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WO2024257145A1 - Échangeur de chaleur et climatiseur - Google Patents

Échangeur de chaleur et climatiseur Download PDF

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Publication number
WO2024257145A1
WO2024257145A1 PCT/JP2023/021665 JP2023021665W WO2024257145A1 WO 2024257145 A1 WO2024257145 A1 WO 2024257145A1 JP 2023021665 W JP2023021665 W JP 2023021665W WO 2024257145 A1 WO2024257145 A1 WO 2024257145A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
inner tube
tube
distributor
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
PCT/JP2023/021665
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English (en)
Japanese (ja)
Inventor
洋次 尾中
理人 足立
七海 岸田
哲二 七種
暁 八柳
祐基 中尾
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Priority to PCT/JP2023/021665 priority Critical patent/WO2024257145A1/fr
Publication of WO2024257145A1 publication Critical patent/WO2024257145A1/fr
Anticipated expiration legal-status Critical
Pending legal-status Critical Current

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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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • This disclosure relates to a heat exchanger and an air conditioner equipped with a double-pipe refrigerant distributor.
  • a heat exchanger includes a double-pipe refrigerant distributor having an outer pipe and an inner pipe provided with a plurality of orifice holes (hereinafter also referred to as refrigerant outlet holes), and distributes a refrigerant to a plurality of heat transfer pipes by the refrigerant distributor (see, for example, Patent Document 1).
  • the refrigerant distributor disclosed in Patent Document 1 is provided on the inner pipe or the outer pipe, and includes a structure that causes the refrigerant to flow into the inner pipe in a state where a gas-liquid two-phase flow is not yet developed.
  • the refrigerant outlet hole is provided in an angle ⁇ from the lower end of the inner pipe on a vertical line passing through the center of the inner pipe to the position where the refrigerant outlet hole is located, which is in the range of 10 degrees to 80 degrees, and only one refrigerant outlet hole is provided in the vertical cross section of the inner pipe at the position where the refrigerant outlet hole is provided.
  • the optimal angle ⁇ of angle ⁇ satisfies ⁇ Do ⁇ Ds, where ⁇ Do is the liquid level angle when it is assumed that the slip ratio of the refrigerant gas and liquid is 1 and the gas-liquid interface is flat and horizontal, ⁇ Ds is the refrigerant liquid level angle, and As [mm 2 ] is the flow path cross-sectional area of the inner tube, and ⁇ Do is (-0.0408 ⁇ As+74.124) ⁇ 0.62, and ⁇ Ds is (-0.0408 ⁇ As+74.124) ⁇ 1.2.
  • the refrigerant outflow holes are provided in the inner tube corresponding to each gap between adjacent heat transfer tubes.
  • the angle ⁇ of the refrigerant outflow hole can be set to an optimal angle
  • This disclosure has been made in consideration of the above-mentioned circumstances, and aims to provide a heat exchanger and air conditioner that can suppress deterioration of distribution performance caused by fluctuations in refrigerant flow rate and dryness.
  • the heat exchanger disclosed herein is a heat exchanger that includes a plurality of heat transfer tubes and a refrigerant distributor that extends in the horizontal direction and distributes refrigerant to the plurality of heat transfer tubes, and is configured with at least one heat exchanger section in which a structural part is provided upstream or upstream of the refrigerant distributor in the flow direction of the refrigerant when the refrigerant distributor functions as an evaporator.
  • the refrigerant distributor includes an outer tube through which the refrigerant flows and through which the plurality of heat transfer tubes are connected at predetermined intervals, and a refrigerant distributor disposed on the inner periphery of the outer tube through which the refrigerant flows.
  • the inner tube is provided with a plurality of refrigerant outlet holes that allow the refrigerant flowing inside to flow out into the space between the outer tube and the inner tube, and the number of the plurality of refrigerant outlet holes provided in the inner tube satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1), where the number of holes is defined as No and the number of the plurality of heat transfer tubes is defined as Nt, and the structural part causes the state of the refrigerant flowing inside the inner tube to be in an underdeveloped state of gas-liquid two-phase flow when functioning as an evaporator.
  • the air conditioning device disclosed herein is equipped with the above-mentioned heat exchanger.
  • the heat exchanger and air conditioning device disclosed herein are equipped with a refrigerant distributor having an outer tube and an inner tube with multiple refrigerant outlet holes, and a structural part is provided upstream or upstream of the refrigerant distributor in the refrigerant flow direction when the heat exchanger functions as an evaporator, which causes the refrigerant flowing inside the inner tube to be in an underdeveloped gas-liquid two-phase flow state.
  • the number of holes in the multiple refrigerant outlet holes provided in the inner tube satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1).
  • the opening area per refrigerant outlet hole is designed to be larger than in the past, and the liquid surface capture area of each refrigerant outlet hole is expanded, making it possible to suppress a decrease in distribution performance caused by fluctuations in the refrigerant flow rate and dryness.
  • FIG. 2 is a schematic front view of the heat exchanger according to the first embodiment.
  • FIG. 2 is a refrigerant circuit diagram of an air conditioner equipped with the heat exchanger of FIG. 1.
  • 2 is a partial cross-sectional view showing a schematic cross section of the heat exchanger of FIG. 1 taken along line AA.
  • FIG. 2 is a diagram showing the relationship between the refrigerant flow rate and the heat exchanger performance of the heat exchanger of FIG. 1 .
  • FIG. 2 is a partial cross-sectional view showing a schematic cross section of the heat exchanger of FIG. 1 taken along the line BB, illustrating fluctuations in the liquid level of the refrigerant in the inner tube.
  • FIG. 6 is a diagram showing fluctuations in the liquid level of the refrigerant when the inner diameter of the inner tube in the refrigerant distributor of the heat exchanger of FIG. 5 is enlarged.
  • FIG. 2 is a partial cross-sectional view showing a schematic cross section of the heat exchanger of FIG. 1 taken along line BB, showing a liquid surface capture region of the refrigerant outlet hole.
  • FIG. 8 is a diagram showing a liquid surface capture region when the opening diameter of the refrigerant outlet hole in the refrigerant distributor of the heat exchanger of FIG. 7 is enlarged.
  • FIG. 2 is a diagram showing the relationship between the flow path cross-sectional area of the inner tube and the opening diameter of the refrigerant outflow hole, which is particularly expected to have an effect of improving robustness in the heat exchanger of FIG. 2 is a schematic front view of the heat exchanger of FIG. 1 in which the refrigerant outlet hole is longer in the vertical direction than in the horizontal direction.
  • FIG. FIG. 11 is a partially enlarged view of the refrigerant outlet hole of FIG. 10 in an elliptical shape. 11 is a partially enlarged view of the refrigerant outlet hole of FIG. 10 in a rectangular shape.
  • FIG. 11 is a partially enlarged view of the refrigerant outlet hole of FIG. 10 in a shape of a plurality of circles connected in a straight line.
  • FIG. FIG. 6 is a partial cross-sectional view illustrating a first modified example of a refrigerant distributor in the heat exchanger of FIG. 5 .
  • FIG. 6 is a partial cross-sectional view illustrating a second modified example of the refrigerant distributor in the heat exchanger of FIG. 5 .
  • FIG. 11 is a schematic front view of a heat exchanger according to a second embodiment. 17 is a schematic front view showing a first modified example of the structure of the heat exchanger of FIG. 16.
  • FIG. 17 is a schematic front view showing a second modified example of the structure of the heat exchanger of FIG. 16.
  • FIG. FIG. 11 is a schematic diagram of a heat exchanger according to a third embodiment.
  • FIG. 20 is a schematic diagram showing a first modified example of the heat exchanger of FIG. 19 .
  • FIG. 1 is a front schematic diagram of a heat exchanger 3 according to the first embodiment.
  • FIG. 2 is a refrigerant circuit diagram of an air conditioner 100 equipped with the heat exchanger 3 of FIG. 1.
  • FIG. 3 is a partial cross-sectional view showing a cross section of the heat exchanger 3 of FIG. 1 along line A-A.
  • the heat exchanger 3 of FIG. 1 is used in an air conditioner 100 having a refrigerant circuit as shown in FIG. 2.
  • FIG. 1 the flow of the refrigerant when the heat exchanger 3 functions as an evaporator is shown by outline arrows and dashed arrows.
  • FIG. 2 the flow of the refrigerant during cooling operation is shown by solid arrows, and the flow of the refrigerant during heating operation is shown by dashed arrows.
  • the heat exchanger 3 is assumed to be provided in an outdoor unit 10.
  • any refrigerant may be used, but examples of the refrigerant include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixed refrigerant of two or more of these, a mixed refrigerant of any of these with another refrigerant, a mixed refrigerant containing R1132(E), and a mixed refrigerant containing R1123.
  • the refrigerant may be a mixed refrigerant of two or more of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, R459A, R474A, and R479A.
  • the air conditioning device 100 includes an outdoor unit 10 and multiple indoor units 11, 12, and 13.
  • the indoor units 11, 12, and 13 are connected in parallel to one another.
  • a refrigerant circulates inside the outdoor unit 10 and the multiple indoor units 11, 12, and 13.
  • the air conditioning device 100 is a multi-type air conditioning device. Note that the first embodiment does not limit the number of indoor units 11, 12, and 13 connected to the outdoor unit 10.
  • the air conditioning device 100 has a refrigerant circuit in which a compressor 1, a flow path switching device 2 such as a four-way valve, an indoor heat exchanger 6, a pressure reducing device 5 such as an expansion valve, a heat exchanger 3, and an accumulator 8 are connected by refrigerant piping 26 and refrigerant piping 27.
  • the heat exchanger 3 and the indoor heat exchanger 6 exchange heat between the wind generated by the fans 4 and 7 and the refrigerant flowing therein.
  • the configuration of the refrigerant circuit is not limited to the above configuration.
  • the flow path switching device 2 may also be configured with, for example, a two-way valve and a three-way valve.
  • the refrigerant compressed in the compressor 1 flows out of the outdoor unit 10 through the flow switching device 2 and flows into the indoor units 11, 12, and 13.
  • the refrigerant that flows into the indoor units 11, 12, and 13 exchanges heat with the wind generated by the fan 7 in the indoor heat exchanger 6, and is then depressurized by the pressure reducing device 5.
  • the refrigerant after being depressurized by the pressure reducing device 5 of the indoor units 11, 12, and 13 flows out of the indoor units 11, 12, and 13 through the refrigerant pipe 27 connecting the pressure reducing device 5 and the heat exchanger 3, and flows into the heat exchanger 3 of the outdoor unit 10.
  • the refrigerant that flows into the heat exchanger 3 of the outdoor unit 10 exchanges heat with the wind generated by the fan 4, then flows out of the refrigerant pipe 26 connecting the heat exchanger 3 and the flow switching device 2, and is sucked into the compressor 1 through the accumulator 8. During heating operation, the above cycle is repeated.
  • the refrigerant compressed in the compressor 1 flows into the heat exchanger 3 from the refrigerant pipe 26 connecting the flow path switching device 2 and the heat exchanger 3 via the flow path switching device 2.
  • the refrigerant that flows into the heat exchanger 3 exchanges heat with the wind generated by the fan 4, then flows out of the outdoor unit 10 via the refrigerant pipe 27 connecting the heat exchanger 3 and the pressure reducing device 5, and flows into the indoor units 11, 12, and 13.
  • the refrigerant that flows into the indoor units 11, 12, and 13 is decompressed by the pressure reducing device 5, and then exchanges heat with the wind generated by the fan 7 in the indoor heat exchanger 6, and flows out of the indoor units 11, 12, and 13.
  • the refrigerant that flows out of the indoor units 11, 12, and 13 flows into the outdoor unit 10, and is sucked into the compressor 1 via the flow path switching device 2 and the accumulator 8.
  • the above cycle is repeated.
  • the heat exchanger 3 mounted in the outdoor unit 10 of the air conditioning apparatus 100 exchanges heat between the refrigerant and the wind (outside air) generated by the fan 4.
  • the heat exchanger 3 is disposed below the fan 4.
  • the heat exchanger 3 is, for example, a corrugated fin type heat exchanger.
  • the heat exchanger 3 has a refrigerant distributor 30, a plurality of heat transfer tubes 31, and a plurality of fins 32.
  • the heat transfer tubes 31 are, for example, flat tubes.
  • a heat exchanger consisting of two connected heat exchangers 3, each having a refrigerant distributor 30, a plurality of heat transfer tubes 31, and a plurality of fins 32, may be mounted on the outdoor unit 10.
  • the heat exchanger may be composed of one heat exchanger section (heat exchanger 3), or may have two or more heat exchanger sections (heat exchangers 3).
  • the refrigerant distributor 30 is arranged horizontally (i.e., in the direction of arrow X).
  • a plurality of heat transfer tubes 31 are spaced apart, and one end of each is inserted into the refrigerant distributor 30.
  • the fins 32 are attached to the heat transfer tubes 31 and are provided between the heat transfer tubes 31. The fins 32 transfer heat to the heat transfer tubes 31.
  • the heat exchanger 3 has a gas header 40 arranged horizontally (i.e., in the direction of the arrow X) above the refrigerant distributor 30.
  • the upper ends of a plurality of heat transfer tubes 31 are connected to the gas header 40.
  • a refrigerant outlet pipe that is connected to the refrigerant piping 26 of the refrigerant circuit is provided at one end of the gas header 40 in the extension direction (direction of the arrow X).
  • the refrigerant outlet pipe has a smaller diameter than the diameter of the gas header 40.
  • the refrigerant distributor 30 has a double-pipe structure including an inner pipe 33 and an outer pipe 34.
  • a plurality of heat transfer pipes 31 are connected to the outer pipe 34 in the extension direction of the outer pipe 34.
  • the refrigerant distributor 30 constitutes the lower part of the heat exchanger 3, and the lower ends of the plurality of heat transfer pipes 31 are connected to the refrigerant distributor 30.
  • the inner pipe 33 is disposed inside the outer pipe 34, and its extension direction is kept horizontal.
  • the inner pipe 33 has refrigerant outflow holes 35, also called orifices, formed at intervals in the extension direction of the inner pipe 33.
  • each refrigerant outlet hole 35 is circular.
  • the refrigerant outflow hole 35 may be formed in the inner tube 33 directly below the heat transfer tube 31 instead of in the portion below the gap G between the heat transfer tubes 31.
  • the outer tube 34 has a rectangular cross-sectional shape perpendicular to its extension direction (vertically elongated rectangle in FIG. 3), and the inner tube 33 has a circular cross-sectional shape perpendicular to its extension direction.
  • the multiple refrigerant outlet holes 35 are spaced apart in the extension direction of the inner tube 33 so that the number of holes per vertical cross-section perpendicular to the extension direction of the inner tube 33 is one or less.
  • the inner tube 33 extends in the extension direction of the outer tube 34 beyond the region where the multiple heat transfer tubes 31 are connected to the outer tube 34.
  • One end (left end) of the inner tube 33 in the extension direction is open, and the other end (right end) of the inner tube 33 in the extension direction is sealed by a cap 36.
  • the outer tube 34 extends further than the inner tube 33, and one and the other ends of the outer tube 34 in the extension direction are sealed. Note that any sealing structure may be used to seal the end (right end) of the inner tube 33 in the extension direction, and instead of providing the cap 36, a configuration in which the end (end) of the inner tube 33 in the extension direction is crushed and sealed may be used.
  • the inner tube 33 may be configured to be sealed by contacting the other end (right end) of the inner tube 33 in the extension direction with the other end (right end) of the outer tube 34 in the extension direction.
  • the right end of the inner tube 33 in the extension direction may be open, just like the left end.
  • An opening (not shown) is formed on the upper surface of the outer tube 34, and a refrigerant inlet tube 63 extending in a straight line is connected to this opening.
  • the refrigerant inlet tube 63 is connected to the refrigerant piping 27 (see FIG. 2) of the refrigerant circuit.
  • refrigerant including liquid refrigerant flows into one end of the outer tube 34 via the refrigerant inlet tube 63, as shown by the white arrow in FIG. 1.
  • the refrigerant inlet pipe 63 may be connected to the underside of the outer pipe 34, or to the front or rear of the outer pipe 34.
  • the refrigerant distributor 30 is provided on both sides of the region where the heat transfer tubes 31 are connected in the extension direction of the outer tube 34, and includes a first partition 61 and a second partition 62 that divide the space inside the outer tube 34.
  • the first partition 61 and the second partition 62 are each composed of a plate-like member with a hole (not shown) in which the inner tube 33 is placed, and divide the space inside the outer tube 34 horizontally between the inner circumference of the outer tube 34 and the outer circumference of the inner tube 33.
  • the first partition 61 and the second partition 62 also have the function of supporting the inner tube 33 and determining the position of the inner tube 33 inside the outer tube 34.
  • the first partition 61 is disposed between the refrigerant inlet tube 63 and the heat transfer tube 31 closest to the refrigerant inlet tube 63 in the extension direction of the outer tube 34.
  • the second partition 62 is disposed between the end of the outer tube 34 farthest from the refrigerant inlet tube 63 in the extension direction and the heat transfer tube 31 farthest from the refrigerant inlet tube 63 in the extension direction of the outer tube 34.
  • the inside of the outer pipe section 34a on the side of the refrigerant inlet pipe 63 from the first partition 61 (left side in FIG. 1) of the outer pipe 34 constitutes the mixing space S1.
  • the refrigerant flows into the inside of the outer pipe section 34b on the side of the outer pipe 34 farther from the refrigerant inlet pipe 63 than the second partition 62 (right side in FIG. 1) from the other end (right end) in the extension direction of the inner pipe 33.
  • This outer pipe section 34b is separated by the second partition 62 from the space outside the inner pipe 33 in the section between the second partition 62 and the first partition 61 (i.e., the ejection space between the inner pipe 33 and the outer pipe 34 through which the refrigerant flowing out through the multiple refrigerant outlet holes 35 of the inner pipe 33 flows). Therefore, the refrigerant that flows into the space inside the outer pipe section 34b does not flow directly into the ejection space.
  • the refrigerant is prevented from flowing into the outer tube portion 34b.
  • the refrigerant flows from the refrigerant piping 27 (see FIG. 2) of the refrigerant circuit into the mixing space S1 through the refrigerant inlet pipe 63.
  • the refrigerant that flows into the mixing space S1 is mixed with gas and liquid in the mixing space S1, and flows into the inner tube 33 from the left end of the inner tube 33 in an underdeveloped gas-liquid two-phase flow state.
  • the refrigerant that flows into the inner tube 33 from the left end of the inner tube 33 flows in the extension direction toward the right end of the inner tube 33. At this time, the refrigerant flows into the space between the inner tube 33 and the outer tube 34 through a plurality of refrigerant outlet holes 35 provided at regular intervals in the extension direction of the inner tube 33.
  • the refrigerant that flows into the space between the inner tube 33 and the outer tube 34 is distributed to a plurality of heat transfer tubes 31 connected to the outer tube 34.
  • the refrigerant distributed to the multiple heat transfer tubes 31 flows from the lower end to the upper end inside each heat transfer tube 31, and at this time, evaporates and gasifies by exchanging heat with air (outside air) passing through gaps G between the heat transfer tubes 31.
  • the refrigerant gasified in each of the multiple heat transfer tubes 31 joins together in the gas header 40 and flows in the extension direction, and then flows out of the heat exchanger 3 through a refrigerant outflow pipe (not shown) into the refrigerant piping 26 (see FIG. 2 ) of the refrigerant circuit.
  • the refrigerant flow has a structural part C upstream or upstream of the refrigerant distributor 30, which causes a gas-liquid two-phase flow to be underdeveloped.
  • Structural part C particularly causes the state of the refrigerant flowing inside the inner tube 33 to be in a state where a gas-liquid two-phase flow is underdeveloped.
  • "a state where a gas-liquid two-phase flow is underdeveloped” means that the refrigerant flowing inside the inner tube 33 is not in a gas-liquid two-phase flow, such as a stratified flow.
  • structural part C where the gas-liquid two-phase flow is underdeveloped is the mixing space S1 provided upstream of the refrigerant distributor 30.
  • the refrigerant distributor 30 is configured to satisfy A2>As, where A2 is the flow path cross-sectional area of the mixing space S1 and As is the flow path cross-sectional area of the inner pipe 33.
  • the vertical liquid phase distribution (liquid level) inside the refrigerant distributor 30 will not be as intended, and if the opening diameter ⁇ o of the refrigerant outlet hole 35 is small, the distribution performance will decrease.
  • the angle ⁇ at which the refrigerant outflow hole 35 is provided in the inner tube 33 is set so that good refrigerant distribution can be obtained even when structural part C, which keeps the gas-liquid two-phase flow underdeveloped, is provided upstream or downstream of the refrigerant distributor 30.
  • the angle ⁇ of the refrigerant outflow hole 35 is defined as the angle seen from the center of the inner tube 33 from the lower end of the inner tube 33 to the center of the refrigerant outflow hole 35 on a vertical line passing through the center of the inner tube 33.
  • the liquid level angle is defined as ⁇ Do and the liquid level angle of the refrigerant when it is assumed that the slip ratio of the refrigerant gas and liquid is 1 and the gas-liquid interface is flat and horizontal, and the refrigerant outflow hole 35 is defined as ⁇ Ds, the refrigerant outflow hole 35 is provided so that the angle ⁇ satisfies ⁇ Do ⁇ Ds.
  • the heat exchanger 3 in FIG. 1 functions in heating operation under low-temperature conditions
  • the progress of frost on the surfaces of the fins 32 reduces the amount of air passing through the gaps G between the heat transfer tubes 31, causing the refrigerant pressure to drop, and thus reducing the heating capacity (reducing the refrigerant flow rate).
  • the refrigerant flow rate and dryness at the refrigerant inlet of the heat exchanger 3 gradually change, causing greater fluctuations in the vertical liquid phase distribution (liquid level) inside the refrigerant distributor 30.
  • the liquid phase distribution may not be in a position suitable for the refrigerant outlet holes 35, and distribution performance may decrease, resulting in a significant decrease in heating capacity.
  • the optimal number of refrigerant outlet holes 35 provided in the inner tube 33 of the refrigerant distributor 30 is specified based on the number of heat transfer tubes 31. Specifically, as shown in FIG. 1, the number No of refrigerant outlet holes 35 provided in the inner tube 33 in the refrigerant distributor 30 is less than the number Nt of heat transfer tubes 31 connected to the outer tube 34, and is set so as to satisfy the following formula (1).
  • pressure is adjusted by arranging one refrigerant outlet hole 35 between each heat transfer tube 31 in the inner tube 33, for example, but in the present disclosure, the number No of the refrigerant outlet holes 35 is made smaller than that (i.e., (Nt-1)).
  • Nt-1 the number of the refrigerant outlet holes 35
  • eight heat transfer tubes 31 are connected to the outer tube 34, and three refrigerant outlet holes 35 are provided in the inner tube 33.
  • the opening area of the multiple refrigerant outlet holes 35 in the refrigerant distributor 30 is determined based on the pressure loss balance. Therefore, when the number No of the refrigerant outlet holes 35 is reduced, the opening area per refrigerant outlet hole 35 (for example, the opening diameter ⁇ o) is designed to be larger.
  • a refrigerant outflow pipe (not shown) is provided at the left end of the gas header 40, and the refrigerant flows into the heat exchanger 3 from the left end of the refrigerant distributor 30, is distributed to the multiple heat transfer tubes 31, and flows out of the heat exchanger 3 from the left end of the gas header 40.
  • the path P1 has a shorter flow distance and is easier for the refrigerant to flow.
  • the refrigerant distributor 30 in the heat exchanger 3 and configuring it so that the refrigerant is distributed through the multiple refrigerant outflow holes 35, flow resistance is applied, and the influence of the flow distance is relatively reduced. This reduces the difference between the refrigerant flow rate in the shortest path P1 and the refrigerant flow rate in the longest path P2.
  • the opening area of the multiple refrigerant outflow holes 35 is designed to create a certain amount of pressure loss in order to adjust the flow resistance balance (pressure loss balance).
  • FIG. 4 is a diagram showing the relationship between the refrigerant flow rate and the heat exchanger performance of the heat exchanger 3 in FIG. 1.
  • the horizontal axis represents the refrigerant flow rate
  • the vertical axis represents the heat exchanger performance.
  • the number of holes No of the refrigerant outlet holes 35 is up to about (Nt-1)/6, it is possible to maintain distribution performance while suppressing deterioration of heat exchanger performance.
  • the two-dot chain line in Figure 4 if the number of holes No of the refrigerant outlet holes 35 is less than (Nt-1)/7, distribution loss occurs in some of the heat transfer tubes 31 that are farther away from the refrigerant outlet holes 35 among the multiple heat transfer tubes 31, and proper distribution is not possible, resulting in a decrease in heat exchanger performance. Therefore, in the heat exchanger 3 disclosed herein, the lower limit of the number of holes No of the refrigerant outlet holes 35 is set to (Nt-1)/6, taking distribution loss into consideration.
  • FIG. 5 is a partial cross-sectional view showing a cross section of the heat exchanger 3 of FIG. 1 along B-B, and shows the liquid level fluctuation AL of the refrigerant in the inner tube 33.
  • FIG. 6 is a diagram showing the liquid level fluctuation AL of the refrigerant when the inner diameter Di of the inner tube 33 in the refrigerant distributor 30 of the heat exchanger 3 of FIG. 5 is enlarged.
  • FIG. 7 is a partial cross-sectional view showing a cross section of the heat exchanger 3 of FIG. 1 along B-B, and shows the liquid level capture region RL of the refrigerant outlet hole 35.
  • FIG. 6 is a diagram showing the liquid level fluctuation AL of the refrigerant when the inner diameter Di of the inner tube 33 in the refrigerant distributor 30 of the heat exchanger 3 of FIG. 5 is enlarged.
  • FIG. 7 is a partial cross-sectional view showing a cross section of the heat exchanger 3 of FIG. 1 along B-B, and shows the liquid level capture region
  • FIG. 8 is a diagram showing the liquid level capture region RL when the opening diameter ⁇ o of the refrigerant outlet hole 35 in the refrigerant distributor 30 of the heat exchanger 3 of FIG. 7 is enlarged.
  • FIG. 9 is a diagram showing the relationship between the flow path cross-sectional area As of the inner tube 33 and the opening diameter ⁇ o of the refrigerant outlet hole 35, which is particularly expected to improve the robustness of the heat exchanger 3 of FIG. 1.
  • the horizontal axis represents the flow passage cross-sectional area As [mm 2 ] of the inner pipe 33
  • the vertical axis represents the opening diameter ⁇ o [mm] of the refrigerant outlet hole 35 formed in the inner pipe 33 .
  • the liquid surface capture region RL of the refrigerant outlet hole 35 when the opening diameter ⁇ o of the refrigerant outlet hole 35 provided in the inner tube 33 is enlarged, the liquid surface capture region RL of the refrigerant outlet hole 35 also becomes larger.
  • the liquid surface capture region RL is the region that is on the liquid surface or liquid phase of the refrigerant in the refrigerant outlet hole 35, and is defined as the vertical width of the opening edge of the refrigerant outlet hole 35 on the inner surface of the inner tube 33.
  • the liquid level capture area RL becomes larger, and, as explained with reference to Figures 5 and 6, by enlarging the inner diameter Di of the inner tube 33, the liquid level fluctuation AL of the refrigerant in the inner tube 33 itself can be reduced. Therefore, not only when the flow pattern differs between the diagram and the actual state, but also during heating operation under low-temperature conditions with large fluctuations in the refrigerant flow rate and dryness, it is possible to suppress the deterioration of distribution performance and the deterioration of heating capacity.
  • the opening diameter ⁇ o of the refrigerant outlet holes 35 is larger than 144.71 ⁇ As -1.25 as shown in Fig. 9.
  • the opening diameter ⁇ o of the refrigerant outlet holes 35 satisfies the condition 144.71 ⁇ As -1.25 ⁇ o ⁇ 1.1287 ⁇ As0.5 .
  • the opening diameter ⁇ o of the refrigerant outflow hole 35 is largely determined by the pressure loss balance, so the adjustment range of the opening diameter ⁇ o is limited.
  • the flow path cross-sectional area As by the inner diameter Di of the inner tube 33 it is possible to further improve robustness. Also, if the inner diameter Di of the inner tube 33 is increased, the opening diameter ⁇ o of the refrigerant outflow hole 35 can be made smaller even if the same robustness is obtained.
  • the shape of the refrigerant outlet hole 35 is not limited to the circular shape described above, and may be non-circular.
  • Fig. 10 is a schematic front view of the heat exchanger 3 in Fig. 1 in which the refrigerant outlet hole 35 is longer in the vertical direction (arrow Z direction) than in the horizontal direction (arrow X direction).
  • Fig. 11 is a partially enlarged view of the refrigerant outlet hole 35 in Fig. 10 in which the shape is elliptical.
  • Fig. 12 is a partially enlarged view of the refrigerant outlet hole 35 in Fig. 10 in which the shape is rectangular.
  • Fig. 13 is a partially enlarged view of the refrigerant outlet hole 35 in Fig. 10 in which the shape is a plurality of circles connected in a straight line.
  • the refrigerant outlet hole 35 provided in the inner tube 33 has an elongated shape with a larger dimension in the vertical direction (arrow Z direction) than in the extension direction (arrow X direction) of the inner tube 33.
  • the shape of the refrigerant outlet hole 35 may be a vertically elongated ellipse as shown in FIG. 10 and FIG. 11, a vertically elongated rectangle as shown in FIG. 12, or a shape in which multiple circles are linearly connected in the vertical direction as shown in FIG. 13.
  • the liquid surface capture region RL is expanded even when the opening area per refrigerant outlet hole 35 is the same, compared to a shape with the same vertical and horizontal dimensions such as a circle, and the robustness of the refrigerant distribution is improved.
  • the cross-sectional shapes of the outer tube 34 and the inner tube 33 of the refrigerant distributor 30 are not limited to those shown in Figures 3 and 5. Two modified examples are shown below.
  • FIG. 14 is a partial cross-sectional view showing a first modified example of the refrigerant distributor 30 in the heat exchanger 3 in FIG. 5.
  • the outer tube 134 has a horizontally long rectangular cross-sectional shape perpendicular to its extension direction
  • the inner tube 133 has a horizontally long rectangular cross-sectional shape perpendicular to its extension direction.
  • the inner tube 233 has a cross-sectional shape perpendicular to its extension direction that is a downwardly convex D-shape.
  • the inner tube 233 has an inner tube upper surface 233a that faces the lower ends of the heat transfer tubes 31 and is flat, an inner tube lower surface 233d that is curved and convex downward, and an inner tube front surface 233b that connects the front edge of the inner tube upper surface 233a to the front edge of the inner tube lower surface 233d and an inner tube rear surface 233c that connects the rear edge of the inner tube upper surface 233a to the rear edge of the inner tube lower surface 233d are each flat.
  • the inner tube lower surface 233d has a cross-sectional shape that is, for example, an arc-shaped.
  • the inner tube 233 is formed so that its cross-sectional shape perpendicular to its extension direction is elongated, with the dimension in the front-to-back direction (arrow Y direction) being greater than the dimension in the vertical direction (arrow Z direction).
  • the inner tube 233 is composed of a D-shaped tube that is wide in the front-to-back direction (arrow Y direction).
  • the outer tube 234 has a cross-sectional shape perpendicular to its extension direction that is a downwardly convex D-shape.
  • the outer tube 234 has a flat outer tube upper surface 234a to which the lower ends of the multiple heat transfer tubes 31 are connected, and an outer tube lower surface 234d that is a downwardly convex curved surface.
  • the outer tube 234 has a cross-sectional shape perpendicular to its extension direction that is elongated such that the dimension in the vertical direction (arrow Z direction) is greater than the dimension in the front-to-rear direction (arrow Y direction).
  • the inner tubes 133, 233 have a horizontally elongated cross-sectional shape perpendicular to their extension direction, with the dimension in the front-to-back direction (arrow Y direction) being greater than the dimension in the vertical direction (arrow Z direction).
  • the inner tubes 133, 233 have a horizontally elongated cross-sectional shape, the liquid level fluctuation AL (see FIG.
  • the heat exchanger 3 is a heat exchanger 3 including a plurality of heat transfer tubes 31 and a refrigerant distributor 30 extending in the horizontal direction (arrow X direction) and distributing a refrigerant to the plurality of heat transfer tubes 31, and including at least one heat exchanger section in which a structural section C in which a gas-liquid two-phase flow is underdeveloped is provided upstream or upstream of the refrigerant distributor 30 in the refrigerant flow direction when functioning as an evaporator.
  • the refrigerant distributor 30 has an outer tube 34 through which the refrigerant flows and to which the plurality of heat transfer tubes 31 are connected at predetermined intervals, and an inner tube 33 through which the refrigerant flows and which is disposed on the inner periphery of the outer tube 34.
  • the inner tube 33 is provided with a plurality of refrigerant outlet holes 35 that allow the refrigerant flowing therein to flow out into the space between the outer tube 34 and the inner tube 33.
  • the number of refrigerant outlet holes 35 provided in the inner tube 33 satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1), where No is the number of holes and Nt is the number of heat transfer tubes 31.
  • Structural part C makes the state of the refrigerant flowing inside the inner tube 33 a state in which gas-liquid two-phase flow is underdeveloped when the heat exchanger 3 functions as an evaporator.
  • the heat exchanger 3 is equipped with a refrigerant distributor 30 having an outer tube 34 and an inner tube 33 with multiple refrigerant outlet holes 35, and a structural part C is provided upstream or at the upstream portion of the refrigerant distributor 30, which causes the refrigerant flowing inside the inner tube 33 to be in an underdeveloped gas-liquid two-phase flow state.
  • the number No of the multiple refrigerant outlet holes 35 provided in the inner tube 33 satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1).
  • the opening area per refrigerant outlet hole 35 is designed to be larger than in the past, and the liquid surface capture region RL of each refrigerant outlet hole 35 is expanded, making it possible to suppress a decrease in distribution performance caused by fluctuations in the refrigerant flow rate and dryness.
  • the multiple refrigerant outlet holes 35 are arranged in the extension direction of the inner tube 33 so that the number of holes per vertical cross section perpendicular to the extension direction (arrow X direction) of the inner tube 33 is one or less. In this way, by dispersing the refrigerant outlet holes 35 in the extension direction of the inner tube 33, the refrigerant is distributed more evenly to the multiple heat transfer tubes 31 even when the number of holes No of the multiple refrigerant outlet holes 35 provided in the inner tube 33 is limited.
  • the opening diameter of each of the plurality of refrigerant outflow holes 35 satisfies 144.71 ⁇ As ⁇ 1.25 ⁇ ⁇ o ⁇ 1.1287 ⁇ As 0.5 . This makes it possible to achieve a balance between the effect of improving the robustness of refrigerant distribution against fluctuations in the refrigerant flow rate and dryness fraction, and the like, and the suppression of deterioration in the heat exchanger performance.
  • each of the multiple refrigerant outlet holes 35 has an elongated shape in which the vertical dimension (arrow Z direction) is greater than the horizontal dimension (arrow X direction).
  • the vertical cross-sectional shape perpendicular to the extension direction of the inner tubes 133, 233 is a horizontally elongated shape in which the dimension in the horizontal direction perpendicular to the extension direction (front-to-back direction, arrow Y direction) is greater than the dimension in the vertical direction (arrow Z direction).
  • the inner tubes 133, 233 have a horizontally elongated cross-sectional shape, the liquid level fluctuation AL (see Figure 6) of the refrigerant in the inner tubes 133, 233 in the vertical direction is reduced, improving the robustness of the refrigerant distribution.
  • the inner pipe 233 may also be made of a wide D-shaped pipe whose dimension in the horizontal direction perpendicular to the extension direction (front-to-back direction, arrow Y direction) is greater than its dimension in the vertical direction.
  • a D-shaped pipe as the inner pipe 233 allows the flow path cross-sectional area As of the inner pipe 233 to be made larger, which in turn reduces the refrigerant liquid level fluctuation AL, which is even better.
  • structural part C is a mixing space S1 provided in the outer tube 34 of the refrigerant distributor 30.
  • the deterioration of refrigerant distribution is suppressed by limiting the number of holes No of the refrigerant outflow holes 35.
  • the heat exchanger 3 also has a sealing structure that seals the end (right end) of the inner tube 33 in the extension direction.
  • the sealing structure is either a crushed end of the inner tube 33 itself or a cap 36 that covers the end.
  • the air conditioning device 100 also includes the above-mentioned heat exchanger 3. As a result, the air conditioning device 100 suppresses a decrease in the distribution performance of the heat exchanger 3 even during operation with large fluctuations in the refrigerant flow rate and dryness, such as heating operation under low-temperature conditions, thereby suppressing a decrease in heating capacity.
  • FIG. 16 is a schematic front view of a heat exchanger 303 according to embodiment 2.
  • the configurations of the refrigerant distributor 330 and the structural portion C of the heat exchanger 303 are different from those in embodiment 1.
  • the configuration of the heat exchanger 303 of embodiment 2 will be described with reference to Fig. 16. Note that the same components as those in embodiment 1 are denoted by the same reference numerals and description thereof will be omitted.
  • the inner pipe 333 is housed in the outer pipe 334, and the side connected to the refrigerant pipe 27 (see FIG. 2) extends beyond the end 334e of the outer pipe 334.
  • the extended portion of the inner pipe 333 is a linear inlet portion 362, which serves as an inlet portion for the refrigerant flowing into the outer pipe 334.
  • the end 334e of the outer pipe 334 has a through hole (not shown) in which the inner pipe 333 is disposed.
  • the heat exchanger 303 functions as an evaporator
  • the inner pipe 333 is supported by the end 334e of the outer pipe 334 on the upstream side of the refrigerant distributor 330 in the refrigerant flow, so the first partition 61 of the first embodiment can be omitted.
  • the inner diameter of the inlet section 362 i.e. the inner diameter Di of the inner tube 333
  • the length of the inlet section 362 in the extension direction of the inner tube 333 arrow X direction
  • L ⁇ 20 x Di many of the flow pattern diagrams used to estimate the flow pattern of a refrigerant represent a state in which the gas-liquid flow is fully developed, in other words, a flow pattern when there is a sufficient run-up distance.
  • the length L of the linear inlet section 362 is L ⁇ 20 x Di, and there is not a sufficient run-up distance upstream of the inner tube 333.
  • the inlet section 362, which is an extended portion of the inner pipe 333, is the structural part C where the gas-liquid two-phase flow is underdeveloped. That is, in the second embodiment, the structural part C is the inlet section 362 provided upstream of the refrigerant distributor 330.
  • the refrigerant that flows through such an inlet section 362 flows into the inner pipe 333 in the outer pipe 334 with the gas-liquid two-phase flow underdeveloped. Then, the refrigerant in the underdeveloped gas-liquid two-phase flow passes through the multiple refrigerant outlet holes 35 from the inner pipe 333 and flows out into the space between the outer pipe 334 and the inner pipe 333.
  • the refrigerant that flows out into the space between the outer pipe 334 and the inner pipe 333 passes through the multiple heat transfer pipes 31 and flows into the gas header 40.
  • the refrigerant that flows into the gas header 40 flows to the right in the extension direction inside the gas header 40 and flows out into the refrigerant piping 26 of the refrigerant circuit through the refrigerant outlet pipe 41 provided at the right end of the gas header 40.
  • FIG. 17 is a front schematic diagram showing a first modified example of the structural part C of the heat exchanger 303 of FIG. 16.
  • the extended part of the inner tube 333a is a bent pipe that is bent in an L shape.
  • the extended part of the inner tube 333a has a straight inlet part 337a that extends horizontally from the part of the inner tube 333a that is disposed in the outer tube 334, which is the same direction, and an extension part 338 that extends upward from the inlet part 337a.
  • the straight inlet part 337a of the extended part of the inner tube 333a becomes the run-up part of the refrigerant that flows into the outer tube 334.
  • the length L of the inlet part 337a is L ⁇ 20 ⁇ Di.
  • the extension 338 of the extended portion of the inner pipe 333a may be a curved pipe.
  • the extension 338 may extend downward from the inlet 337a, or may extend forward or backward.
  • FIG. 18 is a schematic front view showing a second modified example of the structural part C of the heat exchanger 303 of FIG. 16.
  • a valve 339 is provided in the extended part of the inner tube 333b.
  • the valve 339 adjusts the dryness of the refrigerant in the inner tube 333b.
  • the extended part of the inner tube 333b is entirely linear, extending in the horizontal direction, which is the same direction as the part of the inner tube 333a that is disposed in the outer tube 334.
  • the inlet part 337b on the outer tube 334 side of the valve 339 becomes the run-up part for the refrigerant flowing into the outer tube 334.
  • the length L of this inlet part 337b is L ⁇ 20 ⁇ Di.
  • the gas-liquid two-phase flow does not develop sufficiently upstream of the inner pipes 333a, 333b, so that the gas-liquid two-phase flow flows into the inner pipes 333a, 333b in the outer pipe 334 in an underdeveloped state.
  • the heat exchanger 303 includes a refrigerant distributor 330 having an outer pipe 334 and an inner pipe 333 with multiple refrigerant outlet holes 35, as in the first embodiment, and a structural part C is provided upstream of the refrigerant distributor 330, which causes the refrigerant flowing inside the inner pipe 333 to be in an underdeveloped gas-liquid two-phase flow state.
  • the number No of the multiple refrigerant outlet holes 35 provided in the inner pipe 333 satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1).
  • the structural part C is an inlet section 337 that extends linearly from the inner tube 333 of the refrigerant distributor 330 to the outside of the outer tube 334, and satisfies L ⁇ 20 x Di, where Di is the inner diameter of the inner tube 333 and L is the length of the inlet section 337.
  • FIG. 19 is a schematic diagram of a heat exchanger 403 according to the third embodiment.
  • the third embodiment is different from the first and second embodiments in that the heat exchanger 403 has a plurality of heat exchanger parts 403a and 403b.
  • the flow direction of the air supplied to the heat exchanger part 403a and the flow direction of the air supplied to the heat exchanger part 403b are indicated by white arrows.
  • the configuration of the heat exchanger 403 according to the third embodiment will be described with reference to FIG. 1 and FIG. 2.
  • the configurations of the heat exchanger part 403a and the heat exchanger part 403b are assumed to be the same as the configuration of the heat exchanger 3 according to the first embodiment. That is, each of the heat exchanger part 403a and the heat exchanger part 403b includes a refrigerant distributor 30 having a liquid level fluctuation resistance.
  • the refrigerant inlet pipe 463a of the heat exchanger section 403a and the refrigerant inlet pipe 463b of the heat exchanger section 403b are connected to the refrigerant piping 27 (see FIG. 2) of the refrigerant circuit via a connecting pipe 463c.
  • the heat exchanger 403 functions as an evaporator
  • the refrigerant from the refrigerant piping 27 flows through the connecting pipe 463c, branches into two refrigerant inlet pipes 463a and 463b at the upstream branch section 463d, and flows into the heat exchanger section 403a and the heat exchanger section 403b, respectively.
  • the heat exchanger section 403a and the heat exchanger section 403b each have a plurality of heat transfer tubes 31, a plurality of fins 32, and a refrigerant distributor 30 (see FIG. 1).
  • the heat exchanger section 403a and the heat exchanger section 403b have different air volumes, for example, depending on their arrangement.
  • the refrigerant from the refrigerant pipe 27 is branched at the upstream branch section 463d, there may be variations in the refrigerant flow rate or dryness. Therefore, there is a concern that the influence of these variations may cause a deterioration in refrigerant distribution.
  • each of the heat exchanger section 403a and the heat exchanger section 403b is equipped with a refrigerant distributor 30 (see FIG. 1) that has a higher liquid level fluctuation resistance than the conventional one, so that the deterioration of refrigerant distribution is suppressed. This also makes it possible to suppress a decrease in heat exchange efficiency.
  • FIG. 20 is a schematic diagram showing a first modified example of the heat exchanger 403 of FIG. 19.
  • the heat exchanger 503 of the first modified example has heat exchanger section 503a and heat exchanger section 503b, which have different volumes.
  • the flow direction of the refrigerant branched to heat exchanger section 503a and the flow direction of the refrigerant branched to heat exchanger section 503b are respectively indicated by white arrows.
  • the configurations of heat exchanger section 503a and heat exchanger section 503b are assumed to be the same as the configuration of heat exchanger 3 of embodiment 1, except for the difference in volume.
  • the refrigerant inlet pipe 563a of the heat exchanger section 503a and the refrigerant inlet pipe 563b of the heat exchanger section 503b are connected to the refrigerant piping 27 (see FIG. 2) of the refrigerant circuit via a connecting pipe 563c.
  • a flow rate adjustment valve 564 is provided in the refrigerant inlet pipe 563b of the heat exchanger section 503b.
  • the opening degree of the flow rate adjustment valve 564 is controlled to adjust the refrigerant flow rate flowing to the heat exchanger section 503b.
  • the opening degree of the flow rate adjustment valve 564 adjusts the refrigerant flow rate branched to the heat exchanger section 503b, so the refrigerant flow rate flowing to the heat exchanger section 503a also changes.
  • the refrigerant flows from the refrigerant piping 27 through the connecting pipe 563c, branches into two refrigerant inlet pipes 563a, 563b at the upstream branch section 563d, and flows into each of the heat exchanger sections 503a, 503b.
  • the opening of the flow rate control valve 564 is controlled so that the refrigerant flow rate of the heat exchanger section 503a and the refrigerant flow rate of the heat exchanger section 503b correspond to the volume.
  • a flow rate adjustment valve 564 may be provided on each of the refrigerant inlet pipes 563a and 563b.
  • Each of the heat exchanger sections 503a and 503b has a plurality of heat transfer tubes 31, a plurality of fins 32, and a refrigerant distributor 30 (see FIG. 1).
  • the heat exchanger sections 503a and 503b have different volumes, and when the refrigerant from the refrigerant piping 27 branches at the upstream branch section 563d, it is branched at a ratio according to the volumes of the heat exchanger sections 503a and 503b.
  • the flow rate is not distributed at a 1:1 ratio in this way, there is a tendency for the refrigerant flow rate or dryness to vary significantly.
  • the heat exchanger section 503a and the heat exchanger section 503b each have a refrigerant distributor 30 (see FIG. 1) that is more resistant to liquid level fluctuations than conventional refrigerant distributors, so the deterioration of refrigerant distribution is suppressed. This also makes it possible to suppress the decrease in heat exchange efficiency.
  • the heat exchanger 403, 503 includes a refrigerant distributor 30 having an outer tube 34 and an inner tube 33 with multiple refrigerant outlet holes 35, as in the first embodiment, and a structural part C is provided upstream of the refrigerant distributor 30 to make the state of the refrigerant flowing inside the inner tube 33 an underdeveloped gas-liquid two-phase flow.
  • the number No of the multiple refrigerant outlet holes 35 provided in the inner tube 33 satisfies (Nt-1)/6 ⁇ No ⁇ (Nt-1).
  • the heat exchanger 403 of the second embodiment includes two heat exchanger sections 403a and 403b.
  • the two heat exchanger sections are connected to each other upstream of the structural section C of the two heat exchanger sections.
  • the heat exchanger 503 according to the first modified example of the second embodiment is provided with a flow rate adjustment valve 564 that adjusts the ratio of the refrigerant flow rates of the two heat exchanger sections 503a and 503b.
  • the two heat exchanger sections 503a and 503b have different volumes.
  • each heat exchanger section 503a, 503b is provided with a refrigerant distributor 30 that is resistant to liquid level fluctuations, which makes it possible to prevent deterioration of refrigerant distribution.
  • each heat exchanger section 403a, 403b is defined as having the same configuration as the heat exchanger 3 in the first embodiment, but may have the same configuration as the heat exchanger 303, the heat exchanger 303a, or the heat exchanger 303b in the second embodiment.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un échangeur de chaleur selon la présente divulgation comprend une pluralité de tubes de transfert de chaleur et un distributeur de fluide frigorigène qui s'étend dans une direction horizontale transversale et distribue un fluide frigorigène à la pluralité de tubes de transfert de chaleur, l'échangeur de chaleur étant conçu à partir d'au moins une partie échangeur de chaleur dans laquelle une partie structure est disposée en amont ou dans une section amont du distributeur de fluide frigorigène dans une direction d'écoulement de fluide frigorigène lorsqu'il fonctionne en tant qu'évaporateur. Un climatiseur selon la présente divulgation est pourvu de cet échangeur de chaleur. Le distributeur de fluide frigorigène comprend : un tuyau externe dans lequel s'écoule le fluide frigorigène et auquel la pluralité de tubes de transfert de chaleur sont reliés à des intervalles prédéterminés ; et un tuyau interne dans lequel s'écoule le fluide frigorigène et qui est disposé sur le côté périphérique interne du tuyau externe. Le tuyau interne est pourvu d'une pluralité de trous de sortie de fluide frigorigène qui amènent le fluide frigorigène s'écoulant à l'intérieur de celui-ci à s'écouler vers l'extérieur vers un espace entre le tuyau externe et le tuyau interne. Le nombre de trous de la pluralité de trous de sortie de fluide frigorigène disposés dans le tuyau interne satisfait (Nt -1)/6 ≤ No < (Nt -1) lorsque No est défini comme le nombre de trous et Nt est défini comme le nombre de la pluralité de tubes de transfert de chaleur. La partie structure amène l'état du fluide frigorigène s'écoulant dans le tuyau interne dans un état dans lequel un écoulement diphasique gaz-liquide ne se développe pas lors du fonctionnement en tant qu'évaporateur.
PCT/JP2023/021665 2023-06-12 2023-06-12 Échangeur de chaleur et climatiseur Pending WO2024257145A1 (fr)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100089559A1 (en) * 2006-10-13 2010-04-15 Carrier Corporation Method and apparatus for improving distribution of fluid in a heat exchanger
US20110017438A1 (en) * 2009-07-23 2011-01-27 Danfoss Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Multi-channel heat exchanger with improved uniformity of refrigerant fluid distribution
JP2019027727A (ja) * 2017-08-02 2019-02-21 三菱重工サーマルシステムズ株式会社 熱交換器
JP2020143801A (ja) * 2019-03-04 2020-09-10 三菱重工サーマルシステムズ株式会社 蒸発器及びこれを備えた室外機並びに空気調和装置
WO2021235463A1 (fr) * 2020-05-22 2021-11-25 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur de chaleur, et climatiseur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100089559A1 (en) * 2006-10-13 2010-04-15 Carrier Corporation Method and apparatus for improving distribution of fluid in a heat exchanger
US20110017438A1 (en) * 2009-07-23 2011-01-27 Danfoss Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Multi-channel heat exchanger with improved uniformity of refrigerant fluid distribution
JP2019027727A (ja) * 2017-08-02 2019-02-21 三菱重工サーマルシステムズ株式会社 熱交換器
JP2020143801A (ja) * 2019-03-04 2020-09-10 三菱重工サーマルシステムズ株式会社 蒸発器及びこれを備えた室外機並びに空気調和装置
WO2021235463A1 (fr) * 2020-05-22 2021-11-25 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur de chaleur, et climatiseur

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