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WO2021048897A1 - Dispositif à cycle frigorifique - Google Patents

Dispositif à cycle frigorifique Download PDF

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Publication number
WO2021048897A1
WO2021048897A1 PCT/JP2019/035366 JP2019035366W WO2021048897A1 WO 2021048897 A1 WO2021048897 A1 WO 2021048897A1 JP 2019035366 W JP2019035366 W JP 2019035366W WO 2021048897 A1 WO2021048897 A1 WO 2021048897A1
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WO
WIPO (PCT)
Prior art keywords
port
mixed refrigerant
temperature
refrigeration cycle
azeotropic mixed
Prior art date
Application number
PCT/JP2019/035366
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English (en)
Japanese (ja)
Inventor
智隆 石川
英希 大野
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021544986A priority Critical patent/JP7258163B2/ja
Priority to PCT/JP2019/035366 priority patent/WO2021048897A1/fr
Publication of WO2021048897A1 publication Critical patent/WO2021048897A1/fr

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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • the present invention relates to a refrigeration cycle device in which a non-azeotropic mixed refrigerant circulates.
  • Patent Document 1 discloses a refrigerating apparatus in which a non-azeotropic mixed refrigerant circulates.
  • the pressure in the conduit in the evaporation process is lowered along the direction in which the non-coborous mixed refrigerant flows according to the temperature gradient of the non-coborous mixed refrigerant, so that the non-coborous mixture in the evaporator is mixed. It is possible to make the temperature of the refrigerant substantially uniform and suppress the uneven frost formation of the evaporator. As a result, it is possible to suppress a decrease in the coefficient of performance and the refrigerating capacity of the refrigerating apparatus.
  • the heat exchange efficiency in the evaporator is improved by setting the mode of heat exchange between the refrigerant and air in the evaporator as a countercurrent.
  • the temperature of the non-azeotropic mixed refrigerant in the evaporator becomes substantially uniform, improvement in heat exchange efficiency in the evaporator can be suppressed.
  • the present invention has been made to solve the above-mentioned problems, and an object of the present invention is to improve the performance of a refrigeration cycle apparatus.
  • the non-azeotropic mixed refrigerant circulates.
  • the refrigeration cycle device includes a compressor, a first heat exchanger, an expansion valve, a second heat exchanger, and a blower.
  • the second heat exchanger has a first port and a second port.
  • the blower forms an air flow that passes from the second port to the first port in this order.
  • the non-azeotropic mixed refrigerant circulates in the order of the compressor, the first heat exchanger, the expansion valve, the first port, and the second port.
  • the temperature gradient of the non-co-boiling mixed refrigerant which is the relationship between the dryness of the non-co-boiling mixed refrigerant and the temperature of the non-co-boiling mixed refrigerant, represents the dryness. It is represented as an upwardly convex monotonic increase curve in a coordinate plane having a horizontal axis and a vertical axis representing temperature.
  • the temperature gradient of the non-azeotropic mixed refrigerant circulating in the refrigeration cycle apparatus has a horizontal axis representing the degree of dryness.
  • the performance of the refrigeration cycle apparatus can be improved by expressing it as an upwardly convex monotonous increase curve in a coordinate plane having a vertical axis representing temperature.
  • FIG. 1 It is a functional block diagram which shows the structure of the refrigeration cycle apparatus which concerns on embodiment. It is an external perspective view of the evaporator of FIG. A straight line representing the relationship between the position in the flow path passing through the evaporator and the temperature of the refrigerant when R32, which is a single refrigerant, or R410A, which is a pseudo-azeotropic mixed refrigerant, is used as the refrigerant that circulates in the refrigeration cycle device. It is also a figure which also shows the curve which shows the relationship between the position and the temperature of air.
  • R407C which is an azeotropic mixed refrigerant
  • a straight line representing the relationship between the position in the flow path passing through the evaporator and the temperature of the refrigerant, and the position and the temperature of the air. It is a figure which also shows the curve which shows the relationship of. It is a graph which shows the temperature gradient of R463A at the pressure in the evaporation process.
  • R463A is used as the refrigerant circulating in the refrigeration cycle device, a curve showing the relationship between the position in the flow path passing through the evaporator and the temperature of the refrigerant, and a curve showing the relationship between the position and the temperature of the air are shown. It is also shown in the figure.
  • FIG. 1 is a functional block diagram showing the configuration of the refrigeration cycle device 100 according to the embodiment.
  • the refrigeration cycle apparatus 100 includes a compressor 1, a condenser 2 (first heat exchanger), an expansion valve 3, an evaporator 4 (second heat exchanger), and a fan 5. , A fan 6 (blower), and a control device 10.
  • the refrigerant circulates in the order of the compressor 1, the condenser 2, the expansion valve 3, and the evaporator 4.
  • Examples of the refrigeration cycle device 100 include a refrigerator, an air conditioner, or a showcase.
  • the evaporator 4 has a port P1 (first port) and a port P2 (second port).
  • the evaporator 4 is formed so that the flow path FP1 (specific flow path) connecting the ports P1 and P2 is meandering.
  • the refrigerant from the expansion valve 3 flows into the evaporator 4 from the port P1, passes through the flow path FP1, and flows out from the port P2.
  • the evaporator 4 may include another flow path other than the flow path FP1.
  • the fan 5 forms an air flow that passes through the condenser 2.
  • the fan 6 forms an airflow Wd1 that passes in the order of ports P2 to P1.
  • the refrigerant passing through the evaporator 4 and the air flow Wd1 form a countercurrent.
  • the airflow Wd1 intersects the flow path FP1 more than once. When the flow path FP1 is linear, the airflow Wd1 is formed from the ports P2 to P1 along the flow path FP1.
  • the control device 10 controls the drive frequency of the compressor 1 to control the amount of refrigerant discharged by the compressor 1 per unit time.
  • the control device 10 controls the drive frequency so that the evaporation temperature is in the range of ⁇ 40 ° C. to 0 ° C., for example.
  • the control device 10 controls the opening degree of the expansion valve 3 so that the degree of superheat of the refrigerant flowing out from the port P2 is within a desired range (for example, 5K to 10K).
  • the control device 10 controls the amount of air blown per unit time of each of the fans 5 and 6.
  • the control device 10 includes a processing circuit.
  • the processing circuit may be dedicated hardware or a CPU (Central Processing Unit) that executes a program stored in the memory.
  • the processing circuit is dedicated hardware, the processing circuit is, for example, a single circuit, a composite circuit, a programmed processor, a parallel programmed processor, an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate). Array), or a combination of these.
  • the processing circuit is a CPU
  • the function of the control device 10 is realized by software, firmware, or a combination of software and firmware.
  • Software or firmware is written as a program and stored in memory. The processing circuit reads and executes the program stored in the memory.
  • the memory includes a non-volatile or volatile semiconductor memory (for example, RAM (Random Access Memory), ROM (Read Only Memory), flash memory, EPROM (Erasable Programmable Read Only Memory), or EPROM (Electrically Erasable Programmable Read Only Memory). ), And magnetic discs, flexible discs, optical discs, compact discs, mini discs, or DVDs (Digital Versatile Disc).
  • the CPU is also called a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, a processor, or a DSP (Digital Signal Processor).
  • FIG. 2 is an external perspective view of the evaporator 4 of FIG.
  • the evaporator 4 includes a plurality of fins 41 and a plurality of heat transfer tubes 42 through which the refrigerant passes.
  • the plurality of fins 41 are juxtaposed at regular intervals.
  • a ventilation path through which the airflow Wd1 passes is formed between the two fins.
  • the plurality of heat transfer tubes 42 penetrate the plurality of fins 41 in the normal direction of the plurality of fins 41.
  • the diameters of the plurality of heat transfer tubes 42 are substantially constant and the lengths of the plurality of flow paths are long in order to make the pressure loss of each of the plurality of flow paths constant. Is preferably substantially constant.
  • FIG. 3 is a curve showing the relationship between the position in the flow path FP1 and the temperature of the refrigerant when R32 which is a single refrigerant or R410A which is a pseudo azeotropic mixed refrigerant is used as the refrigerant circulating in the refrigeration cycle device 100. It is a figure which also shows R11 and the curve A11 which shows the relationship between the position and the air temperature. As shown in FIG. 3, since the temperature of the refrigerant is substantially constant regardless of the position in the flow path FP1, the curve R11 is substantially parallel to the horizontal axis representing the position in the flow path FP1.
  • the curve A11 is expressed as a downwardly convex monotonically increasing curve in which the temperature decreases monotonically as the position of the flow path FP1 approaches P1 to P2.
  • FIG. 4 shows a curve R12 showing the relationship between the position in the flow path FP1 and the temperature of R407 when the azeotropic mixed refrigerant R407C is used as the refrigerant circulating in the refrigeration cycle device 100, and the curve R12 showing the relationship between the position and the air. It is also a figure which also shows the curve A12 which shows the relationship with temperature. As shown in FIG. 4, the temperature of R407C increases linearly as the position in the flow path FP1 approaches from port P1 to P2. The curve A12 is expressed as a downwardly convex monotonous increase curve in which the temperature monotonously increases as the position in the flow path FP1 approaches P1 to P2.
  • the temperature of the air passing through the evaporator 4 drops sharply near the port P2. Since the amount of saturated water vapor in the air decreases as the temperature decreases, most of the moisture in the air can be liquefied as water droplets in the vicinity of the port P2. In this case, since most of the water content in the air is liquefied by the time it passes near the port P1, the amount of water droplets near the port P2 is larger than the amount of water droplets near the port P1. Therefore, when the evaporation temperature becomes equal to or lower than the freezing point (0 ° C.) of water and the water droplets solidify, the amount of frost formed near the port P2 becomes larger than the amount of frost formed near the port P1.
  • the frost formation in the evaporator 4 is biased to the vicinity of the port P2.
  • the ventilation path near the port P2 is blocked by frost, it becomes difficult for the airflow Wd1 to pass through the evaporator 4.
  • the heat exchange efficiency of the evaporator 4 decreases.
  • the temperature gradient (relationship between the dryness of the refrigerant and the temperature of the refrigerant) at the pressure of the refrigerant in the evaporator 4 is the horizontal axis representing the dryness and the said.
  • a refrigerant represented as an upwardly convex monotonous increase curve in a coordinate plane having a vertical axis representing temperature is used in the refrigeration cycle apparatus 100.
  • the refrigerant include R463A, which is a non-azeotropic mixed refrigerant.
  • R463A contains R32, R125, R134a, R1234yf, and carbon dioxide (CO2).
  • the number of types of the refrigerant contained in R463A is 5.
  • the composition ratio (mass ratio) of R32 is 36 wt%.
  • the composition ratio of R125 is 30 wt%.
  • the composition ratio of R134a is 14 wt%.
  • the composition ratio of R1234yf is 14 wt%.
  • the composition ratio of carbon dioxide is 6 wt%.
  • the refrigerant having the lowest boiling point is carbon dioxide.
  • the composition ratio of carbon dioxide in R463A is smaller than 20 wt% (0.2), which is the value obtained by dividing 100 wt% (1) by the number of types of refrigerant contained in R463A.
  • FIG. 5 is a graph showing the temperature gradient of R463A at the pressure in the evaporation process.
  • the pressure is 0.184 MPa.
  • the temperature gradient of R463A is drawn on a coordinate plane having a horizontal axis representing the dryness of R463A and a vertical axis representing the temperature of R463A.
  • the temperature gradient of R463A is represented as a monotonically increasing curve that is convex upward in the coordinate plane.
  • the slope of the temperature gradient of R463A is steep in the range where the dryness is relatively low, and gentle in the range where the dryness is relatively high.
  • FIG. 6 shows a curve R1 showing the relationship between the position in the flow path FP1 and the temperature of R463A when the non-azeotropic mixed refrigerant R463A is used as the refrigerant circulating in the refrigeration cycle apparatus 100, and the curve R1 showing the relationship between the position and the air. It is also a figure which also shows the curve A1 which shows the relationship with temperature.
  • the ports P1 and P2 in the flow path FP1 are the start point and the end point of the evaporation process, respectively, as the position in the flow path FP1 approaches from the port P1 to P2, the R463A flowing through the flow path FP1 The degree of dryness increases.
  • the curve R1 shows the relationship between the dryness of R463A and the temperature in the evaporation process, it is expressed as an upwardly convex monotonic increase curve similar to the curve shown in FIG.
  • the pressure loss caused by the passage of R463A through the evaporator 4 in the evaporation process is so small that the temperature of R463A at port P2 becomes higher than the temperature of R463A at port P1.
  • the curve A1 relating to the air that exchanges heat with R463A in the evaporation process is also expressed as a convex monotonous increase curve in which the temperature increases monotonically as the position in the flow path FP1 approaches P2 from the port P1 corresponding to the curve R1. The curve.
  • the slope of the curve A1 near the port P2 is smaller and gentler than the slope of the curve A11 near the port P2 of FIG. 3 and the slope of the curve A12 near the port P2 of FIG. Since the rapid temperature drop in the vicinity of the port P2 is suppressed, the amount of water droplets in the vicinity of the port P2 is reduced as compared with the cases of FIGS. 3 and 4.
  • the air passing near the port P1 has a larger amount of water remaining than the air passing near the port P1 in FIGS. 3 and 4, so that the amount of water droplets near the port P1 is shown in FIGS. 3 and 4. It increases more than in the case of FIG.
  • the absolute value of the temperature difference is preferably a reference value (for example, 10K) or less.
  • the reference value can be appropriately calculated by an actual machine experiment or a simulation.
  • the air and port P1 at port P2 It is desirable that the absolute value of the temperature difference from the air in the above is equal to or greater than the absolute value of the temperature difference between the non-azeotropic mixed refrigerant at the port P2 and the non-azeotropic mixed refrigerant at the port P1.
  • the non-azeotropic mixed refrigerant expressed as a monotonically increasing curve in which the temperature gradient is convex upward is not limited to R463A.
  • the features common to the non-co-boiling mixed refrigerants are that they contain at least three types of refrigerants having different boiling points from each other, and that the mass of the refrigerant having the lowest boiling point among the refrigerants contained in the non-co-boiling mixed refrigerant is the non-co-boiling. It can be mentioned that the value divided by the mass of the mixed refrigerant is smaller than the value obtained by dividing 1 by the number of types of the refrigerant contained in the non-coboiling mixed refrigerant.
  • the non-azeotropic mixed refrigerant contains carbon dioxide.
  • the boiling point of carbon dioxide (-78.5 ° C.) is often extremely lower than the boiling point of other refrigerants contained in the non-azeotropic mixed refrigerant. Since the non-co-boiling mixed refrigerant, which is expressed as a monotonically increasing curve in which the temperature gradient is convex upward, contains carbon dioxide, the slope of the temperature gradient becomes steep in a range where the dryness is relatively low, and the dryness is relatively high. The characteristic that the slope of the temperature gradient becomes gentle in the range becomes remarkable.
  • the absolute value of the temperature difference between the boiling point (-51.7 ° C.) of R32 (50 wt%) and the boiling point (-48.1 ° C.) of R125 (50 wt%) contained in R410A, which is a pseudo azeotropic mixed refrigerant, is 3. It is .6K. That is, it is treated that the boiling point of R32 and the boiling point of R125 are equal. Therefore, in the present specification, "the boiling points are different" means that the absolute value of the temperature difference between the boiling points of the two refrigerants is larger than 3.6K.
  • the performance of the refrigeration cycle apparatus can be improved.

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

Abstract

L'invention concerne un dispositif à cycle frigorifique (100) dans lequel circule un fluide frigorigène mixte non azéotrope. Le dispositif à cycle frigorifique (100) comprend un compresseur (1), un premier échangeur de chaleur (2), un détendeur (3), un second échangeur de chaleur (4) et une soufflante (6). Le second échangeur de chaleur (4) comporte un premier orifice (P1) et un second orifice (P2). La soufflante (6) forme un écoulement d'air (Wd1) passant à travers le second orifice (P2) et le premier orifice (P1), dans l'ordre. Le fluide frigorigène mixte non azéotrope circule à travers le compresseur (1), le premier échangeur de chaleur (2), le détendeur (3), le premier orifice (P1) et le second orifice (P2), dans l'ordre. À la pression du fluide frigorigène mixte non azéotrope dans le second échangeur de chaleur (4), le gradient de température du fluide frigorigène mixte non azéotrope, c'est-à-dire la relation entre la siccité du fluide frigorigène mixte non azéotrope et la température du fluide frigorigène mixte non azéotrope, s'exprime sous forme de courbe d'augmentation monotone convexe vers le haut dans un plan de coordonnées doté d'un axe horizontal représentant la siccité et d'un axe vertical représentant la température.
PCT/JP2019/035366 2019-09-09 2019-09-09 Dispositif à cycle frigorifique WO2021048897A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2021544986A JP7258163B2 (ja) 2019-09-09 2019-09-09 冷凍サイクル装置
PCT/JP2019/035366 WO2021048897A1 (fr) 2019-09-09 2019-09-09 Dispositif à cycle frigorifique

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2019/035366 WO2021048897A1 (fr) 2019-09-09 2019-09-09 Dispositif à cycle frigorifique

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WO2021048897A1 true WO2021048897A1 (fr) 2021-03-18

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0798166A (ja) * 1993-09-29 1995-04-11 Toshiba Corp 空気調和装置
JPH07324844A (ja) * 1994-05-31 1995-12-12 Sanyo Electric Co Ltd ６方向切替弁及びそれを用いた冷凍装置
JPH0875280A (ja) * 1994-08-31 1996-03-19 Mitsubishi Electric Corp 非共沸混合冷媒を用いた冷凍空調装置
JP2012220042A (ja) * 2011-04-04 2012-11-12 Mitsubishi Electric Corp 空気調和装置
JP2016161256A (ja) * 2015-03-04 2016-09-05 株式会社富士通ゼネラル 空気調和装置
JP2019512031A (ja) * 2016-02-29 2019-05-09 ザ ケマーズ カンパニー エフシー リミテッド ライアビリティ カンパニー ジフルオロメタン、ペンタフルオロエタン、テトラフルオロエタン、テトラフルオロプロペン、及び二酸化炭素を含む冷媒混合物、並びにその使用

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10001308B2 (en) * 2011-12-22 2018-06-19 Mitsubishi Electric Corporation Refrigeration cycle device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0798166A (ja) * 1993-09-29 1995-04-11 Toshiba Corp 空気調和装置
JPH07324844A (ja) * 1994-05-31 1995-12-12 Sanyo Electric Co Ltd ６方向切替弁及びそれを用いた冷凍装置
JPH0875280A (ja) * 1994-08-31 1996-03-19 Mitsubishi Electric Corp 非共沸混合冷媒を用いた冷凍空調装置
JP2012220042A (ja) * 2011-04-04 2012-11-12 Mitsubishi Electric Corp 空気調和装置
JP2016161256A (ja) * 2015-03-04 2016-09-05 株式会社富士通ゼネラル 空気調和装置
JP2019512031A (ja) * 2016-02-29 2019-05-09 ザ ケマーズ カンパニー エフシー リミテッド ライアビリティ カンパニー ジフルオロメタン、ペンタフルオロエタン、テトラフルオロエタン、テトラフルオロプロペン、及び二酸化炭素を含む冷媒混合物、並びにその使用

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JP7258163B2 (ja) 2023-04-14

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