WO2015093183A1 - Climatiseur - Google Patents

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Publication number
WO2015093183A1
WO2015093183A1 PCT/JP2014/079664 JP2014079664W WO2015093183A1 WO 2015093183 A1 WO2015093183 A1 WO 2015093183A1 JP 2014079664 W JP2014079664 W JP 2014079664W WO 2015093183 A1 WO2015093183 A1 WO 2015093183A1
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WIPO (PCT)
Prior art keywords
refrigerant mixture
air conditioner
compressor
heat exchanger
refrigerant
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PCT/JP2014/079664
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English (en)
Japanese (ja)
Inventor
亮 太田
荒木　邦成
井関　崇
美早 廣瀬
野中　正之
Original Assignee
日立アプライアンス株式会社
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Publication of WO2015093183A1 publication Critical patent/WO2015093183A1/fr

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    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K5/00—Heat-transfer, heat-exchange or heat-storage materials, e.g. refrigerants; Materials for the production of heat or cold by chemical reactions other than by combustion
    • C09K5/02—Materials undergoing a change of physical state when used
    • C09K5/04—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa
    • C09K5/041—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems
    • C09K5/044—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds
    • C09K5/045—Materials undergoing a change of physical state when used the change of state being from liquid to vapour or vice versa for compression-type refrigeration systems comprising halogenated compounds containing only fluorine as halogen
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • 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
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/10—Components
    • C09K2205/12—Hydrocarbons
    • C09K2205/122—Halogenated hydrocarbons
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/10—Components
    • C09K2205/12—Hydrocarbons
    • C09K2205/126—Unsaturated fluorinated hydrocarbons
    • C—CHEMISTRY; METALLURGY
    • C09—DYES; PAINTS; POLISHES; NATURAL RESINS; ADHESIVES; COMPOSITIONS NOT OTHERWISE PROVIDED FOR; APPLICATIONS OF MATERIALS NOT OTHERWISE PROVIDED FOR
    • C09K—MATERIALS FOR MISCELLANEOUS APPLICATIONS, NOT PROVIDED FOR ELSEWHERE
    • C09K2205/00—Aspects relating to compounds used in compression type refrigeration systems
    • C09K2205/34—The mixture being non-azeotropic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units

Definitions

  • the present invention relates to an air conditioner, and more particularly to an air conditioner using a refrigerant having a low global warming potential and utilizing a heat pump cycle.
  • R410A refrigerant (also referred to as HFC410A refrigerant) is a pseudo-azeotropic refrigerant mixture (HFC32 / HFC125 is a 50/50 mass% mixed refrigerant, HFC32: difluoromethane) HFC125: pentafluoroethane).
  • the R410A refrigerant had a higher pressure than the conventionally used R22 refrigerant (chlorodifluoromethane), so it was necessary to review the pressure resistance design of the air conditioner, but it also had the advantage of low pressure loss.
  • the R410A refrigerant has a high global warming potential (GWP) of about 2100, it is required to reduce the amount used and discharged from the viewpoint of preventing global warming, and further studies on alternative refrigerants have been conducted. ing.
  • GWP global warming potential
  • Alternative refrigerants with low ODP and GWP include, for example, HFC32 single refrigerant in hydrofluorocarbons, HFO1234yf (2,3,3,3-tetrafluoropropene) and HFO1234ze (1,3,3, Candidates include single and mixed refrigerants of 3-tetrafluoropropene), propane and propylene in hydrocarbons, and carbon dioxide and ammonia in natural refrigerants.
  • these alternative refrigerants also have advantages and disadvantages.
  • HFO1234yf and HFO1234ze are very low as “GWP ⁇ 10”, but have weakness in chemical stability and slightly flammability.
  • Propane and propylene have a very low refrigeration capacity of “GWP ⁇ 20” and excellent refrigeration capacity.
  • Carbon dioxide gas is non-flammable and generally does not cause toxicity, and has been put to practical use as a refrigerant for water heaters.
  • Patent Document 1 Japanese Patent Laid-Open No. 2013-120029 encloses a mixed refrigerant mainly composed of R32 and HFO1234yf or HFO1234ze and having a R32 concentration of 70% or less, and the refrigerant is a compressor, An air conditioner configured to circulate in a refrigeration cycle configured by connecting a condenser, a decompressor, and an evaporator, and the refrigeration cycle is configured to condense refrigerant at an ambient temperature exceeding 50 ° C. It is disclosed. According to Patent Document 1, even when the ambient temperature is 50 ° C. or higher, the discharge temperature of the compressor is equivalent to that of the currently used R410A, and the reliability of the refrigeration cycle can be improved. It is said that the warming effect can be reduced even if the refrigerant leaks into the atmosphere.
  • Patent Document 2 Japanese Translation of PCT International Publication No. 2010-531970 discloses a method of charging another refrigerant into a type of cooling device system that includes a refrigerant with a high global warming potential and a lubricant, and the lubrication is performed in the system. All or a portion of the high global warming potential refrigerant in the cooling system may be replaced with 1-chloro-3,3,3-trifluoropropene and / or 2-chloro-, while leaving a substantial portion of the agent. Disclosed is a method comprising replacing a halogenated olefin composition comprising 3,3,3-trifluoropropene.
  • the vapor pressure difference between the refrigerants constituting the mixed refrigerant is likely to be large (the non-azeotropic degree is likely to be large), and the temperature gradient indicating the difference between the boiling point and the dew point As a result, the heat exchange efficiency is lowered, and as a result, the energy efficiency (that is, the refrigeration performance) of the entire air conditioner is lowered.
  • an object of the present invention is to provide an air conditioner that uses a non-azeotropic refrigerant mixture that has a low environmental load and is highly safe and does not degrade the refrigeration performance.
  • One aspect of the present invention is an air conditioner using a non-azeotropic refrigerant mixture to achieve the above object,
  • a hermetic electric compressor that is lubricated with compressor oil having a predetermined kinematic viscosity and compresses the non-azeotropic refrigerant mixture, and a heat transfer tube that radiates the non-azeotropic refrigerant mixture discharged from the hermetic electric compressor.
  • the air conditioner constitutes a heat pump cycle in which the non-azeotropic refrigerant mixture discharged from the second heat exchanger is returned to the hermetic electric compressor,
  • the non-azeotropic refrigerant mixture includes difluoromethane, tetrafluoropropene, and monochlorotrifluoropropene, has a global warming potential of 350 or less and exhibits nonflammability,
  • the heat transfer tube is an inner surface grooved tube having a spiral inner surface groove, and the fin constituting the inner surface groove is a sawtooth fin.
  • an air conditioner that uses a non-azeotropic refrigerant mixture that has a low environmental load and is highly safe and that does not degrade the refrigeration performance.
  • the present invention can be improved or changed as follows in the air conditioner according to the present invention described above.
  • the non-azeotropic refrigerant mixture includes 10% to 45% by weight of difluoromethane, 40% to 80% by weight of tetrafluoropropene, and 5% to 20% by weight of monochlorotrifluoro. Including propene.
  • the tetrafluoropropene is 2,3,3,3-tetrafluoropropene or 1,3,3,3-tetrafluoropropene, and the monochlorotrifluoropropene is 1-chloro-3,3, 3-trifluoropropene and / or 2-chloro-3,3,3-trifluoropropene.
  • the compressor oil is composed of at least one of paraffin mineral oil, naphthene mineral oil, polyalphaolefin oil, soft alkylbenzene oil, polyol ester oil, and polyvinyl ether oil, and the predetermined kinematic viscosity is 15 at 40 ° C. mm 2 / s or more and 100 mm 2 / s or less.
  • the hermetic electric compressor is a scroll compressor, a rotary compressor, a twin rotary compressor, a two-stage compression rotary compressor, or a swing compressor.
  • FIG. 1 is a system schematic diagram showing a configuration example of an air conditioner according to the present invention.
  • an air conditioner 10 according to the present invention is an air conditioner using a non-azeotropic refrigerant mixture, and is roughly composed of an outdoor unit 1 and an indoor unit 2.
  • the outdoor unit 1 includes a sealed electric compressor 3, a four-way valve 4, an outdoor heat exchanger 5 having a heat transfer tube 6, a blower 7, and an expansion valve 8.
  • the indoor unit 2 includes an indoor heat exchanger 9 having a heat transfer tube 6 and a blower 7. Each component (except for the blower 7) is connected by a pipe through which the non-azeotropic refrigerant mixture flows.
  • the non-azeotropic refrigerant mixture is adiabatically compressed by the hermetic electric compressor 3 (compression stroke).
  • the compressed high-temperature and high-pressure refrigerant gas passes through the four-way valve 4 and is sent to the outdoor heat exchanger 5 having the heat transfer tube 6 and is radiated through the heat transfer tube 6 of the outdoor heat exchanger 5 to be released into the high-pressure refrigerant liquid. (Condensation process).
  • the heat exchanger to which the high-temperature and high-pressure refrigerant gas discharged from the hermetic electric compressor 3 is first sent is referred to as a first heat exchanger (also referred to as a condenser).
  • the high-pressure refrigerant liquid that has passed through the outdoor heat exchanger 5 is expanded by the expansion valve 8 to become a low-temperature low-pressure refrigerant liquid (expansion process).
  • the low-temperature and low-pressure refrigerant liquid is sent to the indoor heat exchanger 9, and is absorbed through the heat transfer pipe 6 of the indoor heat exchanger 9 to become low-pressure refrigerant gas (evaporation process).
  • the heat exchanger to which the low-temperature and low-pressure refrigerant liquid discharged from the expansion valve 8 is first sent is referred to as a second heat exchanger (also referred to as an evaporator).
  • the low-pressure refrigerant gas that has passed through the indoor heat exchanger 9 returns to the hermetic electric compressor 3 through the four-way valve 4.
  • a heat pump cycle is constituted by this series of processes (compression process, condensation process, expansion process, and evaporation process).
  • the indoor heat exchanger 9 is the first heat exchanger and is responsible for heat dissipation from the high-temperature and high-pressure refrigerant gas
  • the outdoor heat exchanger 5 is the second heat exchanger and is supplied to the low-temperature and low-pressure refrigerant liquid. Responsible for heat absorption.
  • Non-azeotropic refrigerant mixture a non-azeotropic refrigerant mixture is used aiming at a refrigerant with low environmental load and high safety.
  • the refrigerant having a small environmental load means a refrigerant exhibiting “ODP ⁇ 1” and “GWP ⁇ 350”.
  • a highly safe refrigerant means a “non-flammable” and “low toxic” refrigerant.
  • low toxicity means a substance that is not clearly recognized as “toxic” at the time of invention.
  • the non-azeotropic refrigerant mixture to be used it is essential to contain difluoromethane, tetrafluoropropene and monochlorotrifluoropropene. Only difluoromethane and tetrafluoropropene are not incombustible at any blending ratio. In addition, with difluoromethane and monochlorotrifluoropropene alone, GWP ⁇ 350 is not achieved unless the monochlorotrifluoropropene is about 55% by weight or more, and thermochemical stability decreases when the monochlorotrifluoropropene compounding ratio increases.
  • the combination of difluoromethane and monochlorotrifluoropropene has a low vapor pressure and insufficient refrigerating capacity.
  • HFC32 difluoromethane
  • tetrafluoropropene preferably contains propene.
  • the non-azeotropic refrigerant mixture of the present invention may contain a stabilizer (for example, alcohols, phenols, catechols, epoxy compounds, diene compounds) within a range that does not adversely affect the vapor pressure characteristics. Good.
  • 2,3,3,3-tetrafluoropropene (HFO1234yf) and / or 1,3,3,3-tetrafluoropropene (HFO1234ze) can be preferably used as tetrafluoropropene.
  • monochlorotrifluoropropene 1-chloro-3,3,3-trifluoropropene and / or 2-chloro-3,3,3-trifluoropropene can be preferably used.
  • a known hermetic electric compressor can be used as the compressor that compresses the non-azeotropic refrigerant mixture.
  • a scroll compressor, a rotary compressor, a twin rotary compressor, a two-stage compression rotary compressor, and a swing A compressor integrated roller and vane
  • a swing A compressor integrated roller and vane
  • FIG. 2 is a schematic cross-sectional view showing a schematic structure of the vertical scroll compressor.
  • the hermetic electric compressor 3 (here, the vertical scroll compressor) includes a fixed scroll member 31 and an orbiting scroll member 34 engaged with the fixed scroll member 31 inside the pressure vessel 30.
  • a support frame 37 that supports the orbiting scroll member 34, a rotating shaft 38 that causes the orbiting scroll member 34 to orbit and an electric motor 39 are accommodated.
  • the fixed scroll member 31 has an end plate 32 and a spiral wrap 33 provided perpendicular to the end plate 32, and the orbiting scroll member 34 also includes a base 35 and a spiral wrap provided perpendicular to the base 35. 36.
  • the spiral wrap 33 of the fixed scroll member 31 and the spiral wrap 36 of the orbiting scroll member 34 have substantially the same shape, and the compression chamber 40 is formed between the spiral wrap 33 and the spiral wrap 36. (Swirl wraps are meshed with each other).
  • the compression chamber 40 revolves toward the center of the scroll member while gradually reducing its volume. Thereby, the gas in the compression chamber 40 is compressed.
  • the compression chamber 40 reaches the center of the scroll member, the compression chamber 40 and the discharge port 41 communicate with each other, and the compressed gas inside the compression chamber 40 is discharged from the discharge pipe 42 to the outside of the hermetic electric compressor 3.
  • an oil reservoir 43 is provided below the electric motor 39, and compressor oil (also referred to as refrigerator oil) is stored.
  • compressor oil also referred to as refrigerator oil
  • the compressor oil in the oil reservoir 43 is pumped up through an oil hole 44 provided in the rotary shaft 38 due to a pressure difference, and supplied to the lubrication of the main bearing 45 and the sub bearing 46.
  • compressor oil In an air conditioner, in general, the combination of compressor oil and refrigerant is very important because it strongly affects the refrigeration performance.
  • a known compressor oil can be used as the compressor oil.
  • a paraffin mineral oil, a naphthene mineral oil, a poly ⁇ -olefin oil, a soft alkylbenzene oil, a polyol ester oil, a polyvinyl ether oil, and a mixed oil thereof are preferably used. be able to.
  • the non-azeotropic refrigerant mixture of the present invention has poor solubility in paraffin mineral oil, naphthene mineral oil, poly-alpha olefin oil, and soft alkylbenzene oil. It was found that it was compatible with polyol ester oil and polyvinyl ether oil.
  • the kinematic viscosity at 40 ° C. is preferably 15 mm 2 / s to 100 mm 2 / s. More specifically, when hardly soluble oil is used in the scroll compressor, the kinematic viscosity at 40 ° C. is preferably 32 mm 2 / s to 74 mm 2 / s. When a compatible oil is used in a scroll compressor, the kinematic viscosity at 40 ° C. is preferably 46 mm 2 / s or more and 100 mm 2 / s or less.
  • the kinematic viscosity at 40 ° C. is preferably 15 mm 2 / s to 56 mm 2 / s.
  • the kinematic viscosity at 40 ° C. is preferably 32 mm 2 / s to 74 mm 2 / s.
  • a lubricity improver for example, 2,6-di-t-butyl-p-cresol: DBPC
  • DBPC 2,6-di-t-butyl-p-cresol
  • an aliphatic epoxy compound or a carbodiimide compound can be suitably used.
  • the non-azeotropic refrigerant mixture of the present invention has an advantage that GWP is small, the non-azeotropic degree of each refrigerant constituting the mixed refrigerant is large (the temperature gradient indicating the difference between the boiling point and the dew point is large). It also has a weak point that it is difficult to condense and evaporate like conventional refrigerants.
  • the present inventors conducted a detailed and systematic investigation and examination of a heat transfer tube that enables efficient condensation and evaporation of the non-azeotropic refrigerant mixture of the present invention.
  • the heat transfer tube used is not a conventional inner surface grooved tube having a simple spiral inner surface groove (simple spiral inner surface grooved tube), but the fin constituting the spiral inner surface groove is a sawtooth fin. It was confirmed that the inner grooved tube (spiral sawtooth inner grooved tube) is preferable.
  • the material of the heat transfer tube there is no particular limitation on the material of the heat transfer tube, and conventional materials (for example, copper, copper alloy, aluminum, etc.) can be suitably used.
  • FIG. 3A is a schematic cross-sectional view showing the flow of the simple spiral inner grooved tube and the refrigerant
  • FIG. 3B is a schematic cross-sectional view showing the flow of the spiral sawtooth inner grooved tube and the refrigerant.
  • a simple spiral inner groove 62 ′ is formed on the inner surface of the tube wall 61 to constitute an inner groove.
  • the fins are fins 63 ′ having a uniform height. Strictly speaking, the condensed refrigerant liquid flow 64 ′ is influenced mainly by the mass flow velocity of the refrigerant, but mainly occurs along the spiral inner groove 62 ′.
  • the heat transfer tube 6 (spiral sawtooth inner surface grooved tube) used in the present invention has a spiral inner surface groove 62 formed on the inner surface of the tube wall 61.
  • the fins are sawtooth fins 63.
  • FIG. 4 is a schematic graph showing the relationship between the condensation heat transfer coefficient and the mass flow rate of the refrigerant.
  • the condensation heat transfer coefficient increased in proportion to the increase in the refrigerant mass flow rate.
  • the spiral sawtooth inner grooved tube showed a clearly higher condensation heat transfer rate in the low and medium speed regions of the refrigerant mass flow rate than the simple spiral inner grooved tube. In the area, the difference between the two has shrunk.
  • the refrigerant mass flow rate is usually in the low to medium speed region, it can be said that it is significant to use a spiral sawtooth inner grooved tube.
  • the reason why the result shown in FIG. 4 is obtained is that the fin 63 'is not equal in height, but is a sawtooth fin 63, so that the turbulent flow of the refrigerant even in the low to medium speed region. This is thought to be because the agitation of the refrigerant is promoted and the concentration of the refrigerant in the refrigerant (temperature gradient in the refrigerant) is reduced. In addition, when the refrigerant mass flow rate is in the high speed region, the flow of the refrigerant becomes turbulent in any of the heat transfer tubes, so it was considered that the difference in the condensation heat transfer coefficient was reduced.
  • mixed refrigerant a non-copolymer consisting of 40% by mass of difluoromethane, 50% by mass of 1,3,3,3-tetrafluoropropene and 10% by mass of 1-chloro-3,3,3-trifluoropropene.
  • a boiling mixed refrigerant (refrigerant 1) was prepared.
  • the refrigerant 1 is “ODP ⁇ 1” and “GWP ⁇ 300”, and can be said to be a refrigerant with a small environmental load.
  • the non-azeotropic degree between the refrigerants constituting the mixed refrigerant is large, and the temperature gradient indicating the difference between the boiling point and the dew point is about 7 ° C. at the maximum.
  • Another example of the mixed refrigerant of the present invention is composed of 30% by mass of difluoromethane, 55% by mass of 2,3,3,3-tetrafluoropropene, and 15% by mass of 1-chloro-3,3,3-trifluoropropene.
  • a non-azeotropic refrigerant mixture (refrigerant 2) was prepared.
  • the refrigerant 2 is “ODP ⁇ 1” and “GWP ⁇ 240”, and can be said to be a refrigerant with a small environmental load.
  • the non-azeotropic degree between the refrigerants constituting the mixed refrigerant is large, and the temperature gradient indicating the difference between the boiling point and the dew point is about 10 ° C. at the maximum.
  • coolants 1 and 2 is a low toxicity substance, the refrigerant
  • R410A refrigerant (a pseudo-azeotropic mixed refrigerant with 50/50 mass% HFC32 / HFC125, refrigerant 3) was prepared.
  • Example 1 Using a home air conditioner (see FIG. 1, output 4.0 kW) equipped with a scroll compressor (see FIG. 2), an endurance test was performed under high speed and high load conditions.
  • Refrigerant 1 was used as a mixed refrigerant, and a refrigerant amount of 1500 g was sealed in an air conditioner.
  • As the compressor oil of the scroll compressor naphthenic mineral oil (kinematic viscosity at 40 ° C. 56 mm 2 / s, oil amount 400 ml) was used.
  • This compressor oil contains 0.5% by weight of an epoxy acid scavenger, 0.25% by weight of 2,6-di-t-butyl-p-cresol (antioxidant), and 10 ppm of silicone oil as additives. (Antifoaming agent) is blended.
  • the electric motor of the scroll compressor uses a polyester-imide / amide-imide double-coated enameled wire as the coil winding, and heat insulation PET film (B type 130 ° C, thickness 250 ⁇ m) between the iron core and coil of the electric motor ) was used.
  • heat transfer tube a spiral sawtooth-shaped inner surface grooved tube (manufactured by Hitachi Cable, Ltd., Thermo Excel-i tube, see FIG. 3B) was used.
  • the rotation speed of the scroll compressor was set to 6000 min ⁇ 1 and continuous operation was performed for 2160 hours.
  • the scroll compressor installed after 2160 hours of operation was dismantled, and the state of wear of components, deterioration of heat-resistant PET film, and deterioration of compressor oil were investigated and measured.
  • the mechanical properties of the heat-resistant PET film before and after the durability test and the amount of oligomer in the film were measured.
  • the initial heat-resistant PET film had a tensile strength of 180 MPa, an elongation of 80%, and an oligomer amount of 0.6% by mass. It was confirmed that the heat-resistant PET film after the durability test had little decrease in tensile strength and elongation, and the amount of oligomer was hardly decreased.
  • the total acid value and residual additive amount of the compressor oil before and after the durability test were measured. The total acid number of the compressor oil was measured using a titration method, and the residual amount of additive was measured using gas chromatography.
  • the total acid value of the compressor oil was 0.01 mgKOH / g before and after the durability test, and there was no substantial change. Further, it was confirmed that the acid scavenger and antioxidant as additives had a residual amount of 50% or more, and there was no particular problem.
  • Example 2 In the same manner as in Example 1, a test was performed using a polyol ester oil (kinematic viscosity at 40 ° C .: 68 mm 2 / s, oil amount: 400 ml) as the compressor oil.
  • This compressor oil contains 0.9% by mass of an epoxy acid scavenger and 0.25% by mass of 2,6-di-t-butyl-p-cresol (antioxidant) as additives. .
  • a dismantling survey was conducted. It was confirmed that there was very little wear on the scroll compressor main bearing, secondary bearing, orbiting scroll tooth tip, and stationary scroll tooth tip.
  • the total acid value of the compressor oil was 0.03 mgKOH / g, which was a low value. It was confirmed that the additive acid scavenger and antioxidant had a residual amount of 50% or more, and there was no particular problem.
  • Example 3 Using a home air conditioner (see Fig. 1, output 2.8 kW) equipped with a scroll compressor (see Fig. 2), a durability test was conducted under high temperature and high load conditions.
  • Refrigerant 2 was used as a mixed refrigerant, and 1350 g of refrigerant was sealed in an air conditioner.
  • Polyol ester oil (kinematic viscosity at 40 ° C. 68 mm 2 / s, oil amount 350 ml) was used as compressor oil for the scroll compressor.
  • 0.9% by mass of an epoxy acid scavenger and 0.25% by mass of 2,6-di-t-butyl-p-cresol (antioxidant) are blended as additives.
  • Example 2 The same electric motor as in Example 1 was used as the electric motor of the scroll compressor. In addition, the same helical sawtooth inner grooved tube as in Example 1 was used as the heat transfer tube.
  • the scroll compressor mounted after 1080 hours was disassembled, and in the same manner as in Example 1, the wear state of the constituent members, the deterioration state of the heat-resistant PET film, and the deterioration state of the compressor oil were investigated.
  • the constituent members for example, the main bearing of the scroll compressor, the auxiliary bearing, the tip of the orbiting scroll, and the tip of the fixed scroll
  • the heat-resistant PET film had no particular deterioration before and after the durability test.
  • the compressor oil it was confirmed that there was no substantial change in the total acid value before and after the durability test, and there was no problem in the remaining amount even with the acid scavenger and the antioxidant.
  • Examples 4 and 5 In order to evaluate the refrigeration performance of the air conditioner according to the present invention, year-round energy consumption efficiency (APF) was measured.
  • the air conditioners of Examples 4 and 5 measured APF using Examples 1 and 2 described above.
  • the air conditioning apparatus of the comparative example 1 corresponded to a prior art and the air conditioning apparatus of the comparative example 2 which deviate
  • the air conditioner of Comparative Example 1 uses refrigerant 3 as a mixed refrigerant, and uses a simple spiral inner grooved tube (manufactured by Hitachi Cable, Ltd., Thermofin-HGL tube, see FIG. 3A) as a heat transfer tube.
  • the home air conditioner was the same as in Example 1.
  • the air conditioner of Comparative Example 2 uses the refrigerant 1 as a mixed refrigerant, and uses a simple spiral inner grooved tube (manufactured by Hitachi Cable, Ltd., Thermofin-HGL tube, see FIG. 3A) as a heat transfer tube.
  • the home air conditioner was the same as in Example 1.
  • APF year-round energy consumption efficiency
  • APF year-round energy consumption efficiency
  • the APF is not lowered, and is reduced to 1/6 or less as compared with the conventional refrigerant mixture (for example, R410A refrigerant).
  • the global warming potential could be reduced, and a safe air conditioner using non-flammable refrigerant was obtained.
  • a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.
  • a part of the configuration of each embodiment can be deleted, replaced with another configuration, or added with another configuration.
  • a means for improving the heat exchange efficiency may be added, or the heat transfer tube specified in the present invention may be replaced with a heat transfer tube that further improves the heat exchange efficiency. Good.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Geometry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Materials Engineering (AREA)
  • Organic Chemistry (AREA)
  • Lubricants (AREA)

Abstract

La présente invention concerne un climatiseur dans lequel est utilisé un mélange réfrigérant zéotropique, comprenant : un compresseur électrique hermétique qui comprime le mélange réfrigérant zéotropique et qui est lubrifié avec une huile de compresseur ayant une viscosité dynamique prédéfinie ; un premier échangeur de chaleur comportant une conduite de transfert de chaleur destinée à amener le mélange réfrigérant zéotropique déchargé du compresseur électrique hermétique à restituer de la chaleur ; un détendeur destiné à détendre le mélange réfrigérant zéotropique déchargé du premier échangeur de chaleur ; un second échangeur de chaleur comportant une conduite de transfert de chaleur destinée à amener le mélange réfrigérant zéotropique déchargé du détendeur à absorber la chaleur ; et une vanne à quatre voies destinée à commander le sens de circulation du mélange réfrigérant zéotropique. Le climatiseur constitue un cycle de pompage de chaleur dans lequel le mélange réfrigérant zéotropique déchargé du second échangeur de chaleur est renvoyé au compresseur électrique hermétique. Le mélange réfrigérant zéotropique contient du difluorométhane, du tétrafluoropropène et du monochlorotrifluoropropène, a un potentiel de réchauffement global inférieur ou égal à 350 et est ininflammable. La conduite de transfert de chaleur est une conduite intérieurement rainurée comportant des rainures hélicoïdales de surface intérieure, et les ailettes constituant les rainures intérieures sont des ailettes en forme de dents de scie.
PCT/JP2014/079664 2013-12-20 2014-11-10 Climatiseur WO2015093183A1 (fr)

Applications Claiming Priority (2)

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JP2013-263615 2013-12-20
JP2013263615A JP2015117923A (ja) 2013-12-20 2013-12-20 空調装置

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CN108700339A (zh) * 2016-02-24 2018-10-23 三菱电机株式会社 制冷装置
FR3070982B1 (fr) * 2017-09-12 2019-08-30 Arkema France Composition a base d'hydrochlorofluoroolefine et d'huile minerale
JP2019135395A (ja) * 2019-05-23 2019-08-15 ダイキン工業株式会社 冷凍機油の排出を抑制できる圧縮機

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JP2012031239A (ja) * 2010-07-29 2012-02-16 Hitachi Appliances Inc 冷凍空調用圧縮機及び冷凍空調装置
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JP2012002453A (ja) * 2010-06-18 2012-01-05 Hitachi Cable Ltd 内面溝付伝熱管、及び熱交換器
JP2013529703A (ja) * 2010-06-22 2013-07-22 アーケマ・インコーポレイテッド ヒドロフルオロカーボンとヒドロフルオロオレフィンの熱伝達組成物
JP2012031239A (ja) * 2010-07-29 2012-02-16 Hitachi Appliances Inc 冷凍空調用圧縮機及び冷凍空調装置

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RU2658414C1 (ru) * 2017-06-20 2018-06-21 Федеральное государственное бюджетное образовательное учреждение высшего образования "Саратовский государственный технический университет имени Гагарина Ю.А." (СГТУ имени Гагарина Ю.А.) Способ получения рабочего агента в компрессионном тепловом насосе

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