WO2020144764A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2020144764A1
WO2020144764A1 PCT/JP2019/000356 JP2019000356W WO2020144764A1 WO 2020144764 A1 WO2020144764 A1 WO 2020144764A1 JP 2019000356 W JP2019000356 W JP 2019000356W WO 2020144764 A1 WO2020144764 A1 WO 2020144764A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
internal heat
refrigeration cycle
inner pipe
Prior art date
Application number
PCT/JP2019/000356
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
健太 村田
伊東　大輔
拓未 西山
幹 佐藤
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 JP2020565068A priority Critical patent/JP7460550B2/ja
Priority to CN201980079923.1A priority patent/CN113227672A/zh
Priority to PCT/JP2019/000356 priority patent/WO2020144764A1/ja
Priority to EP19908451.8A priority patent/EP3910262A4/de
Publication of WO2020144764A1 publication Critical patent/WO2020144764A1/ja

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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
    • 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
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/06—Superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • F25B2400/05—Compression system with heat exchange between particular parts of the system
    • F25B2400/054—Compression system with heat exchange between particular parts of the system between the suction tube of the compressor and another part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles

Definitions

  • the present invention relates to a refrigeration cycle device.
  • R32 refrigerant and R410A refrigerant have been used as refrigerants for refrigeration cycle devices.
  • a refrigeration cycle device that uses R290 (propane) refrigerant having a smaller global warming potential (GWP) than R32 refrigerant and R410A refrigerant in a refrigerant circuit is known.
  • GWP global warming potential
  • a refrigeration cycle apparatus including an internal heat exchanger for improving cooling capacity is known.
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 2008-164245 (Patent Document 1) describes a refrigeration cycle apparatus that uses propane as a refrigerant in a refrigerant circuit and includes an internal heat exchanger.
  • the refrigeration cycle apparatus described in this publication includes a compressor, a condenser, a heat exchanger, and an evaporator.
  • This heat exchanger corresponds to the internal heat exchanger.
  • This internal heat exchanger has an inner pipe and an outer pipe into which the inner pipe is inserted.
  • the refrigerant sent from the compressor to the internal heat exchanger through the condenser is sent to the evaporator through the inner pipe in the heat exchanger.
  • the refrigerant sent to the evaporator returns to the compressor through the outer pipe in the internal heat exchanger.
  • heat is exchanged between the refrigerant flowing through the inner pipe and the refrigerant flowing through the outer pipe.
  • the present invention has been made in view of the above problems, and an object thereof is to use a refrigerant having a small global warming potential, which can improve the coefficient of performance of a refrigeration cycle device and the amount of refrigerant in an internal heat exchanger. It is to provide a refrigeration cycle device that can reduce
  • the refrigeration cycle device of the present invention includes a refrigerant circuit and a refrigerant.
  • the refrigerant circuit has a compressor, a condenser, an expansion valve, an evaporator and an internal heat exchanger.
  • the refrigerant flows through the refrigerant circuit in the order of the compressor, the condenser, the internal heat exchanger, the expansion valve, the evaporator, and the internal heat exchanger.
  • the refrigerant is a hydrocarbon refrigerant.
  • the internal heat exchanger has an inner pipe connected to the condenser and the expansion valve, and an outer pipe into which the inner pipe is inserted and which is connected to the evaporator and the compressor.
  • the internal heat exchanger is configured to exchange heat between the refrigerant flowing from the condenser to the expansion valve in the inner pipe and the refrigerant flowing from the evaporator to the compressor in the outer pipe to flow outside the inner pipe.
  • the refrigerant flowing outside the inner pipe in the outer pipe is all gas.
  • the refrigerant is a hydrocarbon refrigerant, and the refrigerant flowing outside the inner pipe in the outer pipe of the internal heat exchanger is all gas. Therefore, a refrigerant having a small global warming potential can be used. In addition, the coefficient of performance of the refrigeration cycle apparatus can be improved. Furthermore, the amount of refrigerant in the internal heat exchanger can be reduced.
  • FIG. 3 is a sectional view taken along line III-III in FIG. 2.
  • 6 is a graph showing the relationship between the intake SH of R290 refrigerant and R32 refrigerant and the theoretical COP.
  • 5 is a cross-sectional view schematically showing a refrigerant flow state in the internal heat exchanger of Comparative Example 1.
  • FIG. 6 is a cross-sectional view schematically showing a refrigerant flow state in an internal heat exchanger of Comparative Example 2.
  • FIG. 3 is a cross-sectional view schematically showing a refrigerant flow state in the internal heat exchanger of the refrigeration cycle device according to Embodiment 1 of the present invention.
  • FIG. 8 is a partial cross-sectional view taken along the line VIII-VIII of FIG. 7. It is sectional drawing which shows roughly the flow state of the refrigerant
  • FIG. 10 is a partial sectional view taken along line XX of FIG. 9.
  • Embodiment 1 The configuration of the refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention will be described with reference to FIG. 1 is a configuration diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the refrigeration cycle device according to Embodiment 1 of the present invention is, for example, an air conditioner.
  • a refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention includes a refrigerant circuit 2, a control device 3, a condenser fan 10, an evaporator fan 11, and a refrigerant. There is.
  • the refrigerant circuit 2 has a compressor 4, a condenser 5, an expansion valve 6, an evaporator 7 and an internal heat exchanger 8.
  • the compressor 4, the condenser 5, the expansion valve 6, the evaporator 7, and the internal heat exchanger 8 are connected by a pipe 9. In this way, the refrigerant circuit 2 is configured.
  • the refrigerant circuit 2 is configured to be able to circulate the refrigerant.
  • the refrigerant circuit 2 is configured to perform a refrigeration cycle in which the refrigerant circulates in the order of the compressor 4, the condenser 5, the internal heat exchanger 8, the expansion valve 6, the evaporator 7, and the internal heat exchanger 8 in order. Has been done.
  • the refrigerant flows through the refrigerant circuit 2 in the order of the compressor 4, the condenser 5, the internal heat exchanger 8, the expansion valve 6, the evaporator 7, and the internal heat exchanger 8.
  • the coefficient of performance of the refrigerant increases as the suction superheat degree (suction SH) of the compressor 4 increases.
  • the refrigerant is, for example, a hydrocarbon refrigerant (HC refrigerant).
  • the refrigerant is, for example, propane (R290), isobutane (R600a), pentane (R601), butane (R600), ethane (R170), propylene (R1270).
  • the control device 3 is configured to control the refrigerant circuit 2.
  • the control device 3 is configured to perform calculations, instructions and the like to control each means, equipment and the like of the refrigeration cycle device 1.
  • the control device 3 is electrically connected to the compressor 4, the expansion valve 6, the condenser fan 10, the evaporator fan 11, and the like, and is configured to control these operations.
  • the compressor 4 is configured to compress the inhaled gaseous refrigerant and discharge it.
  • the compressor 4 has a variable capacity.
  • the compressor 4 is configured to change its capacity by changing the frequency by changing the frequency based on an instruction from the control device 3.
  • the compressor 4 uses refrigerating machine oil (lubricating oil).
  • the refrigerator oil is, for example, a polyalkylene glycol (PAG) oil having an ether bond, a polyol ester (POE) oil having an ester bond, or the like.
  • the condenser 5 is configured to condense the refrigerant compressed by the compressor 4.
  • the condenser 5 is connected to the compressor 4 and the internal heat exchanger 8.
  • the condenser 5 has a heat transfer tube through which the refrigerant flows.
  • the condenser 5 is, for example, a fin-and-tube heat exchanger having a plurality of fins and a heat transfer tube that is a circular tube or a flat tube that penetrates the plurality of fins.
  • the expansion valve 6 is configured to expand the liquid refrigerant condensed by the condenser 5 to reduce the pressure.
  • the liquid refrigerant condensed by the condenser 5 is expanded and decompressed by the expansion valve 6, so that the refrigerant at the outlet of the expansion valve 6 becomes a gas-liquid two-phase state.
  • the expansion valve 6 is connected to the condenser 5 and the evaporator 7.
  • the expansion valve 6 is, for example, an electric expansion valve capable of adjusting the flow rate of the refrigerant based on an instruction from the control device 3.
  • the amount of refrigerant passing through the expansion valve 6 is adjusted by adjusting the opening degree of the expansion valve 6.
  • the evaporator 7 is configured to evaporate the refrigerant decompressed by the expansion valve 6.
  • the evaporator 7 is connected to the expansion valve 6 and the internal heat exchanger 8.
  • the evaporator 7 has a heat transfer tube through which the refrigerant flows.
  • the evaporator 7 is, for example, a fin-and-tube heat exchanger having a plurality of fins and a heat transfer tube that is a circular tube or a flat tube that penetrates the plurality of fins.
  • the internal heat exchanger 8 is configured to exchange heat between the refrigerant on the outlet side of the condenser 5 and the refrigerant on the outlet side of the evaporator 7. In the internal heat exchanger 8, heat exchange is performed between the refrigerant condensed in the condenser 5 and the refrigerant evaporated in the evaporator 7.
  • the pipe 9 connects the compressor 4, the condenser 5, the expansion valve 6, the evaporator 7 and the internal heat exchanger 8.
  • the pipe 9 constitutes a gas side refrigerant passage and a liquid side refrigerant passage.
  • the pipe 9 includes a first pipe portion 9a, a second pipe portion 9b, a third pipe portion 9c, and a fourth pipe portion 9d.
  • the first piping section 9a is connected to the condenser 5 and the internal heat exchanger 8.
  • the second piping portion 9b is connected to the internal heat exchanger 8 and the expansion valve 6.
  • the third pipe portion 9c is connected to the evaporator 7 and the internal heat exchanger 8.
  • the fourth pipe portion 9d is connected to the internal heat exchanger 8 and the compressor 4.
  • the condenser fan 10 In cooling, the condenser fan 10 is provided in an outdoor unit (not shown).
  • the condenser fan 10 is configured to forcibly send outdoor air to the condenser 5.
  • the condenser fan 10 is attached to the condenser 5 and is configured to supply air as a heat exchange fluid to the condenser 5.
  • the condenser fan 10 adjusts the amount of air flowing around the condenser 5 by adjusting the number of revolutions of the condenser fan 10 based on an instruction from the control device 3 to adjust the amount of air flowing between the air and the refrigerant. It is configured to adjust the amount of heat exchange.
  • the evaporator fan 11 is provided in an indoor unit (not shown).
  • the evaporator fan 11 is configured to forcibly send indoor air to the evaporator 7.
  • the evaporator fan 11 is attached to the evaporator 7, and is configured to supply air as a heat exchange fluid to the evaporator 7.
  • the evaporator fan 11 adjusts the amount of air flowing around the evaporator 7 by adjusting the number of rotations of the evaporator fan 11 based on an instruction from the control device 3, so that the air between the air and the refrigerant is adjusted. It is configured to adjust the amount of heat exchange.
  • the internal heat exchanger 8 is a double-tube heat exchanger.
  • the internal heat exchanger 8 has an inner pipe 8a and an outer pipe 8b.
  • the inner pipe 8a has a tubular shape.
  • the outer tube 8b has a tubular shape.
  • the inner pipe 8a is inserted into the outer pipe 8b. That is, the inner pipe 8a is arranged inside the outer pipe 8b.
  • a gap GP is provided between the outer peripheral surface of the inner pipe 8a and the inner peripheral surface of the outer pipe 8b. This gap GP may have a uniform dimension over the entire circumference in the outer peripheral direction of the inner pipe 8a.
  • the inner pipe 8a is connected to the condenser 5 and the expansion valve 6.
  • the inner pipe 8a is connected to the condenser 5 via the first pipe portion 9a, and is connected to the expansion valve 6 via the second pipe portion 9b.
  • the inner pipe 8a is configured so that the high-pressure side refrigerant flows.
  • the outer pipe 8b is connected to the evaporator 7 and the compressor 4.
  • the outer pipe 8b is connected to the evaporator 7 via a third pipe portion 9c, and is connected to the compressor 4 via a fourth pipe portion 9d.
  • the outer pipe 8b is configured so that the low-pressure side refrigerant flows.
  • the internal heat exchanger 8 supplies the refrigerant flowing from the condenser 5 to the expansion valve 6 in the inner pipe 8a and the refrigerant flowing from the evaporator 7 to the compressor 4 in the outer pipe 8b to the outside of the inner pipe 8a. It is configured to exchange heat.
  • the internal heat exchanger 8 is configured to exchange heat between the refrigerant flowing through the inner pipe 8a and the refrigerant flowing outside the inner pipe 8a inside the outer pipe 8b via the wall surface of the inner pipe 8a.
  • the internal heat exchanger 8 is configured to exchange heat between the refrigerant flowing through the inner pipe 8a and the refrigerant flowing through the gap GP via the wall surface of the inner pipe 8a.
  • the refrigerant flowing outside the inner pipe 8a inside the outer pipe 8b is all gas.
  • the refrigerant flowing through the gap GP is all gas. All the refrigerant flowing outside the inner pipe 8a in the outer pipe 8b is in a dry state.
  • the gaseous refrigerant compressed by the compressor 4 is discharged from the compressor 4 and sent to the condenser 5 through the pipe 9 serving as the gas side refrigerant passage.
  • the refrigerant is condensed by releasing heat from the refrigerant flowing through the heat transfer tube to the air.
  • the refrigerant is sent to the internal heat exchanger 8 through the first piping portion 9a serving as the liquid side refrigerant passage.
  • the refrigerant sent to the internal heat exchanger 8 through the first pipe portion 9a flows through the inner pipe 8a of the internal heat exchanger 8 and then sent to the expansion valve 6 through the second pipe portion 9b.
  • the liquid refrigerant is decompressed to become a gas-liquid two-phase refrigerant.
  • the refrigerant decompressed by the expansion valve 6 is sent to the evaporator 7 through the pipe 9 serving as the liquid side refrigerant passage. After that, the refrigerant takes in heat from the air in the evaporator 7 and evaporates, and then is sent to the internal heat exchanger 8 through the third pipe portion 9c serving as the gas side refrigerant passage.
  • the refrigerant sent to the internal heat exchanger 8 through the third pipe portion 9c flows through the outer pipe 8b of the internal heat exchanger 8 and then returns to the compressor 4 through the fourth pipe portion 9d.
  • the internal heat exchanger 8 heat is exchanged between the refrigerant on the outlet side of the condenser 5 (high-pressure side refrigerant) flowing through the inner tube 8a and the refrigerant on the outlet side of the evaporator 7 flowing through the outer tube 8b (low-pressure side refrigerant). Exchange will take place. Since the internal heat exchanger 8 can reduce the dryness of the refrigerant at the outlet of the evaporator 7, the heat transfer performance of the evaporator 7 is improved. This improves the coefficient of performance (COP) of the refrigeration cycle apparatus 1.
  • COP coefficient of performance
  • R290 refrigerant is used as an example of the refrigerant in the refrigeration cycle apparatus 1 according to the first embodiment of the present invention.
  • Comparative Example 1 is different from the refrigeration cycle apparatus 1 according to Embodiment 1 of the present invention in that the refrigerant is R32.
  • the R32 refrigerant has a larger global warming potential (GWP) than the R290 refrigerant.
  • Comparative Example 1 is different from the refrigeration cycle apparatus according to Embodiment 1 of the present invention in that in the internal heat exchanger 8, the low pressure side refrigerant flows in the inner pipe 8a and the high pressure side refrigerant flows in the outer pipe 8b. ing. That is, in Comparative Example 1, in the internal heat exchanger 8, the inner pipe 8a is connected to the evaporator 7 and the compressor 4, and the outer pipe 8b is connected to the condenser 5 and the expansion valve 6.
  • FIG. 4 shows a theoretical coefficient of performance (hereinafter, referred to as “theoretical COP”) when R290 refrigerant and R32 refrigerant are used as the refrigerant of the refrigerant circuit 2, and the suction superheat degree (intake SH) of the compressor 4. It is a graph which shows the relationship with.
  • the coefficient of performance (COP) is the ratio of power consumption to the capacity of the refrigeration cycle apparatus 1.
  • the theoretical COP of the R32 refrigerant decreases as the suction superheat degree (suction SH) of the compressor 4 increases.
  • the theoretical COP of the R290 refrigerant improves as the suction superheat (SH) of the compressor 4 increases. This is because the R290 refrigerant and the R32 refrigerant have different characteristics. That is, the coefficient of performance of the R290 refrigerant is more significant when the suction superheat degree (suction SH) of the compressor 4 is increased as compared with the R32 refrigerant.
  • the refrigerant on the low pressure side is made wet in the internal heat exchanger 8 so that the suction superheat degree (suction SH) of the compressor 4 does not become larger than zero (0).
  • FIG. 5 is a cross-sectional view showing the flow state of the refrigerant inside the internal heat exchanger 8 in Comparative Example 1.
  • refrigerant R1 flowing through inner pipe 8a is a low pressure side refrigerant
  • refrigerant R2 flowing through outer pipe 8b is a high pressure side refrigerant.
  • the low-pressure side refrigerant R1 flowing through the inner pipe 8a is in a gas-liquid two-phase state.
  • the low-pressure-side refrigerant R1 flowing through the inner pipe 8a becomes an annular flow.
  • the gas refrigerant Ra flows in the central portion of the inner pipe 8a and the liquid refrigerant Rb flows in the outer portion along the wall surface of the inner pipe 8a. Since the liquid refrigerant Rb comes into contact with the wall surface of the inner pipe 8a serving as the heat transfer surface, the heat transfer performance is improved.
  • the refrigerant of Comparative Example 1 is the R32 refrigerant, the global warming potential is larger than that of the R290 refrigerant. Therefore, in Comparative Example 1, the global warming potential of the refrigerant cannot be reduced.
  • FIG. 6 is a cross-sectional view showing a flow state of the refrigerant inside the internal heat exchanger 8 in Comparative Example 2.
  • the refrigerant R1 flowing through the inner pipe 8a is a low-pressure side refrigerant
  • the refrigerant R2 flowing through the outer pipe 8b is a high-pressure side refrigerant. It is different from the refrigeration cycle apparatus 1 according to Embodiment 1 of the invention.
  • the refrigerant of Comparative Example 2 is propane (R290).
  • the superheat degree of the refrigerant at the outlet of the evaporator 7 becomes close to zero.
  • the superheat degree at the outlet of the internal heat exchanger 8 on the low pressure side, that is, at the inlet of the compressor 4 is zero or more.
  • the refrigerant at the low-pressure side inlet of the internal heat exchanger 8 becomes a gas.
  • the refrigerating machine oil 20 is likely to deposit on the inner surface of the wall surface of the inner pipe 8a.
  • the refrigerating machine oil 20 When the refrigerating machine oil 20 is deposited on the wall surface of the inner pipe 8a of the internal heat exchanger 8, the refrigerating machine oil 20 deposited on the wall surface of the inner tube 8a of the internal heat exchanger 8 becomes a thermal resistance, so that the transfer of the internal heat exchanger 8 is prevented. Thermal performance decreases.
  • FIG. 7 and FIG. 8 are sectional views showing the flow state of the refrigerant inside the internal heat exchanger 8 of the refrigeration cycle device 1 according to Embodiment 1 of the present invention.
  • refrigerant R1 flowing through inner pipe 8a is a high-pressure-side refrigerant and outer pipe 8b is The flowing refrigerant R2 is a low pressure side refrigerant.
  • the heat transfer surface for heat exchange between the high pressure side refrigerant R1 flowing through the inner pipe 8a and the low pressure side refrigerant R2 flowing through the outer pipe 8b becomes the wall surface of the inner pipe 8a.
  • the low-pressure side refrigerant flowing through the outer pipe 8b has heat transfer with the air outside the outer pipe 8b.
  • the area of the wall surface on which the refrigerating machine oil 20 is deposited is increased as compared with Comparative Example 2. Therefore, the amount of refrigerating machine oil deposited on the wall surface of the inner pipe 8a serving as the heat transfer surface is reduced. Therefore, it is possible to prevent the heat transfer performance of the internal heat exchanger 8 from being lowered due to the heat resistance of the refrigerating machine oil deposited on the wall surface of the inner pipe 8a.
  • a propane (R290) refrigerant is used, the high-pressure side refrigerant is caused to flow through the inner pipe 8a of the internal heat exchanger 8, and the low pressure is caused at the outer pipe 8b. Side refrigerant is flowed. Further, the refrigerant at the low-pressure side inlet of the internal heat exchanger 8 becomes dry. That is, the degree of superheat of the refrigerant at the low pressure side inlet of the internal heat exchanger 8 becomes zero. As a result, in the internal heat exchanger 8, deterioration of heat transfer performance due to precipitation of refrigerating machine oil is suppressed. Therefore, the refrigeration cycle apparatus 1 can be operated with a good coefficient of performance.
  • the refrigerant is a hydrocarbon refrigerant (HC refrigerant)
  • a refrigerant having a low global warming potential (GWP) can be used.
  • GWP global warming potential
  • all the refrigerant flowing outside the inner pipe 8a is a gas. Therefore, the degree of superheat of the refrigerant at the inlet of the compressor 4 can be increased as compared with the case where the refrigerant flowing outside the inner pipe 8a inside the outer pipe 8b of the internal heat exchanger 8 contains the liquid refrigerant. Therefore, the coefficient of performance (COP) of the refrigeration cycle apparatus 1 can be improved.
  • COP coefficient of performance
  • the degree of superheat of the refrigerant at the outlet of the outer pipe 8b of the internal heat exchanger 8 is increased as compared with the case where the refrigerant flowing outside the inner pipe 8a inside the outer pipe 8b of the internal heat exchanger 8 contains a liquid refrigerant. can do. Therefore, the amount of refrigerant in the internal heat exchanger 8 can be reduced.
  • the refrigerant is the HC refrigerant. Therefore, the global warming potential (GWP) of the refrigerant can be reduced.
  • GWP global warming potential
  • the expansion valve 6 is an electric expansion valve capable of adjusting the flow rate of the refrigerant. Therefore, the flow rate of the refrigerant can be adjusted by the electric expansion valve.
  • Embodiment 2 The refrigeration cycle device 1 according to the second embodiment of the present invention has the same configuration, operation, and effect as the refrigeration cycle device 1 according to the first embodiment of the present invention described above, unless otherwise specified.
  • refrigeration cycle apparatus 1 according to Embodiment 2 of the present invention has a configuration of outer pipe 8b of internal heat exchanger 8 according to Embodiment 1 of the present invention. Is different from
  • the groove 30 is provided on the inner surface of the outer pipe 8b of the inner heat exchanger 8.
  • the groove 30 may be provided over the entire circumference of the inner surface of the outer pipe 8b of the inner heat exchanger 8.
  • the groove 30 may be configured in a sawtooth shape.
  • the groove 30 is not provided in the inner pipe 8a of the internal heat exchanger 8. That is, no groove is provided on the inner surface and outer surface of the inner pipe 8a of the internal heat exchanger 8.
  • the groove 30 is provided only in the outer pipe 8b of the internal heat exchanger 8, the portion of the internal heat exchanger 8 that does not contribute to heat transfer between the refrigerant flowing in the inner pipe 8a and the refrigerant flowing in the outer pipe 8b.
  • Refrigerating machine oil 20 easily deposits in a certain groove 30. As a result, deterioration of heat transfer performance due to refrigerating machine oil deposited on the wall surface of the inner pipe 8a can be suppressed more than in the first embodiment.
  • the groove 30 is provided on the inner surface of the outer pipe 8b of the inner heat exchanger 8. Since the groove 30 increases the heat transfer area of the outer pipe 8b, the refrigerating machine oil 20 is easily deposited in the groove 30. For this reason, it is possible to suppress a decrease in heat transfer performance due to refrigerating machine oil deposited on the wall surface of the inner pipe 8a.
  • the groove 30 has a sawtooth shape. Therefore, refrigerating machine oil is likely to be deposited on the sawtooth bottom.
  • 1 refrigeration cycle device 1 refrigeration cycle device, 2 refrigerant circuit, 3 control device, 4 compressor, 5 condenser, 6 expansion valve, 7 evaporator, 8 internal heat exchanger, 8a inner pipe, 8b outer pipe, 9 pipe, 10 condenser fan , 11 evaporator fans, 20 refrigerator oil, 30 grooves.

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PCT/JP2019/000356 2019-01-09 2019-01-09 冷凍サイクル装置 WO2020144764A1 (ja)

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PCT/JP2019/000356 WO2020144764A1 (ja) 2019-01-09 2019-01-09 冷凍サイクル装置
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023139758A1 (ja) * 2022-01-21 2023-07-27 三菱電機株式会社 空気調和装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000179959A (ja) * 1998-12-09 2000-06-30 Denso Corp 減圧器一体型熱交換器
JP2003314927A (ja) * 2002-04-18 2003-11-06 Matsushita Electric Ind Co Ltd 熱交換器およびその熱交換器を用いた冷凍サイクル装置
JP2004012127A (ja) * 2003-10-02 2004-01-15 Mitsubishi Electric Corp 可燃性冷媒を用いた冷蔵庫
KR200420568Y1 (ko) * 2006-04-20 2006-07-04 주식회사 두원공조 내부열교환기의 저압측 출구 구조
JP2008164245A (ja) 2006-12-28 2008-07-17 Kobelco & Materials Copper Tube Inc 熱交換器
JP2010127498A (ja) * 2008-11-26 2010-06-10 Nippon Soken Inc 冷凍サイクル装置
JP2014178110A (ja) * 2014-05-28 2014-09-25 Mitsubishi Electric Corp 冷凍空調装置

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19944951B4 (de) * 1999-09-20 2010-06-10 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
JP2001280864A (ja) 2000-03-30 2001-10-10 Hitachi Ltd 熱交換器およびその製造方法
JP2005009833A (ja) * 2003-06-20 2005-01-13 Hitachi Cable Ltd 二重管式熱交換器
JP4884365B2 (ja) 2007-12-28 2012-02-29 三菱電機株式会社 冷凍空調装置、冷凍空調装置の室外機および冷凍空調装置の制御装置
CN101363697A (zh) * 2008-09-28 2009-02-11 湖南晟通科技集团有限公司 一种具有微细通道结构的高效换热管
JP2010261680A (ja) * 2009-05-11 2010-11-18 Sanden Corp 二重管式熱交換器
JP5504050B2 (ja) * 2009-06-30 2014-05-28 株式会社ケーヒン・サーマル・テクノロジー 二重管式熱交換器およびその製造方法
JP5333041B2 (ja) * 2009-08-21 2013-11-06 ダイキン工業株式会社 熱交換器及びそれを備えた冷凍装置
DE102013201313A1 (de) * 2012-02-23 2013-08-29 Ford Global Technologies, Llc Wärmetauscher für eine Klimaanlage
JP2014105890A (ja) * 2012-11-26 2014-06-09 Panasonic Corp 冷凍サイクル装置及びそれを備えた温水生成装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000179959A (ja) * 1998-12-09 2000-06-30 Denso Corp 減圧器一体型熱交換器
JP2003314927A (ja) * 2002-04-18 2003-11-06 Matsushita Electric Ind Co Ltd 熱交換器およびその熱交換器を用いた冷凍サイクル装置
JP2004012127A (ja) * 2003-10-02 2004-01-15 Mitsubishi Electric Corp 可燃性冷媒を用いた冷蔵庫
KR200420568Y1 (ko) * 2006-04-20 2006-07-04 주식회사 두원공조 내부열교환기의 저압측 출구 구조
JP2008164245A (ja) 2006-12-28 2008-07-17 Kobelco & Materials Copper Tube Inc 熱交換器
JP2010127498A (ja) * 2008-11-26 2010-06-10 Nippon Soken Inc 冷凍サイクル装置
JP2014178110A (ja) * 2014-05-28 2014-09-25 Mitsubishi Electric Corp 冷凍空調装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP3910262A4

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023139758A1 (ja) * 2022-01-21 2023-07-27 三菱電機株式会社 空気調和装置

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JP7460550B2 (ja) 2024-04-02
JPWO2020144764A1 (ja) 2021-09-30

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