WO2017145713A1 - Unité d'échange de chaleur - Google Patents

Unité d'échange de chaleur Download PDF

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Publication number
WO2017145713A1
WO2017145713A1 PCT/JP2017/004064 JP2017004064W WO2017145713A1 WO 2017145713 A1 WO2017145713 A1 WO 2017145713A1 JP 2017004064 W JP2017004064 W JP 2017004064W WO 2017145713 A1 WO2017145713 A1 WO 2017145713A1
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WIPO (PCT)
Prior art keywords
compressor
working medium
heat
hfo
heat exchange
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PCT/JP2017/004064
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English (en)
Japanese (ja)
Inventor
洋輝 速水
正人 福島
高木　洋一
真維 田坂
Original Assignee
旭硝子株式会社
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.)
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Application filed by 旭硝子株式会社 filed Critical 旭硝子株式会社
Priority to EP17756155.2A priority Critical patent/EP3421903A4/fr
Priority to JP2018501112A priority patent/JPWO2017145713A1/ja
Priority to CN201780012665.6A priority patent/CN108700344A/zh
Publication of WO2017145713A1 publication Critical patent/WO2017145713A1/fr
Priority to US16/109,081 priority patent/US20190003469A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/20—Electric components for separate outdoor units
    • F24F1/24—Cooling of electric components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0089—Systems using radiation from walls or panels
    • 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
    • F25B31/006—Cooling of compressor or motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2106—Temperatures of fresh outdoor air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the present invention relates to a heat exchange unit, and more particularly to a heat exchange unit used in a refrigeration cycle apparatus.
  • HFC hydrofluorocarbon
  • refrigerants hydrofluorocarbon refrigerants
  • GWP global warming potential
  • Patent Document 1 describes a refrigeration cycle apparatus using a working medium containing 1,1,2-trifluoroethylene (HFO-1123).
  • a disproportionation reaction when energy is input in a high temperature and high pressure state, a chemical reaction accompanied by heat generation called a disproportionation reaction (self-decomposition reaction) may occur in a chain.
  • a disproportionation reaction is a chemical reaction in which two or more of the same type of molecule react with each other to produce two or more different types of products. For this reason, in the refrigeration cycle apparatus using a working medium containing HFO-1123 as the working medium, it is necessary to suppress the occurrence of such disproportionation reaction.
  • an object of the present invention is to provide a heat exchange unit capable of suppressing the occurrence of disproportionation reaction of HFO-1123.
  • the heat exchange unit includes a compressor that compresses a working medium containing 1,1,2-trifluoroethylene circulating in the refrigeration cycle, and a heat exchanger provided in the refrigeration cycle. And heat radiating means for radiating heat generated in the compressor without using the working medium.
  • a heat exchange unit is the above heat exchange unit, wherein the air blower that increases the airflow flowing on the surface of the heat exchanger and promotes heat exchange in the heat exchanger; And a partition plate that partitions the space in which the compressor is disposed and the space in which the compressor is disposed.
  • the partition plate is formed with a vent at a position corresponding to the compressor of the partition plate, the heat dissipating means is composed of the blower, and the air flow sent from the blower is used for the compressor. Dissipate heat.
  • a heat exchange unit includes a wind direction plate that changes the direction of a part of the airflow sent from the blower to the compressor side in the heat exchange unit described above.
  • the blower in the heat exchange unit described above, includes a wind direction switching unit that switches the wind direction of the blower to the compressor side.
  • the heat exchange unit is the above-described heat exchange unit, wherein the detection unit that detects the temperature of the working medium discharged from the compressor, and the temperature of the working medium is lower than a predetermined temperature.
  • a determination unit that determines whether the value is high, and a first control unit that controls the wind direction switching unit according to a determination result of the determination unit.
  • the first control unit controls the wind direction switching unit so that the wind direction of the blower is on the compressor side.
  • the compressor in the above heat exchange unit, is provided with a heat sink as a heat radiating means for radiating heat generated in the compressor.
  • a heat exchange unit is the above heat exchange unit, wherein as the heat radiating means, drain water generated in the refrigeration cycle is supplied to the surface of the compressor to cool the compressor.
  • a drain water supply unit is further provided.
  • the drain water supply unit is drained from a drain water storage unit that stores drain water generated in the refrigeration cycle, and the compressor.
  • a detecting unit for detecting the temperature of the working medium, a determining unit for determining whether or not the temperature of the working medium is higher than a predetermined temperature, and the drain from the drain water storage unit to the surface of the compressor An electromagnetic valve that switches water supply; and a second control unit that controls the electromagnetic valve according to a determination result of the determination unit.
  • the second control unit opens the electromagnetic valve and supplies the drain water from the drain water storage unit to the surface of the compressor.
  • a heat exchange unit capable of suppressing the occurrence of disproportionation reaction of HFO-1123 can be provided.
  • FIG. 1 is a diagram for explaining a refrigeration cycle apparatus.
  • FIG. 2 is a diagram for explaining the refrigeration cycle apparatus.
  • FIG. 3A is a top view illustrating an example of the heat exchange unit according to the first embodiment.
  • FIG. 3B is a front view of an example of the heat exchange unit according to the first embodiment.
  • FIG. 3C is a side view illustrating an example of the heat exchange unit according to the first embodiment.
  • FIG. 4 is a side view showing another example of the heat exchange unit according to the first embodiment.
  • FIG. 5 is a top view of an example of the heat exchange unit according to the second embodiment.
  • FIG. 6 is a front view of an example of the heat exchange unit according to the third embodiment.
  • FIG. 7A is a top view for explaining the operation of the heat exchange unit according to the third embodiment.
  • FIG. 7B is a top view for explaining the operation of the heat exchange unit according to the third embodiment.
  • FIG. 8 is a top view of an example of the heat exchange unit according to the fourth embodiment.
  • FIG. 9 is a side view illustrating an example of the heat exchange unit according to the fifth embodiment.
  • HFO-1123 The working medium used in the present invention includes 1,1,2-trifluoroethylene (HFO-1123).
  • the characteristics of HFO-1123 as a working medium are shown particularly in Table 1 in a relative comparison with R410A (a pseudo-azeotropic refrigerant mixture having a mass ratio of 1: 1 between HFC-32 and HFC-125).
  • the cycle performance is indicated by a coefficient of performance and a refrigerating capacity obtained by a method described later.
  • the coefficient of performance and the refrigeration capacity of HFO-1123 are expressed as relative values (hereinafter referred to as the relative coefficient of performance and relative refrigeration capacity) with R410A as the reference (1.000).
  • the global warming potential is a value of 100 years indicated in the Intergovernmental Panel on Climate Change (IPCC) Fourth Assessment Report (2007) or measured according to the method. In this specification, GWP refers to this value unless otherwise specified.
  • IPCC Intergovernmental Panel on climate Change
  • the working medium used in the present invention preferably contains HFO-1123, and may optionally contain a compound used as a normal working medium in addition to HFO-1123 as long as the effects of the present invention are not impaired.
  • a compound used as a normal working medium in addition to HFO-1123 examples include HFO other than HFC and HFO-1123 (HFC having a carbon-carbon double bond), other components that vaporize and liquefy together with HFO-1123 other than these, etc. Is mentioned.
  • HFO other than HFC and HFO-1123 HFC having a carbon-carbon double bond
  • the working medium contains such a compound in combination with HFO-1123, a better cycle performance can be obtained while keeping the GWP low, and the influence of the temperature gradient is small.
  • thermo gradient When the working medium contains, for example, HFO-1123 and an optional component, it has a considerable temperature gradient except when the HFO-1123 and the optional component have an azeotropic composition.
  • the temperature gradient of the working medium varies depending on the type of the optional component and the mixing ratio of HFO-1123 and the optional component.
  • azeotropic or pseudo-azeotropic mixture such as R410A is preferably used.
  • Non-azeotropic compositions have the problem of causing composition changes when filled from a pressure vessel to a refrigeration air conditioner. Furthermore, when refrigerant leakage from the refrigeration air conditioner occurs, the refrigerant composition in the refrigeration air conditioner is very likely to change, and it is difficult to restore the refrigerant composition to the initial state. On the other hand, the above problem can be avoided if the mixture is azeotropic or pseudo-azeotropic.
  • Temperature gradient is generally used as an index for measuring the possibility of using the mixture in the working medium.
  • a temperature gradient is defined as the property of the start and end temperatures of a heat exchanger, for example, evaporation in an evaporator or condensation in a condenser, differing. In the azeotrope, the temperature gradient is 0, and in the pseudoazeotrope, the temperature gradient is very close to 0, for example, the temperature gradient of R410A is 0.2.
  • the inlet temperature in the evaporator decreases, which increases the possibility of frost formation, which is a problem.
  • a heat cycle system in order to improve heat exchange efficiency, it is common to make the working medium flowing through the heat exchanger and a heat source fluid such as water or air counter flow, and in a stable operation state Since the temperature difference of the heat source fluid is small, it is difficult to obtain an energy efficient thermal cycle system in the case of a non-azeotropic mixed medium having a large temperature gradient. For this reason, when a mixture is used as a working medium, a working medium having an appropriate temperature gradient is desired.
  • HFC The optional HFC is preferably selected from the above viewpoint.
  • HFC is known to have higher GWP than HFO-1123. Therefore, the HFC combined with HFO-1123 is appropriately selected from the viewpoint of improving the cycle performance as the working medium and keeping the temperature gradient within an appropriate range, and particularly keeping the GWP within an allowable range. It is preferred that
  • an HFC having 1 to 5 carbon atoms is preferable as an HFC that has little influence on the ozone layer and has little influence on global warming.
  • the HFC may be linear, branched, or cyclic.
  • HFC examples include HFC-32, difluoroethane, trifluoroethane, tetrafluoroethane, HFC-125, pentafluoropropane, hexafluoropropane, heptafluoropropane, pentafluorobutane, heptafluorocyclopentane, and the like.
  • HFC 1,1-difluoroethane
  • HFC-152a 1,1,1-trifluoroethane
  • HFC-125 1,1,2,2-tetrafluoroethane
  • HFC-132, HFC -152a, HFC-134a, and HFC-125 are more preferred.
  • One HFC may be used alone, or two or more HFCs may be used in combination.
  • the content of HFC in the working medium (100% by mass) can be arbitrarily selected according to the required characteristics of the working medium.
  • the coefficient of performance and the refrigerating capacity are improved when the content of HFC-32 is in the range of 1 to 99% by mass.
  • the coefficient of performance improves when the content of HFC-134a is in the range of 1 to 99% by mass.
  • the preferred HFC GWP is 675 for HFC-32, 1430 for HFC-134a and 3500 for HFC-125. From the viewpoint of keeping the GWP of the obtained working medium low, the HFC-32 is most preferable as an optional HFC.
  • HFO-1123 and HFC-32 can form a pseudo-azeotropic mixture close to azeotropy in a composition range of 99: 1 to 1:99 by mass ratio. The temperature gradient is close to zero. Also in this respect, HFC-32 is advantageous as an HFC combined with HFO-1123.
  • the content of HFC-32 with respect to 100% by mass of the working medium is specifically preferably 20% by mass or more, and 20 to 80% by mass. % Is more preferable, and 40 to 60% by mass is further preferable.
  • HFOs other than HFO-1123 may be used alone or in combination of two or more.
  • the content of HFO other than HFO-1123 in the working medium (100% by mass) can be arbitrarily selected according to the required characteristics of the working medium.
  • the coefficient of performance improves when the content of HFO-1234yf or HFO-1234ze is in the range of 1 to 99% by mass.
  • composition range (S) A preferred composition range in the case where the working medium used in the present invention contains HFO-1123 and HFO-1234yf is shown below as a composition range (S).
  • the abbreviation of each compound is the ratio (% by mass) of the compound with respect to the total amount of HFO-1123, HFO-1234yf, and other components (HFC-32, etc.). Show.
  • the working medium in the composition range (S) has an extremely low GWP and a small temperature gradient.
  • refrigeration cycle performance that can be substituted for the conventional R410A can be expressed.
  • the ratio of HFO-1123 to the total amount of HFO-1123 and HFO-1234yf is more preferably 40 to 95% by mass, further preferably 50 to 90% by mass, and more preferably 50 to 85%. Mass% is particularly preferable, and 60 to 85 mass% is most preferable.
  • the total content of HFO-1123 and HFO-1234yf in 100% by mass of the working medium is more preferably 80 to 100% by mass, further preferably 90 to 100% by mass, and particularly preferably 95 to 100% by mass. .
  • the working medium used in the present invention preferably contains HFO-1123, HFC-32, and HFO-1234yf, and a preferred composition range (P) in the case of containing HFO-1123, HFO-1234yf, and HFC-32.
  • P a preferred composition range
  • the abbreviation of each compound indicates the ratio (mass%) of the compound with respect to the total amount of HFO-1123, HFO-1234yf, and HFC-32.
  • R composition range
  • L composition range
  • M composition range
  • the total amount of HFO-1123, HFO-1234yf, and HFC-32 specifically described is more than 90% by mass and less than 100% by mass with respect to the total amount of the working medium for heat cycle. It is preferable that
  • the working medium having the above composition is a working medium in which the characteristics of HFO-1123, HFO-1234yf, and HFC-32 are exhibited in a well-balanced manner, and the defects possessed by each are suppressed.
  • this working medium is a working medium that has a very low GWP, has a small temperature gradient, and has a certain capacity and efficiency when used in a thermal cycle, and can obtain good cycle performance.
  • the total amount of HFO-1123 and HFO-1234yf with respect to the total amount of HFO-1123, HFO-1234yf, and HFC-32 is preferably 70% by mass or more.
  • the working medium used in the present invention is more preferably composed of 30 to 70% by mass of HFO-1123 and 4 to 4% of HFO-1234yf with respect to the total amount of HFO-1123, HFO-1234yf, and HFC-32.
  • Examples include a composition containing 40% by mass and HFC-32 in a proportion of 0 to 30% by mass, and the content of HFO-1123 with respect to the total amount of the working medium is 70 mol% or less.
  • the working medium in the above range is a highly durable working medium in which the above effect is enhanced and the self-decomposition reaction of HFO-1123 is suppressed.
  • the content of HFC-32 is preferably 5% by mass or more, and more preferably 8% by mass or more.
  • composition range (R) is shown below. ⁇ Composition range (R)> 10% by mass ⁇ HFO-1123 ⁇ 70% by mass 0% by mass ⁇ HFO-1234yf ⁇ 50% by mass 30% by mass ⁇ HFC-32 ⁇ 75% by mass
  • the working medium having the above composition is a working medium in which the characteristics of HFO-1123, HFO-1234yf, and HFC-32 are exhibited in a well-balanced manner, and the defects possessed by each are suppressed. That is, it is a working medium in which good cycle performance can be obtained by having a low temperature gradient and high performance and efficiency when used in a thermal cycle after GWP is kept low and durability is ensured.
  • composition range (R) preferred ranges are shown below. 20% by mass ⁇ HFO-1123 ⁇ 70% by mass 0% by mass ⁇ HFO-1234yf ⁇ 40% by mass 30% by mass ⁇ HFC-32 ⁇ 75% by mass
  • the working medium having the above composition is a working medium in which the characteristics of HFO-1123, HFO-1234yf, and HFC-32 are exhibited in a particularly well-balanced manner, and the defects possessed by each of them are suppressed. That is, it is a working medium in which GWP is kept low and durability is ensured, and when used in a thermal cycle, the temperature gradient is smaller and the cycle performance is higher by having higher capacity and efficiency. is there.
  • composition range (R) a more preferred composition range (L) is shown below.
  • the composition range (M) is more preferable.
  • the working medium having the composition range (M) is a working medium in which the characteristics of the HFO-1123, HFO-1234yf, and HFC-32 are exhibited in a particularly well-balanced manner, and the drawbacks of the working medium are suppressed.
  • this working medium has a GWP with an upper limit of 300 or less, and durability is ensured, and when used in a heat cycle, the temperature gradient is less than 5.8, and the relative coefficient of performance and relative This is a working medium having a refrigerating capacity close to 1 and good cycle performance.
  • the upper limit of the temperature gradient is lowered, and the lower limit of the relative coefficient of performance x the relative refrigeration capacity is raised. From the viewpoint of a large relative coefficient of performance, 8% by mass ⁇ HFO-1234yf is more preferable. Further, HFO-1234yf ⁇ 35 mass% is more preferable from the viewpoint of high relative refrigeration capacity.
  • another working medium used in the present invention preferably contains HFO-1123, HFC-134a, HFC-125, and HFO-1234yf, and the combustibility of the working medium is suppressed by this composition. More preferably, it includes HFO-1123, HFC-134a, HFC-125, and HFO-1234yf, and the ratio of the total amount of HFO-1123, HFC-134a, HFC-125, and HFO-1234yf to the total amount of the working medium is 90%.
  • the ratio of HFO-1123 to the total amount of HFO-1123, HFC-134a, HFC-125, and HFO-1234yf is 3% by mass or more and 35% by mass or less, and HFC-134a.
  • the ratio of HFC-125 is preferably 4% by mass to 50% by mass, and the ratio of HFO-1234yf is preferably 5% by mass to 50% by mass.
  • the working medium is non-flammable and excellent in safety, has less influence on the ozone layer and global warming, and has better cycle performance when used in a thermal cycle system. It can be set as the working medium which has these. Most preferably, it includes HFO-1123, HFC-134a, HFC-125, and HFO-1234yf, and the ratio of the total amount of HFO-1123, HFC-134a, HFC-125, and HFO-1234yf to the total amount of the working medium is 90%.
  • the ratio of HFO-1123 to the total amount of HFO-1123, HFC-134a, HFC-125, and HFO-1234yf is 6 mass% or more and 25 mass% or less, and HFC-134a. It is even more preferable that the ratio of HFC-125 is 20% by mass to 35% by mass, the ratio of HFC-125 is 8% by mass to 30% by mass, and the ratio of HFO-1234yf is 20% by mass to 50% by mass.
  • the working medium is non-flammable, and is more excellent in safety, has less influence on the ozone layer and global warming, and is even better when used in a heat cycle system.
  • the working medium having a high cycle performance can be obtained.
  • the working medium used in the composition for a heat cycle system of the present invention may contain carbon dioxide, hydrocarbon, chlorofluoroolefin (CFO), hydrochlorofluoroolefin (HCFO) and the like in addition to the above optional components.
  • CFO chlorofluoroolefin
  • HCFO hydrochlorofluoroolefin
  • Other optional components are preferably components that have little influence on the ozone layer and little influence on global warming.
  • hydrocarbon examples include propane, propylene, cyclopropane, butane, isobutane, pentane, isopentane and the like.
  • a hydrocarbon may be used individually by 1 type and may be used in combination of 2 or more type.
  • the working medium contains a hydrocarbon
  • the content thereof is less than 10% by weight with respect to 100% by weight of the working medium, preferably 1 to 5% by weight, and more preferably 3 to 5% by weight. If a hydrocarbon is more than a lower limit, the solubility of the mineral refrigeration oil to a working medium will become more favorable.
  • CFO examples include chlorofluoropropene and chlorofluoroethylene.
  • CFO 1,1-dichloro-2,3,3,3-tetrafluoropropene (CFO-1214ya), 1 is easy to suppress the flammability of the working medium without greatly reducing the cycle performance of the working medium.
  • CFO-1214yb 3-dichloro-1,2,3,3-tetrafluoropropene (CFO-1214yb) and 1,2-dichloro-1,2-difluoroethylene (CFO-1112) are preferred.
  • One type of CFO may be used alone, or two or more types may be used in combination.
  • the working medium contains CFO
  • the content thereof is less than 10% by weight with respect to 100% by weight of the working medium, preferably 1 to 8% by weight, and more preferably 2 to 5% by weight. If the CFO content is at least the lower limit value, it is easy to suppress the combustibility of the working medium. If the content of CFO is not more than the upper limit value, good cycle performance can be easily obtained.
  • HCFO examples include hydrochlorofluoropropene and hydrochlorofluoroethylene.
  • HCFO 1-chloro-2,3,3,3-tetrafluoropropene (HCFO-1224yd)
  • 1-chloro can be used because flammability of the working medium can be easily suppressed without greatly reducing the cycle performance of the working medium.
  • -1,2-difluoroethylene (HCFO-1122) is preferred.
  • HCFO may be used alone or in combination of two or more.
  • the content of HCFO in 100% by mass of the working medium is less than 10% by mass, preferably 1 to 8% by mass, and more preferably 2 to 5% by mass. If the content of HCFO is equal to or higher than the lower limit value, it is easy to suppress the combustibility of the working medium. If the content of HCFO is not more than the upper limit value, good cycle performance can be easily obtained.
  • the total content of other optional components in the working medium is less than 10% by mass with respect to 100% by mass of the working medium, and 8% by mass. % Or less is preferable, and 5 mass% or less is more preferable.
  • FIG. 1 is a diagram for explaining a refrigeration cycle apparatus including a heat exchange unit according to the present invention.
  • the refrigeration cycle apparatus 100 includes a compressor 11, a heat exchanger 12, an expansion valve 13, a heat exchanger 14, an accumulator 15, a switching valve 16, and blowers 17 and 21.
  • FIG. 1 shows an example in which the heat exchange unit 1 includes a compressor 11, a heat exchanger 12, an expansion valve 13, an accumulator 15, a switching valve 16, and a blower 21, but the heat according to the present invention.
  • the exchange unit 1 should just be provided with the compressor 11 and the heat exchanger 12 at least.
  • the refrigeration cycle apparatus 100 is, for example, an air conditioner or a refrigeration / refrigeration apparatus.
  • the heat exchange unit 1 corresponds to an outdoor unit
  • the heat exchanger 14 corresponds to a heat exchanger provided in the indoor unit.
  • FIG. 1 shows a state in which the heat exchanger 12 dissipates heat and the heat exchanger 14 absorbs heat.
  • FIG. 1 shows a state where a cooling operation or a defrosting operation is performed.
  • a working medium including HFO-1123 is circulated in the order of the compressor 11, the heat exchanger 12, the expansion valve 13, the heat exchanger 14, and the accumulator 15 to form a refrigeration cycle.
  • the high-temperature and high-pressure working medium (steam) discharged from the compressor 11 is supplied to the heat exchanger 12 via the switching valve 16.
  • the working medium supplied to the heat exchanger 12 radiates heat to the air around the heat exchanger 12 and condenses.
  • the airflow that is, the air volume
  • heat exchange heat radiation
  • the working medium depressurized by the expansion valve 13 is supplied to the heat exchanger 14 and expands in the heat exchanger 14 to become a low temperature and a low pressure, thereby lowering the surface temperature of the heat exchanger 14.
  • the heat exchanger 14 whose surface temperature has been lowered absorbs heat from the surrounding air, whereby the air around the heat exchanger 14 is cooled.
  • the blower 17 in the vicinity of the heat exchanger 14, the airflow flowing on the surface of the heat exchanger 14 can be increased, and heat exchange (heat absorption) in the heat exchanger 14 can be promoted.
  • the low-temperature gaseous working medium After absorbing heat in the heat exchanger 14, the low-temperature gaseous working medium returns to the compressor 11 through the switching valve 16 and the accumulator 15. A part of the working medium entering the accumulator 15 is liquefied, and a part of the liquefied working medium is stored in the accumulator 15.
  • the refrigeration cycle apparatus 200 shown in FIG. 2 shows a state where the heat exchanger 12 absorbs heat and the heat exchanger 14 dissipates heat.
  • FIG. 2 shows a state where a heating operation is performed.
  • a working medium including HFO-1123 is circulated in the order of the compressor 11, the heat exchanger 14, the expansion valve 13, the heat exchanger 12, and the accumulator 15 to form a refrigeration cycle. Yes.
  • the circulation direction of the working medium is opposite to that of the refrigeration cycle apparatus 100 shown in FIG.
  • the circulation direction of the working medium can be switched by switching the switching valve 16.
  • the high-temperature and high-pressure working medium (steam) discharged from the compressor 11 is supplied to the heat exchanger 14 via the switching valve 16.
  • the working medium supplied to the heat exchanger 14 radiates heat to the air around the heat exchanger 14 and condenses.
  • the blower 17 in the vicinity of the heat exchanger 14 the airflow flowing on the surface of the heat exchanger 14 can be increased, and heat exchange (heat radiation) in the heat exchanger 14 can be promoted.
  • the working medium that is condensed to be liquid is supplied from the heat exchanger 14 to the expansion valve 13, and is decompressed by the expansion valve 13.
  • the working medium depressurized by the expansion valve 13 is supplied to the heat exchanger 12, expands in the heat exchanger 12, becomes a low temperature and a low pressure, and lowers the surface temperature of the heat exchanger 12.
  • the heat exchanger 12 whose surface temperature has dropped absorbs heat from the surrounding air.
  • the airflow flowing on the surface of the heat exchanger 12 can be increased, and heat exchange (heat absorption) in the heat exchanger 12 can be promoted.
  • the low-temperature gaseous working medium After absorbing heat in the heat exchanger 12, the low-temperature gaseous working medium returns to the compressor 11 through the switching valve 16 and the accumulator 15. A part of the working medium entering the accumulator 15 is liquefied, and a part of the liquefied working medium is stored in the accumulator 15.
  • a heat exchange unit according to the present invention is generated in a compressor for compressing a working medium containing 1,1,2-trifluoroethylene circulating in the refrigeration cycle, a heat exchanger provided in the refrigeration cycle, and the compressor. And heat radiating means for radiating heat without using a working medium. Since the heat exchange unit according to the present invention includes a heat radiating unit that radiates heat generated in the compressor, cooling of the compressor can be promoted. Therefore, generation of disproportionation reaction of HFO-1123 can be suppressed.
  • the heat radiating means is configured by using the blower 21 (see FIG. 3A). That is, the heat of the compressor is radiated using the airflow sent from the blower 21.
  • the heat radiating means is configured using the heat sink 51 (see FIG. 8). That is, the heat generated in the compressor is dissipated by providing the heat sink 51 in the compressor 11.
  • the heat radiating means is configured using a drain water supply unit (see the drain water storage unit 62 and the like shown in FIG. 9). That is, the heat of the compressor is radiated by supplying the drain water generated in the refrigeration cycle to the surface of the compressor using the drain water supply unit.
  • 3A to 3C are respectively a top view, a front view, and a side view showing an example of the heat exchange unit according to the present embodiment.
  • a compressor 11, a heat exchanger 12, an accumulator 15, and a blower 21 are accommodated in a housing 10 formed of a steel plate or the like.
  • the heat exchange unit 1 shown in FIGS. 3A to 3C is an example, and the heat exchange unit 1 may include the expansion valve 13 and the switching valve 16 shown in FIGS. 3A to 3C show a state in which a part of the housing 10 is removed in order to show the internal state of the heat exchange unit 1.
  • the heat exchanger 12 is L-shaped when viewed in plan, and is disposed along the back surface 10_1 and the side surface 10_2 of the housing 10.
  • the blower 21 is fixed to the upper surface 10_5 and the lower surface 10_6 of the housing 10 using a fixing member 22.
  • the blower 21 is driven using a motor 23. Ventilation holes are formed in the back surface 10_1 and the front surface 10_3 of the housing 10, and the wind flows in the direction indicated by the arrow (broken line) in FIG. Thereby, the airflow which flows on the surface of the heat exchanger 12 can be increased, and the heat exchange in the heat exchanger 12 can be promoted.
  • the heat exchanger 12 and the blower 21 are disposed in a space 31 surrounded by the back surface 10_1, the side surface 10_2, the front surface 10_3, and the partition plate 25 of the housing 10.
  • the compressor 11 and the accumulator 15 are disposed in a space 32 surrounded by the rear surface 10_1, the side surface 10_4, the front surface 10_3, and the partition plate 25 of the housing 10.
  • illustration of the piping 18 on the outlet side of the compressor 11 and the piping on the inlet side of the accumulator 15 is omitted, but these piping are connected to the switching valve 16 shown in FIGS. 1 and 2. Has been.
  • the air vent 27 is formed at a position corresponding to the compressor 11 of the partition plate 25.
  • the vent hole 27 is formed at a position where the compressor 11 and the partition plate 25 overlap when the heat exchange unit 1 is viewed from the side. 3A and 3B, the position where the vent hole 27 is formed is indicated by a broken line.
  • the compressor 11 and the accumulator 15 are indicated by broken lines in order to clearly indicate the position of the vent hole 27.
  • FIG. 3C shows an example in which a plurality of ventilation holes 27 are formed in the partition plate 25, but the shape of the ventilation holes in the heat exchange unit 1 according to the present embodiment is not limited to this shape.
  • a vent 28 having a size corresponding to the compressor 11 may be formed in the partition plate 25.
  • the vent hole 28 is formed at a position corresponding to the compressor 11 of the partition plate 25, that is, a position where the compressor 11 and the partition plate 25 overlap when the heat exchange unit 1 is viewed from the side.
  • HFO-1123 sometimes has a chain of chemical reactions accompanied by heat generation called a disproportionation reaction (self-decomposition reaction) when energy is input in a high temperature and high pressure state. For this reason, in the refrigeration cycle apparatus using a working medium containing HFO-1123 as the working medium, it is necessary to suppress the occurrence of such disproportionation reaction. In particular, such a disproportionation reaction is likely to occur in the compressor 11 in which the working medium is at a high temperature and a high pressure.
  • the air vent 27 is formed at a position corresponding to the compressor 11 of the partition plate 25.
  • the vent hole 27 in the partition plate 25 the airflow flowing around the compressor 11 can be increased, and the cooling of the compressor 11 can be promoted. Therefore, generation of disproportionation reaction of HFO-1123 can be suppressed.
  • FIG. 5 is a top view of an example of the heat exchange unit 2 according to the second embodiment.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
  • the heat exchange unit 2 includes a wind direction plate 35 that changes the direction of a part of the airflow sent from the blower 21 to the compressor 11 side.
  • the wind direction plate 35 can be formed using, for example, a steel material or a resin material.
  • the wind direction plate 35 may have a height corresponding to the compressor 11, and in this case, the wind direction plate 35 is fixed to the lower surface 10_6 (see FIG. 3B) of the housing 10. Further, the wind direction plate 35 may be formed so as to extend to the upper and lower surfaces of the housing 10. In this case, the wind direction plate 35 can be fixed to the upper surface 10_5 and the lower surface 10_6 (see FIG. 3) of the housing 10. .
  • the wind direction plate 35 may be configured to be rotatable about an axis extending in the vertical direction of the housing 10 as a central axis. Thereby, the direction of the airflow reflected by the wind direction plate 35 can be adjusted, and the wind direction can be more reliably set to the compressor 11 side.
  • the airflow flowing around the compressor 11 can be increased. Therefore, the cooling of the compressor 11 can be promoted more than the heat exchange unit 1 according to the first embodiment, and the occurrence of the disproportionation reaction of HFO-1123 can be more effectively suppressed.
  • FIG. 6 is a front view of an example of the heat exchange unit 3 according to the third embodiment.
  • 7A and 7B are top views for explaining the operation of the heat exchange unit 3 according to the third embodiment.
  • the heat exchange unit 3 according to the present embodiment is provided with a wind direction switching unit 41 that switches the wind direction of the blower 21 to the compressor 11 side. It differs from the heat exchange unit 1 concerning. Since the configuration other than this is the same as the configuration of the heat exchange unit 1 described in the first embodiment, the same components are denoted by the same reference numerals, and redundant description is omitted.
  • the heat exchange unit 3 includes a wind direction switching unit 41, a detection unit 42, a determination unit 43, and a control unit 44.
  • the air direction switching unit 41 is configured to be able to switch the air direction of the blower 21 to the compressor 11 side. Specifically, as shown in FIGS. 7A and 7B, the air direction switching unit 41 switches the direction of the blower 21 around a rotating shaft 48 extending in the vertical direction of the heat exchange unit 3.
  • FIG. 7A shows a state where the wind direction of the blower 21 is normal
  • FIG. 7B shows a state where the direction of the blower 21 faces the compressor 11 side.
  • the detection unit 42 detects the temperature of the working medium discharged from the compressor 11, specifically, the temperature in the pipe 18 on the outlet side of the compressor 11.
  • the determination unit 43 determines whether or not the temperature of the working medium detected by the detection unit 42 is higher than a predetermined temperature.
  • the control unit 44 controls the wind direction switching unit 41 according to the determination result of the determination unit 43. Specifically, when the temperature of the working medium is higher than a predetermined temperature, the control unit 44 controls the wind direction switching unit 41 so that the wind direction of the blower 21 is on the compressor 11 side as illustrated in FIG. 7B. .
  • the predetermined temperature that serves as a determination criterion in the determination unit 43 is set to a temperature lower than the temperature at which the working medium HFO-1123 undergoes a disproportionation reaction. That is, since the working medium is likely to cause a disproportionation reaction at a high temperature, before the working medium causes a disproportionation reaction, cooling of the compressor 11 is promoted with the air direction of the blower 21 as the compressor 11 side. Thereby, it is possible to suppress the disproportionation reaction from occurring in the compressor 11. For example, the disproportionation reaction can be more reliably suppressed by setting a lower temperature as the predetermined temperature.
  • FIG. 8 is a top view of an example of the heat exchange unit 4 according to the fourth embodiment.
  • the same components as those in the first embodiment are denoted by the same reference numerals, and redundant description is omitted.
  • the compressor 11 is provided with a heat sink 51 for radiating heat generated in the compressor 11.
  • FIG. 8 shows the case where the heat sink 51 is provided in a part of the periphery of the compressor 11, the heat sink 51 may be provided in the entire periphery of the compressor 11.
  • a case where the heat sink 51 is formed on the side of the compressor plate 11 on the side where the vent hole 27 of the partition plate 25 is formed is shown.
  • the compressor 11 can be effectively cooled by forming the heat sink 51 on the side of the partition plate 25 where the vent holes 27 are formed.
  • a material constituting the heat sink 51 a material having high thermal conductivity such as a metal material can be used.
  • the heat sink 51 is provided, so that the cooling of the compressor 11 can be promoted, and the occurrence of the disproportionation reaction of HFO-1123 can be more effectively suppressed. it can.
  • this embodiment may be combined with the second embodiment. That is, you may provide the wind direction board 35 shown in FIG. 5 in the heat exchange unit 4 shown in FIG. With such a configuration, the compressor 11 can be cooled more effectively. Further, this embodiment may be combined with Embodiment 3. That is, the heat exchange unit 4 shown in FIG. 8 may be provided with the wind direction switching unit 41, the detection unit 42, the determination unit 43, and the control unit 44 shown in FIGS. With such a configuration, the compressor 11 can be cooled more effectively.
  • the invention according to this embodiment may be used alone without being combined with other embodiments. That is, in FIG. 8, it is good also as a structure which does not provide the vent hole 27 in the partition plate 25. FIG. In this case, the heat of the compressor 11 can be radiated through the heat sink 51 without providing a vent hole in the partition plate 25.
  • FIG. 9 is a side view showing an example of the heat exchange unit 5 according to the fifth embodiment.
  • the heat exchange unit 5 according to the present embodiment is different from the heat exchange unit 1 according to the first embodiment in that the compressor 11 is cooled using drain water generated in the refrigeration cycle. Since the configuration other than this is the same as the configuration of the heat exchange unit 1 described in the first embodiment, the same components are denoted by the same reference numerals, and redundant description is omitted.
  • the heat exchange unit 5 includes a pipe 61, a drain water storage unit 62, a pipe 63, and a solenoid valve 64. These constitute a drain water supply unit.
  • the drain water storage unit 62 stores drain water generated in the refrigeration cycle. For example, drain water is generated in the heat exchanger 14 of the refrigeration cycle apparatus 100 shown in FIG. The drain water generated in the refrigeration cycle is supplied to the drain water storage unit 62 via the pipe 61. The drain water stored in the drain water storage unit 62 is supplied to the surface of the compressor 11 through the pipe 63. The supply of drain water from the drain water storage unit 62 to the surface of the compressor 11 can be switched using the electromagnetic valve 64. Thus, by supplying drain water to the surface of the compressor 11, the compressor 11 can be cooled.
  • the heat exchange unit 5 further includes a detection unit 66, a determination unit 67, and a control unit 68 as a drain water supply unit.
  • the detection unit 66 detects the temperature of the working medium discharged from the compressor 11, specifically, the temperature in the pipe 18 on the outlet side of the compressor 11.
  • the determination unit 67 determines whether the temperature of the working medium detected by the detection unit 66 is higher than a predetermined temperature.
  • the control unit 68 controls the electromagnetic valve 64 according to the determination result of the determination unit 67. Specifically, when the temperature of the working medium is higher than a predetermined temperature, the control unit 68 opens the electromagnetic valve 64 and supplies drain water from the drain water storage unit 62 to the surface of the compressor 11 for compression. The machine 11 is cooled.
  • the predetermined temperature that is a criterion for determination in the determination unit 67 is set to a temperature lower than the temperature at which the working medium HFO-1123 undergoes a disproportionation reaction. That is, since the working medium is liable to cause a disproportionation reaction at a high temperature, the solenoid valve 64 is opened to supply drain water to the surface of the compressor 11 before the working medium causes the disproportionation reaction. The compressor 11 is cooled. Thereby, it is possible to suppress the disproportionation reaction from occurring in the compressor 11. For example, the disproportionation reaction can be more reliably suppressed by setting a lower temperature as the predetermined temperature.
  • the shape of the pipe 63 for supplying drain water to the surface of the compressor 11 is preferably a shape in which drain water is uniformly supplied to the surface of the compressor 11.
  • drain water can be uniformly supplied to the surface of the compressor 11 by attaching a shower head to the tip of the pipe 63.
  • evaporation of the drain water is promoted, and cooling of the compressor 11 can be promoted.
  • this embodiment may be combined with the second embodiment. That is, you may provide the wind direction board 35 shown in FIG. 5 in the heat exchange unit 5 shown in FIG. With such a configuration, the compressor 11 can be cooled more effectively. Further, this embodiment may be combined with Embodiment 3. That is, the heat exchange unit 5 shown in FIG. 9 may be provided with the wind direction switching unit 41, the detection unit 42, the determination unit 43, and the control unit 44 shown in FIGS. With such a configuration, the compressor 11 can be cooled more effectively. In this case, the detection units 42 and 66, the determination units 43 and 67, and the control units 44 and 68 can be shared. Further, this embodiment may be combined with Embodiment 4. That is, the heat sink 51 shown in FIG. 8 may be provided in the compressor 11 shown in FIG. With such a configuration, the compressor 11 can be cooled more effectively.
  • the invention according to this embodiment may be used alone without being combined with other embodiments. That is, in FIG. 9, it is good also as a structure which does not provide a vent hole in the partition plate 25. FIG. In this case, the heat of the compressor 11 can be radiated using the drain water without providing a vent hole in the partition plate 25.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Lubricants (AREA)
  • Compressor (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

La présente invention concerne une unité d'échange de chaleur (1) comprenant : un compresseur (11) destiné à comprimer un agent actif comportant du 1,1,2-trifluoroéthylène et circulant dans un cycle frigorifique ; un échangeur de chaleur (12) disposé dans le cycle frigorifique ; et un moyen de rayonnement thermique destiné à rayonner, sans utiliser l'agent actif, la chaleur produite à l'intérieur du compresseur (11). Le moyen de rayonnement thermique peut être conçu, par exemple, à l'aide d'une soufflante, d'un dissipateur thermique, d'une unité d'alimentation en eaux d'écoulement ou analogues.
PCT/JP2017/004064 2016-02-22 2017-02-03 Unité d'échange de chaleur WO2017145713A1 (fr)

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EP17756155.2A EP3421903A4 (fr) 2016-02-22 2017-02-03 Unité d'échange de chaleur
JP2018501112A JPWO2017145713A1 (ja) 2016-02-22 2017-02-03 熱交換ユニット
CN201780012665.6A CN108700344A (zh) 2016-02-22 2017-02-03 热交换单元
US16/109,081 US20190003469A1 (en) 2016-02-22 2018-08-22 Heat exchange unit

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JP2016030562 2016-02-22

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EP3421903A4 (fr) 2019-08-28
CN108700344A (zh) 2018-10-23
US20190003469A1 (en) 2019-01-03
JPWO2017145713A1 (ja) 2018-12-20

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