WO2000052398A1 - Dispositif frigorifique - Google Patents

Dispositif frigorifique Download PDF

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Publication number
WO2000052398A1
WO2000052398A1 PCT/JP2000/001184 JP0001184W WO0052398A1 WO 2000052398 A1 WO2000052398 A1 WO 2000052398A1 JP 0001184 W JP0001184 W JP 0001184W WO 0052398 A1 WO0052398 A1 WO 0052398A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
heat transfer
refrigerant
inner diameter
transfer tube
Prior art date
Application number
PCT/JP2000/001184
Other languages
English (en)
Japanese (ja)
Inventor
Koichi Kita
Ryuzaburo Yajima
Original Assignee
Daikin Industries, Ltd.
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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to AU28241/00A priority Critical patent/AU2824100A/en
Publication of WO2000052398A1 publication Critical patent/WO2000052398A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/12—Inflammable refrigerants
    • 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
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant

Definitions

  • the present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus using a single refrigerant of R32 or a mixed refrigerant containing R32.
  • R22 has been often used as a suitable refrigerant for refrigeration systems such as air conditioners.
  • various refrigerants such as R407C, R410A or R134a are being developed as alternative refrigerants to replace R22.
  • each of the above alternative refrigerants has a low ozone depletion potential, but a global warming potential (GWP) equivalent to that of R22. Therefore, the above alternative refrigerants cannot be said to be sufficiently satisfactory from the viewpoint of preventing global warming.
  • GWP global warming potential
  • the COP of the refrigeration system will be lower than before, so the load on thermal power plants etc. will increase with the increase in power consumption, apart from the direct global warming effect due to refrigerant discharge And indirectly contribute to global warming. Therefore, the development of an alternative refrigerant that truly suppresses global warming has been desired.
  • the present invention has been made in view of the above, and an object of the present invention is to provide a refrigeration apparatus that can effectively prevent the global warming by effectively utilizing the characteristics of R32. . Disclosure of the invention
  • the present invention provides a heat exchanger with a heat transfer tube having a smaller diameter than before, so as to reduce the amount of refrigerant charged in a refrigerant circuit while maintaining the same device performance as before.
  • the invention of the first aspect uses a compressor (11), an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat source so as to form a vapor compression refrigeration cycle using R32 as a refrigerant. It is intended for a refrigeration system equipped with a refrigerant circuit (10) having an exchanger (15).
  • the heat transfer tube of the indoor heat exchanger (15) is formed by a heat transfer tube having an inner diameter of 5.9 mm or less.
  • Another invention uses a refrigerant as R32 to form a vapor compression refrigeration cycle, a compressor (11), an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger. It is intended for a refrigeration system equipped with a refrigerant circuit (10) having (15).
  • the heat transfer tube of the indoor heat exchanger (15) is formed by a heat transfer tube having an inner diameter of 4.7 mm to 5.9 mm.
  • the heat transfer tube of the indoor heat exchanger (15) is formed of a heat transfer tube having an inner diameter of 5.3 mm or less.
  • Another invention relates to a compressor (11), an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger that form a vapor compression refrigeration cycle using R32 as a refrigerant. It is intended for a refrigeration system equipped with a refrigerant circuit (10) having (15).
  • the heat transfer tube of the outdoor heat exchanger (13) is formed by a heat transfer tube having an inner diameter of 6.7 mm or less.
  • Another invention uses a refrigerant as R32 to form a vapor compression refrigeration cycle, a compressor (11), an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger. (15) It is intended for a refrigeration system equipped with a refrigerant circuit (10).
  • the inside diameter of the heat transfer tube of the outdoor heat exchanger (13) is 5.4 mn! It is formed by a heat transfer tube that is ⁇ 6.7 mm.
  • the heat transfer tube of the outdoor heat exchanger (13) is formed by a heat transfer tube having an inner diameter of 6.1 mm or less.
  • Another invention provides a compressor (75% by weight or more and less than 100% by weight) that uses a mixed refrigerant of R32 and R125 as a refrigerant to form a vapor compression refrigeration cycle.
  • a refrigeration system equipped with a refrigerant circuit (10) having an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger (15).
  • the heat transfer tube of the indoor heat exchanger (15) is formed by a heat transfer tube having an inner diameter of 6.2 mm or less.
  • Another invention provides a compressor (75% by weight or more and less than 100% by weight) that uses a mixed refrigerant of R32 and R125 as a refrigerant to form a vapor compression refrigeration cycle.
  • a refrigerating system equipped with a refrigerant circuit (10) having an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger (15).
  • the inside diameter of the heat transfer tube of the indoor heat exchanger (15) is 4.7 mn! It is formed by heat transfer tubes that are ⁇ 6.2 mm.
  • the heat transfer tube of the indoor heat exchanger (15) is formed of a heat transfer tube having an inner diameter of 5.5 mm or less from the viewpoint of reducing the amount of refrigerant to be charged.
  • Another invention provides a compressor (75% by weight or more and less than 100% by weight) that uses a mixed refrigerant of R32 and R125 as a refrigerant to form a vapor compression refrigeration cycle.
  • a refrigeration system equipped with a refrigerant circuit (10) having an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger (15).
  • the heat transfer tube of the outdoor heat exchanger (13) is formed by a heat transfer tube having an inner diameter of 7.1 mm or less.
  • Another invention provides a compressor (75% by weight or more and less than 100% by weight) that uses a mixed refrigerant of R32 and R125 as a refrigerant to form a vapor compression refrigeration cycle. 11), a refrigerant circuit having an outdoor heat exchanger (13), a pressure reducing mechanism (14), and an indoor heat exchanger (15) 0
  • the heat transfer tube of the outdoor heat exchanger (13) is formed by a heat transfer tube having an inner diameter of 5.4 mm to 7.1 mm.
  • the heat transfer tube of the outdoor heat exchanger (13) is formed by a heat transfer tube having an inner diameter of 6.3 mm or less.
  • the diameter of the heat transfer tube of the outdoor heat exchanger (13) or the indoor heat exchanger (15) is smaller than in the past.
  • R32 / R125 mixed refrigerant containing R32 single refrigerant or R32 in an amount of 75% by weight or more and less than 100% by weight is regarded as a refrigerant and has a characteristic of R22. Low pressure loss. As a result, even if the inner diameter of the heat transfer tube becomes smaller, the pressure loss of the refrigerant is maintained at the same level as before.
  • the smaller the inner diameter of the heat transfer tube the smaller the amount of refrigerant charged in the refrigerant circuit (10). Therefore, the refrigerant charge is reduced while maintaining the performance equivalent to that of the conventional refrigeration system using R22. Therefore, in addition to the low global warming potential of R32, the global warming effect is significantly reduced by reducing the refrigerant charge of the refrigerant circuit (10). Effect of one invention
  • the present invention by reducing the diameter of the heat transfer tube of the outdoor heat exchanger (13) or the indoor heat exchanger (15) as compared with the conventional device using R22, the same performance as the conventional device can be obtained.
  • the refrigerant charge in the refrigerant circuit (10) can be reduced while maintaining the pressure.
  • the R32 single refrigerant or the R32 mixed refrigerant can be used more effectively than before, and the global warming effect is reduced by reducing the global warming potential of the refrigerant itself and reducing the refrigerant charge. Can be greatly reduced. Therefore, it is possible to provide a device suitable for global environmental protection.
  • the heat exchanger can be downsized by reducing the diameter of the heat transfer tube.
  • FIG. 1 is a refrigerant circuit diagram of the air conditioner.
  • Figure 2 is a Mollier diagram.
  • Figure 3 is a table showing the results of calculating the ratio of the inner diameter of the heat transfer tubes.
  • FIG. 4 is a sectional view of a grooved tube.
  • Figure 5 is a Mollier diagram.
  • FIG. 6 is a table showing calculation results of the inner diameter ratio of the liquid side pipe.
  • FIG. 7 is a diagram showing the pipe diameter of the gas side pipe and the liquid side pipe for R22 with respect to the rated cooling capacity.
  • FIG. 8 is a diagram showing a small diameter ratio of the gas side pipe and the liquid side pipe to the rated cooling capacity.
  • FIG. 9 is a diagram showing the relationship between the R22 copper tube and the R32 copper tube.
  • Figure 10 is a table showing global warming potential.
  • the refrigeration apparatus is an air conditioner (1) formed by connecting an indoor unit (17) and an outdoor unit (16).
  • the refrigerant circuit (10) of the air conditioner (1) uses a single refrigerant of R32 (hereinafter referred to as "32 single refrigerant") as a refrigerant, or 75% by weight or more and 100% by weight.
  • % Of mixed refrigerant of R32 and R125 R32 mixed rich refrigerant, hereinafter referred to as R32 / R125 mixed refrigerant is used as the refrigerant.
  • the refrigerant circuit (10) is a refrigerant circuit forming a vapor compression refrigeration cycle, and is a compressor (11), a four-way switching valve (12), an outdoor heat exchanger (13), and an expansion mechanism.
  • the expansion valve (14) and the indoor heat exchanger (15) are sequentially connected via a gas pipe (31) and a liquid pipe (32), which are refrigerant pipes.
  • the discharge side of the compressor (11) and the first port (12a) of the four-way switching valve (12) are connected by a first gas side pipe (21).
  • the second port (12b) of the four-way switching valve (12) and the outdoor heat exchanger (13) are connected by the second gas side pipe (22).
  • Outdoor The heat exchanger (13) and the expansion valve (14) are connected by the first liquid side pipe (25).
  • the expansion valve (14) and the indoor heat exchanger (15) are connected by the second liquid side pipe (26).
  • the indoor heat exchanger (15) and the third port (12c) of the four-way switching valve (12) are connected by a third gas side pipe (23).
  • the fourth port (12d) of the four-way selector valve (12) and the suction side of the compressor (11) are connected by a fourth gas side pipe (24).
  • the valve (14) and the fourth gas side pipe (24) are housed in an outdoor unit (16) together with an outdoor blower (not shown).
  • the indoor heat exchanger (15) is housed in an indoor unit (17) together with an indoor blower (not shown).
  • a part of the second liquid-side pipe (26) and the third gas-side pipe (23) constitutes a so-called communication pipe that connects the outdoor unit (16) and the indoor unit (17).
  • R32 single refrigerant or R32 / R125 mixed refrigerant has a greater refrigeration effect per unit volume than R222, the required amount of refrigerant circulation to achieve the specified capacity is R2. Less than 2 Therefore, in the case of the R32 single refrigerant or the R32 / R125 mixed refrigerant, when the inner diameter of the heat transfer tube of the heat exchanger is fixed, the refrigerant circulation amount is reduced. It is smaller than 2.
  • the performance of the entire device is reduced due to a decrease in heat transfer area and an increase in refrigerant pressure loss.
  • the refrigerant-side heat transfer coefficient in the heat transfer tube is larger than R22, so the pressure loss in the tube is equivalent to R22. Even if it is increased to the extent, it is possible to exhibit the same or better performance as R22 as a whole.
  • the portion of the refrigerant circuit (10) having the largest amount of refrigerant is the outdoor heat exchanger (13). Therefore, by reducing the diameter of the heat transfer tube of the outdoor heat exchanger (13), the amount of refrigerant charged can be effectively reduced.
  • the outdoor heat exchanger (13) and the indoor heat exchanger (15) will be reduced in size by reducing the diameter of the heat transfer tubes, so that the outdoor unit (16) and the indoor unit (17) will be made more compact. Is also possible. _ ⁇ Therefore, in this air conditioner (1), the diameter of the heat transfer tubes of the outdoor heat exchanger (13) and the indoor heat exchanger (15) is reduced until the pressure loss in the tubes reaches the same level as R22. I decided that.
  • this air conditioner (1) considering the amount of change in the refrigerant saturation temperature corresponding to the pressure loss in the heat transfer tube, the outdoor heat exchange was performed so that the amount of change in temperature would be equal to R22.
  • the inner diameter of the heat transfer tubes of the heat exchanger (13) and the indoor heat exchanger (15) was set.
  • the outdoor heat exchanger (T) is set so that the saturation temperature change amount ⁇ Te corresponding to the pressure loss of the evaporative refrigerant becomes equal to the saturation temperature change amount of R 22 in the conventional device. 13) Set the heat transfer tubes of the indoor heat exchanger (15). That is,
  • the ratio of the inner diameter of the heat transfer tube for R32 to the heat transfer tube for R22 is given by the following formula. You can ask for it.
  • FIG. 3 shows a calculation result obtained by substituting each physical property value into the above equation (6).
  • the evaporation temperature Te was assumed to be 2 ° C and the condensing temperature Tc was assumed to be 49 ° C, and the superheat SH at the evaporator outlet was set to 5 ° and the subcool SC at the condenser outlet was set to 5 °.
  • the heat transfer tubes of the indoor heat exchanger (15) must be The diameter is 4.7mn!
  • the heat transfer tube of the outdoor heat exchanger (13) is formed of a heat transfer tube with an inner diameter of 5.4 mm to 6.7 mm.
  • the inside diameter of the heat transfer tube of the indoor heat exchanger (15) is 4.7mn!
  • the heat transfer tube of the outdoor heat exchanger (13) has an inner diameter of 5.4mn! It was decided to be formed of 7.1 mm heat transfer tube.
  • each heat transfer tube When the inner diameter of each heat transfer tube is smaller than the above numerical range, the refrigerant pressure is further reduced, but the refrigerant pressure loss becomes excessive. On the other hand, if the inner diameter of each heat transfer tube is larger than the above numerical range, the refrigerant pressure loss is reduced and the efficiency of the device is improved, but the effects of R32, such as the effect of reducing the refrigerant charge, should be fully utilized. Becomes difficult.
  • the inner diameters of the heat transfer tubes of the outdoor heat exchanger (13) and the indoor heat exchanger (15) are set within the above numerical ranges.
  • the heat transfer tube of the indoor heat exchanger is formed of a heat transfer tube with an inner diameter of 4.9 mm-5.7 mm, and the heat transfer tube of the outdoor heat exchanger (13)
  • the inner diameter of the heat transfer tube is 5.6mn! It may be formed of a heat transfer tube of up to 6.5 mm.
  • the heat transfer tube of the indoor heat exchanger (15) is formed of a heat transfer tube having an inner diameter of 5.1 mm to 5.5 mm, and the heat transfer tube of the outdoor heat exchanger (13) is used.
  • the heat transfer tube may be formed of a heat transfer tube having an inner diameter of 5.8 mm to 6.3 mm.
  • the heat transfer tube of the indoor heat exchanger (15) is formed of a heat transfer tube with an inner diameter of 4.9 mm to 6.0 mm, and the heat transfer tube of the outdoor heat exchanger (13) is used.
  • the heat transfer tube may be formed of a heat transfer tube having an inner diameter of 5.6 mm to 6.9 mm.
  • the inside diameter of the heat transfer tube of the indoor heat exchanger (15) is 5.2mn!
  • the heat transfer tube of the outdoor heat exchanger (13) may be formed of a heat transfer tube with an inner diameter of 5.9 mm to 6.6 mm.
  • the inner diameter of the heat transfer tube means the inner diameter of the tube after expansion in the case of a smooth inner surface tube.
  • the heat transfer tube various heat transfer tubes such as a copper tube and an aluminum tube can be used.
  • the external heat exchanger (13) and the indoor heat exchanger (13) according to the present embodiment are a type of air heat exchanger for performing heat exchange with air, which is a plate fin tube heat exchanger composed of copper tubes and aluminum fins.
  • the heat transfer tubes are made of copper tubes.
  • the pressure loss of the refrigerant is reduced. Therefore, even if the inside diameter of the liquid side pipe (32) of the refrigerant circuit (10) is reduced to increase the pressure loss in the pipe to the same level as when R22 is used, the performance of the device is maintained at the same level as before. Is done. Therefore, in this air conditioner (1), the liquid side pipe (32) is reduced in diameter until the pressure loss in the pipe becomes R22, so that the refrigerant circuit (10) is maintained while maintaining the performance of the apparatus. Refrigerant charge was reduced.
  • the gas side pipe (31), especially the fourth gas side pipe (24), which is the suction pipe for the compressor (11), is reduced in diameter, the amount of refrigerant charged will not be reduced so much, but the suction
  • the efficiency of the equipment is greatly reduced due to the effect of the increased pressure loss. Such a reduction in the efficiency of the equipment indirectly leads to an increase in the effect of global warming.
  • the gas side pipe (31) is the same as the conventional R22 gas side pipe, and only the liquid side pipe (32) is smaller than the conventional R22 liquid side pipe. Was also reduced in diameter.
  • the liquid-side piping (32) is sized so that the ratio of the pressure drop of the liquid-side piping (32) to the pressure drop of the refrigerant from the condenser outlet to the evaporator inlet accounts for the same amount as in R22.
  • Design (32) That is, the following equation is established using the symbols shown in FIG. (Pco-Pvi) + (Pvo-Pbi)
  • the ratio of the small diameter of the liquid side pipe (32) of R32 to the liquid side pipe of R22 is calculated as follows. be able to.
  • FIG. 6 shows a calculation result obtained by substituting each physical property value into the above equation (12).
  • the evaporation temperature Te was 2 ° C
  • the condensation temperature Tc was 49 ° C
  • the superheat SH was 5 deg
  • the subcool SC was 5 deg.
  • the liquid side pipe (32) of the R32 single refrigerant can be reduced to about 0.76 times the diameter of the liquid side pipe for R22. It was also found that the R32 / R125 mixed refrigerant can be reduced in diameter to about 0.76 to 0.8 times if the composition of R32 is contained at 75% by weight or more. . For reference, similar calculations were performed for other alternative refrigerants, but it was found that the effect of reducing the diameter as compared to R32 could not be obtained (see Fig. 6).
  • FIG. 7 is a diagram showing the pipe diameter (outer diameter) of the gas side pipe and the liquid side pipe in the conventional apparatus using R22 for each cooling capacity rating.
  • the gas side pipe (31) uses the same diameter as the R22 gas side pipe, while the liquid side pipe (32) uses the above. Use a pipe with a smaller diameter than the liquid side pipe for R22.
  • gas side piping (31) and liquid side piping (32) having the following inner diameter ratios are used according to the rated cooling capacity.
  • the rated cooling capacity when the rated cooling capacity is more than 5 kW and less than 9 kW, use the gas side pipe (31) and the liquid side pipe (32) so that the above inner diameter ratio becomes 2.1 to 3.5. .
  • the rated cooling capacity is 5 kW or less or greater than 9 kW, the above inner diameter ratio is 2.6
  • Cooling rating is greater than 5 kW and 22.
  • the inner diameter ratio or the inner diameter of the liquid side pipe (32) is smaller than the above numerical range, the refrigerant performance is further reduced, though the refrigerant charging amount is further reduced.
  • the inner diameter ratio or the inner diameter of the liquid side pipe (32) is larger than the above numerical range, the effect of reducing the refrigerant charge is reduced although the refrigerant pressure loss is reduced and the device performance is improved.
  • the gas-side pipe (31) and the liquid-side pipe (32) are set within the above numerical ranges so that the refrigerant filling amount can be sufficiently reduced while maintaining the performance of the apparatus. .
  • the above inner diameter ratio may be set to 2.4 to 3.2.
  • the above inner diameter ratio may be 2.8-3.3.
  • the inner diameter ratio may be set to 2.6 to 3.0.
  • the above inner diameter ratio may be set to 2.9 to 3.1.
  • the inner diameter of the liquid side pipe (32) is 3.5 m ⁇ when the rated cooling capacity is 5 kW or less. Up to 3.9 mm, 5.7 mm to 6.7 mm when the rated cooling capacity is greater than 5 kW and less than 22.4 kW, and 7.8 mm when the rated cooling capacity is 22.4 kW or more It may be 9.5 mm.
  • the inner diameter of the liquid side pipe (32) should be 3.6 mm to 3.8 mm when the cooling capacity is 5 kW or less, and the cooling capacity should be greater than 5 kW and less than 22.4 kW. 6. Omn! When the rated cooling capacity is 22.4 kW or more, it may be 8.1 mm to 9.1 mm.
  • both the liquid side pipe (32) and the gas side pipe (31) should be composed of only standard products. Is preferred.
  • Fig. 9 compares the specifications of the copper pipe for R22 (JISB 8607) with the specifications of the high-pressure compliant pipe for R32 proposed by the Japan Refrigeration and Air Conditioning Industry Association (Nichirei).
  • the optimum inner diameter ratio calculated from the above calculation results is 0.76 for the R32 single refrigerant, and 0.80 for the R32 / R125 mixed refrigerant containing 75% by weight of R32. From FIG. 9 above, it was found that within the range of ⁇ 10% of the optimal inner diameter ratio, the combination of standard products can easily realize the inner diameter ratio.
  • the present embodiment is a form that can be easily realized by combining standard products.
  • the operation of the air conditioner (1) will be described based on the refrigerant circulation operation in the refrigerant circuit (10).
  • the four-way switching valve (12) is set to the solid line side shown in Fig. 1. That is, in the four-way switching valve (12), the first port (12a) and the second port (12b) communicate with each other, and the third port (12c) and the fourth port (12d) communicate with each other.
  • the gas refrigerant discharged from the compressor (11) flows through the first gas side pipe (21), the four-way switching valve (12), and the second gas side pipe (22), and passes through the outdoor heat exchanger. Condensed in (13).
  • the liquid refrigerant flowing out of the outdoor heat exchanger (13) flows through the first liquid side pipe (25), and is expanded.
  • the pressure is reduced to a gas-liquid two-phase refrigerant.
  • the two-phase refrigerant flowing out of the expansion valve (14) flows through the second liquid side pipe (26), exchanges heat with the indoor air in the indoor heat exchanger (15), evaporates, and cools the indoor air.
  • the gas refrigerant flowing out of the indoor heat exchanger (15) flows through the third gas-side pipe (23), the four-way switching valve (12), and the fourth gas-side pipe (24), and flows to the compressor (11). Inhaled o
  • the four-way switching valve (12) is set to the broken line side shown in FIG. In other words, the four-way switching valve (12) is in a state where the first port (12a) and the fourth port (12d) communicate with each other, and the second port (12b) and the third port (12c) communicate with each other. .
  • the gas refrigerant discharged from the compressor (11) flows through the first gas-side pipe (21), the four-way switching valve (12), and the third gas-side pipe (23), and passes through the indoor heat exchanger. (15).
  • the refrigerant flowing into the indoor heat exchanger (15) exchanges heat with the indoor air to condense and heat the indoor air.
  • the liquid refrigerant flowing out of the indoor heat exchanger (15) flows through the second liquid side pipe (26) and is decompressed by the expansion valve (14) to become a gas-liquid two-phase refrigerant.
  • the two-phase refrigerant flowing out of the expansion valve (14) flows through the first liquid side pipe (25) and evaporates in the outdoor heat exchanger (13).
  • the gas refrigerant flowing out of the outdoor heat exchanger (13) flows through the second gas pipe (22), the four-way switching valve (12), and the fourth gas pipe (24), and is sucked into the compressor (11). Is done.
  • R32 single refrigerant or R32 / R125 mixed refrigerant is used as the refrigerant, and the heat transfer tubes of the outdoor heat exchanger (13) and the indoor heat exchanger (15) are used. Since the diameter was made smaller than before, it became possible to reduce the amount of refrigerant charged while maintaining the performance of the device, and to reduce the effect of global warming.
  • the cost and size of the outdoor heat exchanger (13) and the indoor heat exchanger (15) can be reduced and the indoor unit (17) and the outdoor unit (16) can be reduced. ) Can be reduced in size.
  • Embodiment 1 In addition, by forming the liquid-side pipe (32) with a relatively small-diameter pipe, it is possible to further reduce the amount of refrigerant charged in the refrigerant circuit (10) while maintaining the same operating efficiency as before. became. Therefore, the characteristics of R32, which have a small global warming potential and a small pipe pressure loss, can be fully utilized, and the global warming effect can be greatly reduced.
  • Other Embodiment 1
  • the so-called heat pump type air conditioner capable of selectively performing the cooling operation and the heating operation is described. It may be a cooling only machine.
  • the present invention is applied to a heating-only machine by setting the inner diameter of the liquid side pipe (32) and the gas side pipe (31) or the ratio of the inner diameter to each of the heating rated capacity corresponding to the cooling rated capacity. It is also possible to do so.
  • the gas side pipe (31) and the liquid side pipe (32) need not necessarily be formed of copper pipes, but may be formed of other pipes such as SUS pipes, aluminum pipes, and iron pipes.
  • the outdoor heat exchanger (13) and the indoor heat exchanger (15) are not limited to the air heat exchanger, but may be a liquid-liquid heat exchanger such as a double tube heat exchanger.
  • the internal volume of the refrigerant circuit (10) is reduced. (The internal volume of the part through which the refrigerant passes). Therefore, the amount of air, moisture, impurities and the like mixed in the refrigerant circuit (10) becomes smaller than before, and the opportunity for the refrigerating machine oil to come into contact with moisture and the like is reduced. Therefore, according to the present embodiment, the deterioration of the refrigerating machine oil is less likely to occur than before. Therefore, when synthetic oil such as ether oil or ester oil is used as the refrigerating machine oil, the superiority of the present embodiment is more remarkably exhibited.
  • the refrigeration apparatus of the present invention is not limited to a refrigeration apparatus in a narrow sense, but is a refrigeration apparatus in a broad sense including a refrigeration apparatus, a dehumidifier, and the like, as well as the air conditioner described above.
  • the cooling rated capacity in the above embodiment means the capacity of the evaporator, and is not limited to the capacity of the air conditioner at the time of cooling.
  • the cooling capacity rating is that the connecting pipe length is 5 m and the indoor unit and outdoor unit When the height difference is 0 m, the ability to be exhibited under the specified JIS conditions (indoor dry bulb temperature of 27 ° C, indoor wet bulb temperature of 19 ° C, outdoor dry bulb temperature of 35 ° C) is there.
  • the refrigeration apparatus of the present invention is useful when a refrigerant having a small ozone depletion coefficient is used, and is suitable for a refrigeration apparatus that can truly prevent global warming.

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

Abstract

L'invention concerne un circuit frigorifique (10) comprenant un compresseur (11), une soupape de commutation à quatre voies (12), un échangeur thermique d'extérieur (13), un détendeur (14) et un échangeur thermique d'intérieur (15) connectés en ordre entre eux. Un R32 est injecté dans ce circuit. Des tubes de transfert de chaleur de l'échangeur thermique d'intérieur (15) sont constitués de tubes de transfert de chaleur présentant un diamètre intérieur compris entre 4,7 et 5,9 mm, tandis que les tubes de transfert de chaleur de l'échangeur thermique d'extérieur (13) sont constitués de tubes de transfert de chaleur présentant un diamètre intérieur compris entre 5,4 et 6,7 mm.
PCT/JP2000/001184 1999-03-02 2000-03-01 Dispositif frigorifique WO2000052398A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU28241/00A AU2824100A (en) 1999-03-02 2000-03-01 Refrigerating device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11054289A JP2000257974A (ja) 1999-03-02 1999-03-02 冷凍装置
JP11/54289 1999-03-02

Publications (1)

Publication Number Publication Date
WO2000052398A1 true WO2000052398A1 (fr) 2000-09-08

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PCT/JP2000/001184 WO2000052398A1 (fr) 1999-03-02 2000-03-01 Dispositif frigorifique

Country Status (4)

Country Link
JP (1) JP2000257974A (fr)
CN (1) CN2460895Y (fr)
AU (1) AU2824100A (fr)
WO (1) WO2000052398A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001194016A (ja) 1999-10-18 2001-07-17 Daikin Ind Ltd 冷凍装置
JP2002089978A (ja) * 2000-09-11 2002-03-27 Daikin Ind Ltd ペア型の冷凍装置およびマルチ型の冷凍装置
CN102003740A (zh) * 2010-11-23 2011-04-06 Tcl空调器(中山)有限公司 一种载冷式空调器
WO2016051606A1 (fr) * 2014-10-03 2016-04-07 三菱電機株式会社 Dispositif de climatisation

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5599562A (en) * 1979-01-24 1980-07-29 Tokyo Shibaura Electric Co Heat pump type air conditioner
JPH08233377A (ja) * 1995-02-28 1996-09-13 Sanyo Electric Co Ltd 空気調和装置
EP0732550A2 (fr) * 1995-03-14 1996-09-18 Kabushiki Kaisha Toshiba Installation de climatisation
JPH10170081A (ja) * 1996-12-11 1998-06-26 Toshiba Corp 空気調和装置
JPH10176867A (ja) * 1996-12-13 1998-06-30 Toshiba Corp 空気調和装置
WO1998041803A1 (fr) * 1997-03-17 1998-09-24 Daikin Industries, Ltd. Conditionneur d'air
JPH1163735A (ja) * 1997-08-12 1999-03-05 Toshiba Corp 冷凍サイクル装置
JPH11108480A (ja) * 1997-10-01 1999-04-23 Daikin Ind Ltd 空気調和機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5599562A (en) * 1979-01-24 1980-07-29 Tokyo Shibaura Electric Co Heat pump type air conditioner
JPH08233377A (ja) * 1995-02-28 1996-09-13 Sanyo Electric Co Ltd 空気調和装置
EP0732550A2 (fr) * 1995-03-14 1996-09-18 Kabushiki Kaisha Toshiba Installation de climatisation
JPH10170081A (ja) * 1996-12-11 1998-06-26 Toshiba Corp 空気調和装置
JPH10176867A (ja) * 1996-12-13 1998-06-30 Toshiba Corp 空気調和装置
WO1998041803A1 (fr) * 1997-03-17 1998-09-24 Daikin Industries, Ltd. Conditionneur d'air
JPH1163735A (ja) * 1997-08-12 1999-03-05 Toshiba Corp 冷凍サイクル装置
JPH11108480A (ja) * 1997-10-01 1999-04-23 Daikin Ind Ltd 空気調和機

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
"JYOKYU HYOJUN TEXT REITO KUCHO GIJUTSU", SHADAN HOJIN NIPPON REITO KYOKAI, XX, XX, 20 January 1988 (1988-01-20), XX, pages 125 - 143, XP002946287 *
BURNS L D, HOFFMAN L, SCHUSTER D: "R 410 A EXPERIENCES IN UNITARY AIR CONDITINER SYSTEMS", REITO - REFRIGERATION, NIPPON REITO KYOKAI, TOKYO,, JP, vol. 72, no. 834, 15 April 1997 (1997-04-15), JP, pages 369 - 374, XP002946678, ISSN: 0034-3714 *

Also Published As

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CN2460895Y (zh) 2001-11-21
JP2000257974A (ja) 2000-09-22
AU2824100A (en) 2000-09-21

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