high-source side refrigerant. At the same time, the degree of superheat is imparted to the low-source refrigerant.
  • the refrigeration capacity of the high-side refrigerant circuit that is, the high-source refrigeration cycle 20 is improved. Can do. Further, the capacity of the high-end compressor 21 can be reduced.
  • the degree of superheat of the low-side refrigerant sucked into the low-side compressor 11 is increased by giving the superheat degree to the low-side refrigerant, the low-side side in the low-side compressor 11
  • the refrigerant discharge temperature can be increased.
  • the temperature of the low-source side refrigerant flowing into the auxiliary radiator 12 can be made higher than before. Therefore, the temperature difference with the outside air which performs heat exchange in the auxiliary radiator 12 can be increased, the amount of heat exchange in the auxiliary radiator 12 can be improved, and the auxiliary radiator 12 can be effectively used.
  • Embodiment 2 the binary refrigeration apparatus 1 according to Embodiment 2 will be described.
  • the second embodiment is different from the first embodiment described above in that a flow rate adjusting valve is provided in the branch circuit 20a of the high-side refrigerant circuit.
  • FIG. 2 is a block diagram illustrating an example of the configuration of the binary refrigeration apparatus 1 according to the second embodiment.
  • the binary refrigeration apparatus 1 includes a low-source refrigeration cycle 10, a high-source refrigeration cycle 20, a first cascade capacitor 30, and a control device 40, as in the first embodiment.
  • a branch circuit 20 a is provided in the high-side refrigerant circuit of the refrigeration cycle 20.
  • the branch circuit 20a is provided with a flow rate adjusting valve 42.
  • a discharge temperature sensor 43 is provided on the discharge side of the low-source compressor 11.
  • the flow rate adjustment valve 42 is provided to adjust the flow rate of the high-side refrigerant flowing into the branch circuit 20a, and the opening degree is controlled by the control device 40.
  • a flow rate controlling means such as an electronic expansion valve, a capillary such as a capillary, a refrigerant flow rate adjusting means such as a temperature sensitive expansion valve, or the like can be used.
  • the discharge temperature sensor 43 is provided to detect the low-side refrigerant discharge temperature in the low-side compressor 11.
  • the discharge temperature sensor 43 supplies information indicating the detected low-source-side refrigerant discharge temperature to the control device 40.
  • control device 40 further controls the flow rate based on the outside air temperature supplied from the outside air temperature sensor 41 and the low-source refrigerant discharge temperature supplied from the discharge temperature sensor 43.
  • the opening degree of the regulating valve 42 is controlled.
  • the flow rate adjustment valve 42 When the temperature of the low-side refrigerant discharged from the low-side compressor 11 is low, the flow rate adjustment valve 42 is set to the “open” state. In this case, the high-side condensed and liquefied by the high-side condenser 22 The side refrigerant passes through the high-side expansion valve 23 and also flows into the branch circuit 20a. The high-side refrigerant that has flowed into the branch circuit 20a flows into the second cascade condenser 26 and exchanges heat with the low-side refrigerant that has been vaporized and gasified by the low-side evaporator 15. Thereby, a supercooling degree is provided to the high-source side refrigerant. The high-side refrigerant provided with the degree of supercooling flows through the branch circuit 20 a and passes through the high-side expansion valve 23.
  • the flow rate adjustment valve 42 is in a “closed” state, and in this case, the low-side side refrigerant 22 is condensed and liquefied by the high-side condenser 22.
  • the high-side refrigerant does not flow into the branch circuit 20a and passes through the high-side expansion valve 23.
  • the high-side refrigerant that has passed through the high-side expansion valve 23 is decompressed and flows into the high-side evaporator 24.
  • the high-side refrigerant flowing into the high-side evaporator 24 is heat-exchanged with the low-side refrigerant passing through the low-side condenser 13 by the first cascade condenser 30, and is evaporated and gasified. Is done. Then, the high-side refrigerant that has been vaporized is sucked into the high-side compressor 21.
  • the heat exchange amount Q [W] indicating the capability of the heat exchanger can be generally expressed by the formula (1).
  • K indicates the heat passage rate [W / m 2 ⁇ K] of the heat exchanger, and is determined by the specifications of the heat exchanger and the air volume combined in the case of the air heat exchanger. Is done.
  • A indicates the heat transfer area [m 2 ] of the heat exchanger, and is determined by the area of the heat exchanger.
  • ⁇ T m indicates an average temperature difference [K] between the two media that perform heat exchange.
  • heat transfer coefficient K and the heat transfer area A is always assumed to take the same value, by increasing the average temperature difference [Delta] T m, it is possible to increase the heat exchange amount Q. That is, by increasing the temperature of the refrigerant flowing into the heat exchanger, it is possible to increase the average temperature difference [Delta] T m, it is possible to increase the heat exchange amount Q.
  • the low-end side refrigerant discharge temperature in the low-end side compressor 11 can be increased by controlling the opening degree of the flow rate adjusting valve 42, and thereby the auxiliary radiator 12.
  • the temperature of the low-side refrigerant flowing into the refrigerant increases, and the amount of heat exchange in the auxiliary radiator 12 can be increased.
  • control for improving the refrigeration capacity in the low-source refrigeration cycle 10 and the high-source refrigeration cycle 20 will be described.
  • a case is considered in which, based on control by the control device 40, the opening degree of the low-side expansion valve 14 is increased so that the low-side refrigerant flowing out of the low-side evaporator 15 enters a gas-liquid two-phase state.
  • the low-side refrigerant in the gas-liquid two-phase state and the cooling target such as air in the refrigerator Will exchange heat.
  • the amount of heat exchange in the second cascade condenser 26 that performs heat exchange between the low-side refrigerant flowing out of the low-side evaporator 15 and the high-side refrigerant flowing through the branch circuit 20a also increases. Therefore, the degree of supercooling imparted to the high-source-side refrigerant can be increased, and the enthalpy in the high-source-side refrigerant circuit is increased, so that the refrigeration capacity of the high-source refrigeration cycle 20 can be improved.
  • the binary refrigeration apparatus 1 detects the outside air temperature sensor 41 that detects the temperature of the outside air and the discharge temperature of the low-side refrigerant discharged from the low-side compressor 11. And a flow rate adjusting valve 42 for adjusting the flow rate of the high-side refrigerant flowing into the branch circuit 20a.
  • the control device 40 detects the detection result by the outside air temperature sensor 41 and the discharge temperature sensor 43. Based on the detection result, the opening degree of the flow rate adjustment valve 42 is controlled.
  • the opening degree of the flow rate adjustment valve 42 is controlled based on the low-source refrigerant discharge temperature detected by the discharge temperature sensor 43 and the outside air temperature detected by the outside air temperature sensor 41. To do. Therefore, the temperature difference between the low-side refrigerant discharge temperature flowing into the auxiliary radiator 12 and the outside air temperature can be increased, and the auxiliary radiator 12 can be effectively used as in the first embodiment. As a result, even when the low-side refrigerant discharge temperature in the low-side compressor 11 is difficult to rise and the evaporation temperature of the low-side evaporator 15 is high, the cooling capacity of the low-side refrigerant circuit is ensured. be able to.
  • an upper limit is set for the discharge temperature of the compressor in order to prevent problems such as failure of the compressor.
  • the temperature of the low-side refrigerant sucked into the low-side compressor 11 is adjusted by controlling the opening degree of the flow rate adjustment valve 42, and the low-side side in the low-side compressor 11 is adjusted.
  • the refrigerant discharge temperature can be adjusted. For this reason, it is possible to prevent a malfunction of the low-side compressor 11 due to an increase in the low-side refrigerant discharge temperature, and to extend the life of the low-side compressor 11.
  • Embodiment 3 the binary refrigeration apparatus 1 according to the third embodiment will be described.
  • the third embodiment is that a low-side injection circuit that connects between the low-side condenser and the low-side expansion valve and between the low-side evaporator and the low-side compressor is provided. This is different from the second embodiment described above.
  • FIG. 3 is a block diagram illustrating an example of the configuration of the binary refrigeration apparatus 1 according to the third embodiment.
  • the binary refrigeration apparatus 1 includes a low-source refrigeration cycle 10, a high-source refrigeration cycle 20 provided with a branch circuit 20a, a first cascade capacitor 30, and a control device, as in the second embodiment. 40.
  • the low-source side refrigerant circuit of the low-source refrigeration cycle 10 is formed with a low-source-side injection circuit 10a.
  • the low-side injection circuit 10 a is a branch circuit that connects between the low-side condenser 13 and the low-side expansion valve 14 and between the low-side evaporator 15 and the low-side compressor 11.
  • the low expansion side injection circuit 10a is provided with an injection expansion valve 51.
  • the injection expansion valve 51 is provided to adjust the flow rate of the low-side refrigerant flowing into the low-side injection circuit 10a, and the opening degree is controlled by the control device 40.
  • a flow rate control means such as an electronic expansion valve, a capillary such as a capillary, a refrigerant flow rate adjustment means such as a temperature-sensitive expansion valve, or the like can be used.
  • an electronic expansion valve capable of adjusting the low-side refrigerant discharge temperature in the low-side compressor 11 can be used as the injection expansion valve 51.
  • the control device 40 controls the opening degree of the injection expansion valve 51 based on the low-side refrigerant discharge temperature in the low-side compressor 11 supplied from the discharge temperature sensor 43.
  • the second cascade capacitor 26 provided in the low-source side injection circuit 10a flows through the high-side refrigerant flowing through the high-side branch circuit 20a and the low-side injection circuit 10a and is throttled by the injection expansion valve 51. Heat exchange is performed with the low-side refrigerant in the low-temperature low-pressure gas-liquid two-phase state.
  • the low-side refrigerant condensed and liquefied by the low-side condenser 13 passes through the low-side expansion valve 14 and also flows into the low-side injection circuit 10a.
  • the low-side refrigerant flowing into the low-side injection circuit 10 a passes through the injection expansion valve 51.
  • the injection expansion valve 51 squeezes the condensed low liquefied refrigerant to form a low-temperature low-pressure gas-liquid two-phase low-source refrigerant.
  • the low-side refrigerant that has passed through the injection expansion valve 51 and has entered a low-temperature low-pressure gas-liquid two-phase state passes through the low-side evaporator 15 and is sucked into the low-side compressor 11.
  • the pressure is the same as that of the side refrigerant. This is because the downstream side of the injection expansion valve 51 is connected to the suction side of the low-side compressor 11.
  • the low-side refrigerant that has become a low-temperature low-pressure gas-liquid two-phase refrigerant passes through the second cascade capacitor 26.
  • the second cascade capacitor 26 performs heat exchange between the low-side refrigerant in a gas-liquid two-phase state at low temperature and low pressure and the high-side refrigerant condensed and liquefied.
  • the low-side refrigerant passing through the second cascade condenser 26 is applied by the low-side evaporator 15 as compared with the low-temperature and low-pressure gasified low-side refrigerant passing through the low-side evaporator 15.
  • the temperature is lowered by the degree of superheat. This is obtained by adding the degree of superheat given by the low-side evaporator 15 to the saturation temperature in which the temperature of the low-side refrigerant that has passed through the low-side evaporator 15 is converted from the low pressure on the low side. This is because the temperature of the low-side refrigerant that has passed through the injection expansion valve 51 is a saturation temperature converted from the low-pressure on the low-side side.
  • the temperature difference between the low-side refrigerant and the high-side refrigerant that is heat-exchanged in the second cascade condenser 26 is lower than the temperature difference in the second embodiment when it passes through the low-side evaporator 15. It increases by the degree of superheat imparted to the former refrigerant.
  • the high-side refrigerant that is a high-temperature and high-pressure liquid refrigerant that performs heat exchange with the second cascade condenser 26.
  • the enthalpy of the high yuan side can be enlarged and the refrigerating capacity of the high refrigeration cycle 20 can be improved.
  • a compressor with a small capacity can be used as the high-end compressor 21.
  • the binary refrigeration apparatus 1 includes the low-side evaporator 13 and the low-side compressor 11 between the low-side condenser 13 and the low-side expansion valve 14. And a low expansion side injection circuit 10a connected to the low expansion side injection circuit 10a.
  • the control device 40 is based on the detection result by the discharge temperature sensor 43, and the injection expansion valve The opening of 51 is controlled.
  • the temperature difference between the low-side refrigerant and the high-side refrigerant that performs heat exchange with the second cascade capacitor 26 can be made larger than those in the first and second embodiments, so that the high-side enthalpy is reduced.
  • the refrigeration capacity of the high-source refrigeration cycle 20 can be further improved.
  • Embodiment 4 FIG. Next, the binary refrigeration apparatus 1 according to the fourth embodiment will be described.
  • the fourth embodiment is different from the third embodiment described above in that an intake temperature sensor for detecting the temperature of the low-side refrigerant sucked on the suction side of the low-side compressor 11 is provided.
  • FIG. 4 is a block diagram illustrating an example of the configuration of the binary refrigeration apparatus 1 according to the fourth embodiment.
  • the binary refrigeration apparatus 1 includes a low-source refrigeration cycle 10 provided with a low-source injection circuit 10a and a high-source refrigeration cycle 20 provided with a branch circuit 20a, as in the third embodiment.
  • the first cascade capacitor 30 and the control device 40 are included.
  • a suction temperature sensor 44 is provided on the suction side of the low-source compressor 11.
  • the suction temperature sensor 44 is provided to detect a low-source-side refrigerant suction temperature indicating the suction temperature of the low-source-side refrigerant sucked into the low-source side compressor 11.
  • the suction temperature sensor 44 supplies information indicating the detected low-source side refrigerant suction temperature to the control device 40.
  • control device 40 further includes the outside air temperature supplied from the outside air temperature sensor 41, the low-side refrigerant discharge temperature supplied from the discharge temperature sensor 43, and the suction Based on the low-source side refrigerant suction temperature supplied from the temperature sensor 44, the opening degree of the injection expansion valve 51 is controlled.
  • the binary refrigeration apparatus 1 further includes the suction temperature sensor 44 that detects the suction temperature of the low-side refrigerant sucked into the low-side compressor 11, and includes the control device 40. Controls the opening degree of the injection expansion valve 51 based on the detection result by the outside air temperature sensor 41, the detection result by the discharge temperature sensor 43, and the detection result by the suction temperature sensor 44. Thereby, the operation range of the low-side compressor 11 can be secured, and problems such as a failure of the low-side compressor 11 can be prevented.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

Un dispositif de réfrigération binaire comprend : un cycle de réfrigération d'ordre supérieur dans lequel un compresseur, un condensateur, une soupape de détente, et un évaporateur, tous côté ordre supérieurs sont reliés par une tuyauterie et forment un circuit de réfrigérant du côté ordre supérieur dans lequel circule un réfrigérant; un cycle de réfrigération d'ordre inférieur dans lequel un compresseur, un radiateur auxiliaire, un condenseur , une soupape de détente et un évaporateur, tous côté ordre inférieur sont reliés par une tuyauterie et forment un circuit de réfrigérant côté ordre inférieur dans lequel circule un réfrigérant; et un premier condenseur en cascade composé de l'évaporateur côté ordre supérieur et du condensateur côté ordre inférieur et qui effectue un échange de chaleur entre le réfrigérant s'écoulant dans le circuit de réfrigérant côté ordre supérieur et le réfrigérant qui s'écoule dans le circuit de réfrigérant côté ordre inférieur. Le dispositif de réfrigération binaire comprend : un circuit de dérivation qui se ramifie à partir du côté aval du condenseur dans le cycle de réfrigération d'ordre supérieur et qui revient vers le côté amont de la soupape de détente d'ordre supérieur; un second condenseur en cascade disposé dans le circuit de dérivation et qui effectue un échange de chaleur entre le réfrigérant côté ordre supérieur s'écoulant dans le circuit de dérivation et le réfrigérant côté ordre inférieur s'écoulant à partir de l'évaporateur côté ordre inférieur; et un dispositif de commande du fonctionnement de chaque appareil prévu dans le dispositif de réfrigération binaire.
PCT/JP2016/068697 2016-06-23 2016-06-23 Dispositif de réfrigération binaire WO2017221382A1 (fr)

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GB1818273.3A GB2565472B (en) 2016-06-23 2016-06-23 Cascade refrigeration system
PCT/JP2016/068697 WO2017221382A1 (fr) 2016-06-23 2016-06-23 Dispositif de réfrigération binaire
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WO2022211077A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif de cycle frigorifique
WO2022211076A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif de cycle frigorifique
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CN108692475A (zh) * 2018-06-08 2018-10-23 贺吉军 一种喷气增焓制冷机
JP2021011985A (ja) * 2019-07-08 2021-02-04 富士電機株式会社 二元冷凍機
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WO2022211078A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif à cycle de réfrigération
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JP7208577B2 (ja) 2021-03-31 2023-01-19 ダイキン工業株式会社 冷凍サイクル装置
JP7208576B2 (ja) 2021-03-31 2023-01-19 ダイキン工業株式会社 冷凍サイクル装置
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WO2022211077A1 (fr) * 2021-03-31 2022-10-06 ダイキン工業株式会社 Dispositif de cycle frigorifique
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JP6664478B2 (ja) 2020-03-13
GB2565472B (en) 2020-11-18

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