WO2011148567A1 - Refrigeration device and cooling and heating device - Google Patents
Refrigeration device and cooling and heating device Download PDFInfo
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- WO2011148567A1 WO2011148567A1 PCT/JP2011/002369 JP2011002369W WO2011148567A1 WO 2011148567 A1 WO2011148567 A1 WO 2011148567A1 JP 2011002369 W JP2011002369 W JP 2011002369W WO 2011148567 A1 WO2011148567 A1 WO 2011148567A1
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- refrigerant
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- heat exchanger
- refrigeration apparatus
- indoor heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/21—Refrigerant outlet evaporator temperature
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- 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
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
Definitions
- the present invention relates to a refrigeration apparatus and a cooling / heating apparatus using a refrigerant.
- HFC As the refrigerant used in the refrigeration apparatus, HCFC is used as an alternative refrigerant after ozone layer destruction due to the use of Freon has become a problem, and HFC (R410A) is currently widely used as shown in FIG. For example, see Patent Document 1.
- the global warming potential (GWP) of the R410A refrigerant is as large as 2088, which is a problem from the viewpoint of preventing global warming.
- HWP1234yf of GWP4 has been proposed as a refrigerant with a small GWP, but this refrigerant has a small refrigerating capacity per unit volume as compared with the R410A refrigerant.
- this refrigerant is applied as it is in the conventional apparatus to obtain the same capacity as the R410A refrigerant, it is necessary to increase the volume circulation amount of the refrigerant by increasing the rotation speed of the compressor.
- the cylinder volume of the compressor is increased so as to increase the refrigerant circulation amount so as to have the same capacity as the R410A refrigerant during the cooling operation, the pressure loss in the heat exchanger increases, and the predetermined cooling capacity cannot be secured.
- the present invention has been made in view of such problems of the prior art, and reduces the pressure loss of the heat exchanger even when a refrigerant having a small refrigeration capacity per unit volume compared to the R410A refrigerant is used. It is an object of the present invention to provide a highly efficient refrigeration apparatus and air conditioning apparatus while ensuring cooling capacity.
- the present invention comprises at least a compressor, an outdoor heat exchanger, a throttle device, and an indoor heat exchanger in order to form an annular refrigerant circuit, and as a refrigerant sealed in the refrigerant circuit,
- the indoor heat exchanger includes a plurality of fins arranged at predetermined intervals, and the refrigerant passes through the fins at a substantially right angle so that the refrigerant passes inside.
- a heat transfer tube that circulates is provided, and the mass flow rate of the refrigerant that flows inside the heat transfer tube includes three or more different portions.
- the pressure loss of the heat exchanger can be reduced even when a refrigerant having a small refrigeration capacity per unit volume compared to the R410A refrigerant can be used, so that the cooling capacity of the refrigeration apparatus can be ensured and high efficiency can be achieved. Can be.
- FIG. 1 is a configuration diagram of an air conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is a diagram of refrigeration capacity per unit volume of R410A refrigerant and HFO1234yf refrigerant.
- FIG. 3 is an indoor heat exchanger piping diagram for the R410A refrigerant.
- FIG. 4 is a diagram of mass flow rate, dryness, saturation temperature difference, and cooling capacity when an indoor heat exchanger for R410A refrigerant is used.
- FIG. 5 is a PH diagram when an indoor heat exchanger for R410A refrigerant is used.
- FIG. 6 is an indoor heat exchanger piping diagram according to Embodiment 1 of the present invention.
- FIG. 1 is a configuration diagram of an air conditioning apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is a diagram of refrigeration capacity per unit volume of R410A refrigerant and HFO1234yf refrigerant.
- FIG. 3 is an indoor heat exchanger piping
- FIG. 7 is a diagram of mass flow rate, dryness, saturation temperature difference, and cooling capacity when the indoor heat exchanger of FIG. 6 is used.
- FIG. 8 is a PH diagram when the indoor heat exchanger piping of FIG. 6 is used.
- 9 (a) and 9 (b) are partial arrangement diagrams of the indoor heat exchanger in FIG.
- FIG. 10 is a diagram showing a calculation result when the mass flow rate per unit capacity is changed.
- FIG. 11 is a block diagram of a conventional air conditioning unit
- a refrigerant having a smaller refrigeration capacity per unit volume than the R410A refrigerant is used as the refrigerant sealed in the refrigerant circuit, and the indoor heat exchangers are arranged at predetermined intervals.
- the indoor heat exchangers are arranged at predetermined intervals.
- the portion when the indoor heat exchanger functions as an evaporator, the portion is configured as an inlet portion, an intermediate portion, and an outlet portion along the refrigerant flow.
- the mass flow rate in the pipe of the refrigerant per unit capacity flowing to the inlet part, the intermediate part, and the outlet part is 0.44 g / mm 2 hW or more and less than 0.50 g / mm 2 hW, 0.14 g / mm 2 hW more than 0.16 g / mm 2 less than hW, those having the structure such that a 0.15 g / mm 2 less than hW at 0.13 g / mm 2 hW more.
- the dryness of the refrigerant flowing through the inlet portion, the intermediate portion, and the outlet portion is 0.215 or more at the standard cooling capacity. And below 0.437, above 0.437 and below 0.8, and above 0.8 and below 1.0. According to this aspect, it is possible to optimize the mass flow rate during cooling operation, suppress pressure loss, and obtain an appropriate temperature difference between air and refrigerant.
- the refrigerant flowing through the inlet portion, the intermediate portion, and the outlet portion when the indoor heat exchanger has an intermediate cooling capacity.
- the dryness was 0.23 or more and less than 0.408, 0.408 or more and less than 0.645, and 0.645 or more and 1.0 or less. According to this aspect, it is possible to optimize the mass flow rate during cooling operation, suppress pressure loss, and obtain an appropriate temperature difference between air and refrigerant.
- the part includes the outlet part, the intermediate part, and the inlet when the indoor heat exchanger functions as a condenser.
- pipe mass flow rate of refrigerant per unit capacity flowing through the site each 0.121 g / mm 2 less than hW at 0.120 g / mm 2 hW above, 0.127 g / mm 2 hW least 0.129 g / mm 2 hW below, was constructed such that a 0.451 g / mm 2 less than hW at 0.446 g / mm 2 hW more. According to this aspect, it is possible to suppress the performance degradation even during the heating operation, and to obtain an optimal annual efficiency that is well balanced with the cooling performance.
- the refrigerant flowing through the outlet part, the intermediate part, and the inlet part was 0.408 or more and less than 1.00, 0 or more and less than 0.408 and 0.00. According to this aspect, it is possible to suppress the performance degradation even during the heating operation, and to obtain an optimal annual efficiency that is well balanced with the cooling performance.
- the refrigerant flowing through the outlet portion, the intermediate portion, and the inlet portion when the indoor heat exchanger has an intermediate heating capacity.
- the dryness was 0.681 or more and less than 1.00, 0.163 or more and less than 0.681, and 0.00 or more and 0.681 or less.
- a four-way valve in the refrigeration apparatus according to any one of the first to seventh aspects to change the direction of the refrigerant flowing through the outdoor heat exchanger and the indoor heat exchanger. Made possible. According to this aspect, it is possible to switch between the cooling operation and the heating operation.
- an indoor air supply mechanism that supplies the indoor heat exchanger is provided, and the indoor heat exchanger is a condenser.
- the downstream of the flow direction of the refrigerant in the indoor heat exchanger is the upstream of the air flow formed by the indoor blowing mechanism. According to this aspect, the efficiency at the time of heating operation can be improved.
- the refrigerant is a refrigerant having a base component of hydrofluoroolefin having a double bond between carbon and carbon.
- a single refrigerant or a mixed refrigerant containing the refrigerant is filled.
- FIG. 1 is a configuration diagram of an air conditioning apparatus according to the present embodiment.
- the air conditioning apparatus includes a compressor 1 that compresses refrigerant, a four-way valve 2 that switches a refrigerant circuit during cooling and heating operation, an outdoor heat exchanger 3 that exchanges heat between the refrigerant and outside air, and a throttle that depressurizes the refrigerant.
- the apparatus 4 includes an indoor heat exchanger 5 that exchanges heat between refrigerant and room air.
- the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the expansion device 4, and the indoor heat exchanger 5 are connected in a ring shape with a connecting pipe.
- the outdoor unit 10 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, and an expansion device 4, and the indoor unit 11 includes an indoor heat exchanger 5.
- the outdoor unit 10 and the indoor unit 11 are connected by a connection pipe A12 and a connection pipe B13.
- the refrigerant compressed by the compressor 1 becomes a high-temperature and high-pressure refrigerant and is sent to the outdoor heat exchanger 3 through the four-way valve 2. Then, heat is exchanged with the outside air to dissipate the heat, and the high-pressure liquid refrigerant is sent to the expansion device 4.
- the refrigerant is decompressed to become a low-temperature and low-pressure two-phase refrigerant, passes through the connecting pipe B 13, enters the indoor heat exchanger 5, exchanges heat with the indoor air, absorbs heat, evaporates and becomes a low-temperature gas refrigerant. At this time, the room air is cooled to cool the room. Further, the refrigerant is returned to the compressor 1 through the connection pipe A12 and the four-way valve 2.
- the refrigerant compressed by the compressor 1 becomes a high-temperature and high-pressure refrigerant and is sent to the connection pipe A12 through the four-way valve 2. Then, it enters the indoor heat exchanger 5 to exchange heat with room air to dissipate heat, and is cooled to become a high-pressure liquid refrigerant. At this time, the room air is heated to heat the room. Thereafter, the refrigerant is sent to the expansion device 4 through the connection pipe B13, and is reduced in pressure by the expansion device 4 to become a low-temperature and low-pressure two-phase refrigerant, and is sent to the outdoor heat exchanger 3 to exchange heat with the outside air to evaporate. And returned to the compressor 1 via the four-way valve 2. In this way, the air conditioning operation is performed.
- the refrigerant circuit constituting the cooling / heating apparatus encloses a refrigerant having a smaller refrigeration capacity per unit volume than the R410A refrigerant.
- This refrigerant is a refrigerant based on tetrafluoropropene in a hydrofluoroolefin having a double bond between carbon and carbon.
- HFO1234yf will be described as an example.
- FIG. 2 shows a comparison of the refrigeration capacity per unit volume between the R410A refrigerant and the HFO1234yf refrigerant.
- FIG. 2 shows saturated gas density, latent heat of vaporization, and refrigerating capacity per unit volume of the evaporator (saturated gas density x latent heat of vaporization) for R410A refrigerant and HFO1234yf refrigerant when the evaporation temperature of the evaporator is 5 ° C and 10 ° C. Yes.
- the refrigerating capacity per unit volume at the time of cooling operation when the evaporation temperature 5 ° C., a 3310.5kJ / m 3 In 7715.1kJ / m 3, HFO1234yf at R410A, also the evaporation temperature 10
- R410A has 8742.6 kJ / m 3
- HFO1234yf has 3791.7 kJ / m 3
- HFO1234yf is about 1 / 2.3 times R410A. Therefore, in order to make the refrigeration capacity of HFO1234yf comparable to R410A, the volume flow rate of refrigerant per unit time (hereinafter referred to as refrigerant circulation amount) needs to be about 2.3 times that of R410A.
- FIG. 3 shows an example of the indoor heat exchanger 5 for the R410A refrigerant.
- the indoor heat exchanger 5 includes a plurality of fins 19 arranged at predetermined intervals, and heat transfer tubes that penetrate the fins 19 at substantially right angles and through which the refrigerant flows. Further, air and the refrigerant exchange heat with the blower 18. Furthermore, it comprises an inlet part 80, an intermediate part 81, and an outlet part 82 along the flow of the refrigerant, and has different mass flow rates for each part.
- the flow of the refrigerant is sent from the expansion device 4, flows in from the heat transfer tube 50, enters the heat transfer tube 52 through the heat transfer tube 51, and reaches the heat transfer tube 53. After four branches from the heat transfer tube 53 to the heat transfer tubes 60, 61, 62 and 63, the refrigerant reaches the heat transfer tubes 60 ', 61', 62 'and 63', respectively.
- the refrigerant of the heat transfer tubes 60 ′, 61 ′, 62 ′, and 63 ′ branches, for example, through a header (not shown) into the heat transfer tubes 70 and 71 at a substantially equal flow rate to reach the heat transfer tubes 70 ′ and 71 ′.
- the refrigerant is returned to the compressor 1 through the connection pipe B13 and the four-way valve 2.
- FIG. 4 shows the mass flow rate, the dryness, the saturation temperature difference, and the cooling capacity of each part of each refrigerant when the indoor heat exchanger 5 for R410A refrigerant in FIG. 3 is used and R410A and HFO1234yf are used as refrigerants. Yes.
- the saturation temperature difference was used as an index of pressure loss.
- the saturation temperature difference was determined by obtaining the saturation temperature for each refrigerant from the refrigerant pressure at the inlet and outlet of the indoor heat exchanger 5. Since the relationship between pressure and temperature differs depending on the refrigerant, the pressure loss related to performance cannot be simply compared as a pressure difference. When comparing the pressure loss of different refrigerants, it is customary to match the saturation temperature difference, and it can be determined that the greater the saturation temperature difference, the greater the pressure loss.
- FIG. 4 also shows data under conditions where the cooling capacity is maximized by increasing the refrigerant circulation rate when HFO1234yf is used.
- FIG. 5 shows a PH diagram under the conditions of FIG. 4 using the indoor heat exchanger 5 for R410A refrigerant in FIG. 3 and using HFO1234yf refrigerant.
- Point A indicates the compressor inlet
- point B indicates the compressor discharge
- point C indicates the condenser inlet
- point D indicates the condenser outlet
- point E indicates the evaporator inlet
- point F indicates the evaporator outlet.
- FIG. 5 shows that the slope of the line from the point E to the point F at the entrance / exit of the evaporator is large, and the pressure loss is large because the refrigerant circulation amount is increased. Further, since the temperature of the refrigerant increases from the point F toward the point E, the temperature difference between the refrigerant and the air that is the heat exchange fluid gradually decreases, and the temperature difference at the point E that is the inlet of the indoor heat exchanger 5. Is negligible. Thus, since the heat exchange amount is reduced by reducing the difference between the refrigerant and the air temperature, a predetermined cooling capacity cannot be ensured.
- FIG. 6 is an example of the indoor heat exchanger 5 of the present invention.
- the indoor heat exchanger 5 includes a plurality of fins 19 arranged at predetermined intervals, and heat transfer tubes that penetrate the fins 19 at substantially right angles and through which the refrigerant flows. Further, air and the refrigerant exchange heat with the blower 18. At this time, the refrigerant flow and the air flow direction are the same. Furthermore, it is comprised of the inlet part 15, the intermediate part 16, and the outlet part 17 along the flow of the refrigerant, and the mass flow rate per unit capacity is different for each part.
- the flow of the refrigerant is sent from the expansion device 4, branches into the heat transfer tubes 20 and 21, and flows into the heat transfer tubes 20 'and 21', respectively.
- the refrigerant of the heat transfer tubes 20 ′ and 21 ′ passes, for example, through a header (not shown), and is approximately equally branched into the heat transfer tubes 30, 31, 32, 33, 34, 35, and 36, and the heat transfer tubes 30 ′, 31 ′, and 32, respectively.
- ⁇ 6.35 mm may be used at the inlet portion 15 and the intermediate portion 16, and ⁇ 7 mm may be used at the outlet portion 17. Further, the entrance portion 15 may have 2 passes, the intermediate portion 16 may have 7 passes, and the exit portion 17 may have 6 passes.
- FIG. 7 shows the mass flow rate, the dryness, and the saturation temperature difference of each part of each refrigerant calculated by simulation with the standard cooling capacity when the indoor heat exchanger 5 of the present invention in FIG. 6 is used and HFO1234yf is used as the refrigerant. And the cooling capacity.
- the mass flow rate in the pipe of the refrigerant per unit capacity flowing through the inlet portion 15, the intermediate portion 16, and the outlet portion 17 is 0.44 g / mm 2 hW or more and less than 0.50 g / mm 2 hW and 0.14 g, respectively.
- / mm 2 hW more than 0.16 g / mm 2 less than hW becomes less than 0.15 g / mm 2 hW at 0.13 g / mm 2 hW above, the dryness in the cooling standard capacity, respectively 0.215 or 0 Less than .437, 0.437 or more and less than 0.8, 0.8 or more and 1.0 or less.
- the dryness at the time of cooling intermediate period capacity is 0.23 or more and less than 0.408, 0.408 or more and less than 0.645, and 0.645 or more and 1.0 or less.
- the saturation temperature difference is about 9.5 K, and the cooling capacity is 3912 W, which is almost the same as when the R410A refrigerant shown in FIG. 4 is used, and the cooling capacity can be secured.
- FIG. 8 shows a PH diagram under the conditions of FIG. 7 using the indoor heat exchanger 5 of the present invention in FIG. 6 and using HFO1234yf refrigerant.
- a point is the compressor inlet
- B is the compressor discharge
- C is the condenser inlet
- D is the condenser outlet
- E ' is the evaporator inlet
- F is the evaporator outlet.
- point E indicates the indoor heat exchanger inlet when the indoor heat exchanger 5 for R410A is used.
- FIG. 8 shows that when the indoor heat exchanger 5 for R410A is used, the pressure loss is large and the slope of the line from the F point to the E point is large, whereas the indoor heat exchanger 5 of the present invention is When used, it can be seen that the slope from the point F to the point E ′ is gentle. Therefore, an appropriate refrigerant and air temperature can be secured, that is, a heat exchange amount can be secured, and a predetermined cooling capacity can be secured.
- the gas refrigerant that has passed through the connection pipe B13 reaches the heat transfer pipes 40 ′, 41 ′, 42 ′, 43 ′, 44 ′, and 45 ′, and further passes through the heat transfer pipes 40, 41, 42, 43, 44, and 45.
- the heat transfer tubes 30 ′, 31 ′, 32 ′, 33 ′, 34 ′, 35 ′, and 36 ′ are branched substantially evenly through a header (not shown).
- the heat transfer tubes 30, 31, 32, 33, 34, 35, and 36 pass through, for example, a header (not shown), branch substantially evenly, flow into the heat transfer tubes 20 ′ and 21 ′, and enter the heat transfer tubes 20 and 21.
- a header not shown
- the refrigerant is composed of the outlet part 17, the intermediate part 16, and the inlet part 15 along the flow, and has a mass flow rate per unit capacity that is different for each part.
- Mass flow rate per unit capacity of each site was calculated by simulation, 0.120g / mm 2 hW more than 0.121 g / mm 2 less than hW, 0.127g / mm 2 hW more than 0.129 g / mm 2 hW below, the 0.451 g / mm 2 less than hW at 0.446 g / mm 2 hW more.
- the dryness of each of the simulations is 0.408 or more and less than 1.00 at the heating standard capacity, 0 or more and less than 0.408 or 0.00 at the heating standard capacity, and 0.681 or more and less than 1.00 at the heating intermediate capacity. 0.163 or more and less than 0.681, and 0.00 or more and 0.681 or less.
- the air and the refrigerant exchange heat with the blower 18.
- the refrigerant flow and the air flow direction are the same.
- the downstream of the flow direction of the refrigerant in the indoor heat exchanger 5 is the upstream of the air flow formed by the blower 18, that is, the flow direction of the air sent by the blower 18 is opposite to the flow direction of the refrigerant. Therefore, since the average temperature difference is larger than that flowing in the same direction, the efficiency is improved.
- Fig. 9 shows the layout of the parts.
- the indoor heat exchanger 5 When the indoor heat exchanger 5 is configured, an example in which the inlet portion 15, the intermediate portion 16, and the outlet portion 17 are configured in FIG. 9 is shown.
- each part As shown in FIG. 9 (a), each part may be divided and arranged, or as shown in FIG. 9 (b), the three parts may overlap, and the arrangement of each part is not limited to this figure. Absent.
- FIG. 10 shows the calculation results when the indoor heat exchanger 5 of the present invention is used and when the mass flow rate per unit capacity is changed in each of the inlet part 15, the intermediate part 16, and the outlet part 17.
- the case where the indoor heat exchanger 5 of the present invention is used is shown in bold in the center of the table, the cooling standard, the cooling middle, the heating standard and the heating middle capacity are set to 100%, and the period efficiency is set to 100%. it's shown.
- the heating capacity is higher at the mass flow rate per unit capacity of 0.117 g / mm 2 hW at (3) the exit part in FIG. 10, but the heating performance is somewhat lowered as a characteristic of this refrigerant. However, it can be seen that the point is to improve the cooling performance.
- the pipe diameter is determined as a standard, any pipe diameter cannot be selected. Therefore, the pipe diameter and the number of passes are appropriately selected so as to be as close as possible to the mass speed and the dryness of the refrigerant shown in the embodiment.
- HFO1234yf has been described as an example.
- a refrigerant using a hydrofluoroolefin having a double bond between carbon and a carbon as a base component may be used.
- HFO1234ze may be used, and such a refrigerant may be used alone or as a mixed refrigerant containing the refrigerant, for example, a refrigerant mixed with hydrofluorocarbon having no double bond as the working refrigerant.
- a mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf or HFO1234ze) and the hydrofluorocarbon is difluoromethane (HFC32) may be used as the working refrigerant.
- a mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf) and the hydrofluorocarbon is pentafluoroethane (HFC125) may be used as the working refrigerant.
- a three-component mixed refrigerant in which the hydrofluoroolefin is tetrafluoropropene (HFO1234yf) and the hydrofluorocarbon is pentafluoroethane (HFC125) and difluoromethane (HFC32) may be used as the working refrigerant.
- a heat exchanger and an outdoor heat exchanger are a condenser and an evaporator.
- a refrigerant having a small GWP such as HFO1234yf of GWP4.
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- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
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- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
図1は本実施の形態による冷暖房装置の構成図である。 (Embodiment 1)
FIG. 1 is a configuration diagram of an air conditioning apparatus according to the present embodiment.
2 四方弁
3 室外熱交換器
4 絞り装置
5 室内熱交換器
6 単位体積当たりの冷凍能力が小さな冷媒
15 入口部位
16 中間部位
17 出口部位
18 送風装置
19 フィン
20、21、20’、21’、30、31、32、33、34、35、36、
30’、31’、32’、33’、34’、35’、36’、40、41、42、43、44、45、40’、41’、42’、43’、44’、45’ 伝熱管 DESCRIPTION OF SYMBOLS 1
30 ', 31', 32 ', 33', 34 ', 35', 36 ', 40, 41, 42, 43, 44, 45, 40', 41 ', 42', 43 ', 44', 45 ' Heat transfer tube
Claims (10)
- 少なくとも圧縮機、室外熱交換器、絞り装置、及び室内熱交換器を順次接続管で接続して環状の冷媒回路を構成し、前記冷媒回路に封入する冷媒として、R410A冷媒に比べて単位体積当たりの冷凍能力小さな冷媒を用いた冷凍装置であって、
前記室内熱交換器は所定の間隔に並べられた複数のフィンと、前記フィンに略直角に貫通して冷媒が内部を流通する伝熱管を備え、前記伝熱管内部を流れる冷媒の質量流速が三つ以上の異なる部位を備えた事を特徴とする冷凍装置。 At least the compressor, the outdoor heat exchanger, the expansion device, and the indoor heat exchanger are connected in order by a connecting pipe to form an annular refrigerant circuit, and the refrigerant enclosed in the refrigerant circuit is per unit volume as compared with the R410A refrigerant. Refrigeration equipment using a small refrigerant,
The indoor heat exchanger includes a plurality of fins arranged at predetermined intervals, and a heat transfer tube that passes through the fins at a substantially right angle and through which the refrigerant flows, and the mass flow rate of the refrigerant flowing through the heat transfer tube is three. A refrigeration apparatus having two or more different parts. - 請求項1記載の冷凍装置において、前記部位は前記室内熱交換器が蒸発器として機能する場合、冷媒の流れに沿って入口部位、中間部位、出口部位として構成され、前記入口部位、前記中間部位、前記出口部位に流れる単位能力当たりの冷媒の配管内質量流速が、それぞれ0.44g/mm2hW以上で0.50g/mm2hW未満、0.14g/mm2hW以上で0.16g/mm2hW未満、0.13g/mm2hW以上で0.15g/mm2hW未満となる様に構成したことを特徴とする冷凍装置。 2. The refrigeration apparatus according to claim 1, wherein, when the indoor heat exchanger functions as an evaporator, the part is configured as an inlet part, an intermediate part, and an outlet part along a refrigerant flow, and the inlet part and the intermediate part The mass flow rate in the pipe of the refrigerant per unit capacity flowing to the outlet site is 0.44 g / mm 2 hW or more and less than 0.50 g / mm 2 hW, 0.14 g / mm 2 hW or more and 0.16 g / mm, respectively. A refrigeration apparatus configured to be less than mm 2 hW, 0.13 g / mm 2 hW or more and less than 0.15 g / mm 2 hW.
- 請求項1または請求項2記載の前記室内熱交換器において、冷房の標準能力時には前記入口部位、前記中間部位、前記出口部位に流れる冷媒の乾き度が、それぞれ0.215以上で0.437未満、0.437以上で0.8未満、0.8以上で1.0以下となる様に構成したことを特徴とする冷凍装置。 3. The indoor heat exchanger according to claim 1, wherein the dryness of the refrigerant flowing through the inlet portion, the intermediate portion, and the outlet portion is 0.215 or more and less than 0.437, respectively, at a standard capacity of cooling. A refrigeration apparatus configured to be 0.437 or more and less than 0.8 and 0.8 or more and 1.0 or less.
- 請求項1~3記載の何れかの冷凍装置において、前記室内熱交換器が冷房の中間能力時には前記入口部位、前記中間部位、前記出口部位に流れる冷媒の乾き度が、それぞれ0.23以上で0.408未満、0.408以上で0.645未満、0.645以上で1.0以下となる様に構成したことを特徴とする冷凍装置。 The refrigeration apparatus according to any one of claims 1 to 3, wherein when the indoor heat exchanger has an intermediate capacity of cooling, the dryness of the refrigerant flowing through the inlet part, the intermediate part, and the outlet part is 0.23 or more, respectively. A refrigeration apparatus configured to be less than 0.408, 0.408 or more and less than 0.645, or 0.645 or more and 1.0 or less.
- 請求項1~4の何れかに記載の冷凍装置において、前記部位は前記室内熱交換器が凝縮器として機能する場合、前記出口部位、前記中間部位、前記入口部位に流れる単位能力当たりの冷媒の配管内質量流速が、それぞれ0.120g/mm2hW以上で0.121g/mm2hW未満、0.127g/mm2hW以上で0.129g/mm2hW未満、0.446g/mm2hW以上で0.451g/mm2hW未満となる様に構成したことを特徴とする請求項1記載の冷凍装置。 The refrigeration apparatus according to any one of claims 1 to 4, wherein when the indoor heat exchanger functions as a condenser, the part is a refrigerant per unit capacity flowing through the outlet part, the intermediate part, and the inlet part. a mass flow rate piping, respectively 0.120 g / mm 2 hW more than 0.121 g / mm 2 less than hW, 0.129 g / mm 2 less than hW at 0.127 g / mm 2 hW above, 0.446 g / mm 2 hW The refrigeration apparatus according to claim 1, wherein the refrigeration apparatus is configured to be less than 0.451 g / mm 2 hW.
- 請求項1~5の何れかに記載の冷凍装置において、前記室内熱交換器が暖房の標準能力時には前記出口部位、前記中間部位、前記入口部位に流れる冷媒の乾き度が、それぞれ0.408以上で1.00未満、0以上で0.408未満、0.00となる様に構成したことを特徴とする冷凍装置。 6. The refrigeration apparatus according to claim 1, wherein when the indoor heat exchanger has a standard heating capacity, the dryness of the refrigerant flowing through the outlet part, the intermediate part, and the inlet part is 0.408 or more, respectively. The refrigeration apparatus is configured to be less than 1.00, 0 or more and less than 0.408 and 0.00.
- 請求項1~6の何れかに記載の冷凍装置において、前記室内熱交換器が暖房の中間能力時には前記出口部位、前記中間部位、前記入口部位に流れる冷媒の乾き度が、それぞれ0.681以上で1.00未満、0.163以上で0.681未満、0.00以上で0.681以下となる様に構成したことを特徴とする冷凍装置。 The refrigeration apparatus according to any one of claims 1 to 6, wherein when the indoor heat exchanger has an intermediate heating capacity, the dryness of the refrigerant flowing through the outlet part, the intermediate part, and the inlet part is 0.681 or more, respectively. The refrigeration apparatus is configured to be less than 1.00, 0.163 or more and less than 0.681, and 0.00 or more and 0.681 or less.
- 請求項1~請求項7何れかに記載の冷凍装置に四方弁を設けて、前記室外熱交換器、前記室内熱交換器に流れる冷媒の向きを変え冷・暖房を可能とした冷暖房装置。 8. A cooling / heating device provided with a four-way valve in the refrigeration apparatus according to claim 1 to enable cooling / heating by changing the direction of refrigerant flowing in the outdoor heat exchanger and the indoor heat exchanger.
- 請求項1~8の何れかに記載の冷凍装置または冷暖房装置において、前記室内熱交換器に供給する送風装置を備え、前記室内熱交換器が凝縮器として機能する場合、前記室内熱交換器内の冷媒の流れ方向の下流が、前記送風装置が形成する空気流れの上流となっていることを特徴とする冷凍装置または冷暖房装置。 The refrigeration apparatus or cooling / heating apparatus according to any one of claims 1 to 8, further comprising a blower that supplies the indoor heat exchanger, wherein the indoor heat exchanger functions as a condenser. The refrigerant | coolant flow direction downstream is the upstream of the air flow which the said air blower forms, The refrigeration apparatus or the air conditioning apparatus characterized by the above-mentioned.
- 前記冷媒として、炭素と炭素間に2重結合を有するハイドロフルオロオレフィンをベース成分とした冷媒からなる単一冷媒または前記冷媒を含む混合冷媒が充填されたことを特徴とする請求項1から請求項9の何れかに記載の冷凍装置または冷暖房装置。 2. The refrigerant according to claim 1, wherein the refrigerant is filled with a single refrigerant composed of a refrigerant composed of carbon and a hydrofluoroolefin having a double bond between carbons or a mixed refrigerant containing the refrigerant. 10. The refrigeration apparatus or air conditioning apparatus according to any one of 9.
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BR112012029878A BR112012029878A2 (en) | 2010-05-27 | 2011-04-22 | cooling equipment and air conditioner |
CN2011800261631A CN102918338A (en) | 2010-05-27 | 2011-04-22 | Refrigeration device and cooling and heating device |
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WO2013084455A1 (en) * | 2011-12-08 | 2013-06-13 | パナソニック株式会社 | Heat exchanger and air conditioner provided with same |
JP2015140990A (en) * | 2014-01-29 | 2015-08-03 | 日立アプライアンス株式会社 | air conditioner |
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JP6494916B2 (en) * | 2014-03-07 | 2019-04-03 | 三菱重工サーマルシステムズ株式会社 | Heat exchanger and air conditioner using the same |
FR3019637A1 (en) * | 2014-04-02 | 2015-10-09 | Bosch Gmbh Robert | AIR / FLUID EVAPORATOR COMPRISING A HEAT EXCHANGER WITH FINS |
FR3028930B1 (en) * | 2014-11-20 | 2016-12-02 | Air Liquide | COMPACT EXCHANGER FOR CRYOGENIC TRANSPORT IN INDIRECT INJECTION |
CN106091486A (en) * | 2016-07-15 | 2016-11-09 | 珠海格力电器股份有限公司 | Heat exchanger and there is its air-conditioner |
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JPH04186079A (en) * | 1990-11-16 | 1992-07-02 | Hitachi Ltd | Refrigerator |
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WO2013084455A1 (en) * | 2011-12-08 | 2013-06-13 | パナソニック株式会社 | Heat exchanger and air conditioner provided with same |
JPWO2013084455A1 (en) * | 2011-12-08 | 2015-04-27 | パナソニックIpマネジメント株式会社 | Heat exchanger and air conditioner equipped with the same |
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BR112012029878A2 (en) | 2016-08-16 |
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EP2578966B1 (en) | 2020-08-26 |
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