WO2024084543A1 - Dispositif à cycle de réfrigération, échangeur thermique et distributeur de fluide frigorigène - Google Patents

Dispositif à cycle de réfrigération, échangeur thermique et distributeur de fluide frigorigène Download PDF

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Publication number
WO2024084543A1
WO2024084543A1 PCT/JP2022/038548 JP2022038548W WO2024084543A1 WO 2024084543 A1 WO2024084543 A1 WO 2024084543A1 JP 2022038548 W JP2022038548 W JP 2022038548W WO 2024084543 A1 WO2024084543 A1 WO 2024084543A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
refrigeration cycle
side heat
distributor
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PCT/JP2022/038548
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English (en)
Japanese (ja)
Inventor
敬三 鎌田
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三菱電機株式会社
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Priority to PCT/JP2022/038548 priority Critical patent/WO2024084543A1/fr
Publication of WO2024084543A1 publication Critical patent/WO2024084543A1/fr

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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
    • 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
    • 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

Definitions

  • This disclosure relates to a refrigeration cycle device, and a heat exchanger and a refrigerant distributor used in the refrigeration cycle device.
  • a parallel-flow type heat exchanger is disclosed in Patent Document 1 as a heat exchanger used in a refrigeration cycle device.
  • a parallel-flow type heat exchanger is composed of refrigerant distributors installed in parallel with a gap between them, a number of heat transfer tubes arranged between the refrigerant distributors and having a number of refrigerant flow paths inside, and a number of fins arranged between the heat transfer tubes.
  • the refrigeration cycle device disclosed herein includes a compressor that compresses a refrigerant, a load-side heat exchanger into which the refrigerant compressed by the compressor flows and into which heat is exchanged between the refrigerant and a load-side heat medium, a pressure reducing device that reduces the pressure of the refrigerant that has undergone heat exchange in the load-side heat exchanger, and a heat-source-side heat exchanger into which the refrigerant reduced in pressure by the pressure reducing device flows and into which heat is exchanged between the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger and a heat-source-side heat medium, the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger is compressed by the compressor, and the refrigerant that flows into the heat-source-side heat exchanger is in a two-phase gas-liquid state, and the heat-source-side heat exchanger includes a refrigerant flow path section in which a flow path
  • the heat source side heat exchanger of the present disclosure also includes a refrigerant flow path section having a flow path formed therein through which a gas-liquid two-phase refrigerant flows in a flow direction having a vector component perpendicular to the direction of gravity, a refrigerant distributor having a plurality of refrigerant outlet holes arranged along the flow direction from which the refrigerant flowing through the refrigerant flow path section flows out, and a protrusion protruding from the inner wall surface of the flow path of the refrigerant flow path section, and a plurality of heat transfer tubes through which the refrigerant flowing out of the refrigerant outlet holes of the refrigerant distributor flows.
  • the refrigerant distributor of the present disclosure also has a refrigerant flow path section in which a flow path is formed through which a two-phase gas-liquid refrigerant flows in a flow direction having a vector component perpendicular to the direction of gravity, a plurality of refrigerant outlet holes are provided so that the refrigerant flowing through the refrigerant flow path section flows out and is aligned along the flow direction, and a protrusion protruding from the inner wall surface of the flow path of the refrigerant flow path section.
  • the refrigeration cycle device, heat source side heat exchanger, and refrigerant distributor disclosed herein have the effect of suppressing the imbalance of the liquid refrigerant when a gas-liquid two-phase refrigerant flows in.
  • FIG. 1 is a refrigerant circuit diagram showing a flow of a refrigerant in a refrigeration cycle device according to a first embodiment.
  • 1 is a schematic diagram showing an outdoor unit of a refrigeration cycle device according to a first embodiment.
  • 2 is a side view of a heat source side heat exchanger of the refrigeration cycle apparatus according to the first embodiment.
  • FIG. 4 is a cross-sectional view of the heat source side heat exchanger of the refrigeration cycle apparatus according to the first embodiment taken along the line CC of FIG. 3.
  • 5 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle apparatus according to the first embodiment taken along the line D-D of FIG. 4.
  • FIG. 4 is a cross-sectional view of a heat source side heat exchanger of a refrigeration cycle apparatus according to a first comparative example, the cross section corresponding to the CC cross section in FIG. 3 .
  • 7 is a cross-sectional view taken along the line E-E of FIG. 6 of the gas-liquid refrigerant distributor of the refrigeration cycle apparatus according to the first comparative example.
  • FIG. 4 is a refrigerant circuit diagram showing a refrigerant circuit of a refrigeration cycle device according to a modified example of the first embodiment.
  • 5 is a cross-sectional view of a heat source side heat exchanger of a refrigeration cycle apparatus according to a second embodiment, taken along a cross section corresponding to cross section CC in FIG. 3 .
  • FIG. 10 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle apparatus according to the second embodiment taken along the line F-F of FIG. 9 .
  • 11 is a cross-sectional view of a heat source side heat exchanger of a refrigeration cycle apparatus according to a third embodiment of the present invention, taken along a cross section corresponding to cross section CC.
  • 12 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle apparatus according to embodiment 3 taken along line G-G in FIG. 11 .
  • 11 is a cross-sectional view of a heat source side heat exchanger of a refrigeration cycle apparatus according to a fourth embodiment of the present invention, taken along a cross section corresponding to cross section CC.
  • FIG. 14 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle apparatus according to embodiment 4 taken along line H-H in FIG. 13 .
  • 7 is a cross-sectional view taken along the line E-E of FIG. 6 of a gas-liquid refrigerant distributor of a refrigeration cycle apparatus according to a second comparative example.
  • FIG. 1 is a refrigerant circuit diagram showing the flow of refrigerant in a refrigeration cycle device 1 according to the first embodiment.
  • the refrigeration cycle device 1 includes an outdoor unit 101 and an indoor unit 102.
  • the outdoor unit 101 and the indoor unit 102 are connected to each other by a first external pipe 17 and a second external pipe 21.
  • the outdoor unit 101 includes a compressor 11, an outdoor fan 13, and a heat source side heat exchanger 14.
  • the compressor 11, the outdoor fan 13, and the heat source side heat exchanger 14 are each connected to each other by an outdoor unit refrigerant pipe 23.
  • the indoor unit 102 includes an indoor fan 19, a load side heat exchanger 20, and an expansion valve 18.
  • the indoor fan 19, the load side heat exchanger 20, and the expansion valve 18 are each connected to each other by an indoor unit refrigerant pipe 24.
  • a refrigerant circuit is formed in which the refrigerant flows in the order of the compressor 11, the load side heat exchanger 20, the expansion valve 18, the heat source side heat exchanger 14, and the compressor 11.
  • the refrigerant that circulates through the refrigerant circuit is a refrigerant that vaporizes or condenses in the heat source side heat exchanger 14 and the load side heat exchanger 20 .
  • the compressor 11 compresses the low-temperature, low-pressure refrigerant drawn in from the suction port, converts it into a high-temperature, high-pressure gaseous state, and discharges it from the discharge port.
  • the compressor 11 is, for example, a capacity-controllable inverter compressor.
  • the outdoor fan 13 blows outdoor air to the heat source side heat exchanger 14.
  • the heat source side heat exchanger 14 exchanges heat between the refrigerant that has flowed into the heat source side heat exchanger 14 and the outdoor air that passes over the surface of the heat source side heat exchanger 14.
  • the heat source side heat exchanger 14 is also configured with a gas refrigerant distributor 2 and a gas-liquid refrigerant distributor 3. The configuration of the heat source side heat exchanger 14 will be described later.
  • the expansion valve 18 corresponds to a pressure reducing device, and reduces the pressure of the refrigerant by expanding it.
  • the expansion valve 18 is, for example, an electronic expansion valve.
  • the indoor fan 19 blows indoor air to the load side heat exchanger 20.
  • the load side heat exchanger 20 exchanges heat between the refrigerant that flows into the load side heat exchanger 20 and the indoor air that passes over the surface of the load side heat exchanger 20.
  • the flow of the refrigerant is indicated by solid arrows.
  • the compressor 11 draws in low-temperature, low-pressure refrigerant from the suction port, compresses it, and discharges it as high-temperature, high-pressure gaseous refrigerant.
  • the discharged high-temperature, high-pressure gaseous refrigerant is transferred to the indoor unit 102 through the first external piping 17 and flows into the load-side heat exchanger 20.
  • the high-temperature, high-pressure gaseous refrigerant that flows into the load-side heat exchanger 20 is condensed to become high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant that flows out of the load-side heat exchanger 20 is decompressed by the expansion valve 18 and becomes a low-pressure two-phase gas-liquid refrigerant.
  • the low-pressure two-phase gas-liquid refrigerant that flows out of the expansion valve 18 is transferred to the outdoor unit 101 through the second external piping 21 and flows into the heat source-side heat exchanger 14.
  • the low-pressure two-phase gas-liquid refrigerant that flows into the heat source-side heat exchanger 14 evaporates to become a low-pressure gaseous refrigerant.
  • the low-temperature, low-pressure gas refrigerant that flows out of the heat source side heat exchanger 14 is supplied again to the compressor 11. By circulating the refrigerant in this way, the indoor air is heated by the high-temperature, high-pressure gas refrigerant in the load side heat exchanger 20.
  • FIG. 2 is a schematic diagram showing an outdoor unit of a refrigeration cycle device according to embodiment 1 of the present disclosure.
  • the outdoor unit 101 according to embodiment 1 is a top-flow type, and includes a casing 111 that forms a housing.
  • the casing 111 includes a side opening 112, an air guide section 113, and an upper opening 114.
  • the casing also includes a compressor 11, an outdoor fan 13, and a heat source-side heat exchanger 14.
  • the side openings 112 are provided on the side and back sides of the casing 111.
  • the heat source side heat exchanger 14 is disposed inside the side openings 112.
  • the side openings 112 are structured to draw in air so that it passes through the heat source side heat exchanger 14.
  • the refrigerant flowing inside the heat source side heat exchanger 14 exchanges heat with the air drawn in from the side openings 112.
  • the air guide section 113 is provided at the top of the casing 111 and is configured to surround the outdoor fan 13.
  • the air guide section 113 guides the air that has passed through the heat source side heat exchanger 14 to the top.
  • the top opening 114 is provided at the top of the casing 111 and at the top of the air guide section 113.
  • the top opening 114 discharges the air guided by the air guide section above the casing 111.
  • FIG. 3 is a side view showing the heat source side heat exchanger of the refrigeration cycle device according to embodiment 1 of the present disclosure.
  • FIG. 4 is a cross-sectional view taken along C-C in FIG. 3 of the heat source side heat exchanger of the refrigeration cycle device according to embodiment 1.
  • the configuration of the heat source side heat exchanger 14 and the flow of refrigerant will be explained using FIG. 3 and FIG. 4.
  • the arrows in FIG. 3 and FIG. 4 indicate the flow of refrigerant when the heat source side heat exchanger 14 functions as an evaporator during heating operation.
  • the heat source side heat exchanger 14 includes a gas refrigerant distributor 2, a gas-liquid refrigerant distributor 3, a plurality of flat tubes 4, fins 5, a partition section 9, and a folded section 10.
  • the gas refrigerant distributor 2 has an elongated shape, and its longitudinal direction is parallel to a horizontal plane.
  • the gas refrigerant distributor 2 is a tube with an internal space formed therein, and the internal space of the gas refrigerant distributor 2 communicates with a plurality of flat tubes 4.
  • the gas-liquid refrigerant distributor 3 has an elongated shape and is arranged with its longitudinal direction parallel to the horizontal plane.
  • the gas-liquid refrigerant distributor 3 has a double-tube structure including an inner tube 30, which is a tube with an internal space, and an outer tube 31 that houses the inner tube 30 in the internal space.
  • the inner tube 30 of the gas-liquid refrigerant distributor 3 has one longitudinal end open and the other longitudinal end closed.
  • the inner tube 30 has a plurality of refrigerant holes 7, a refrigerant flow path portion 33, and a protrusion portion 8.
  • the refrigerant holes 7 are arranged vertically below half the height of the gas-liquid refrigerant distributor 3.
  • the term "located below” also includes the case where even a part of the refrigerant holes 7 is located below half the height of the gas-liquid refrigerant distributor 3.
  • the refrigerant flow path portion 33 forms a flow path that flows the refrigerant in a flow direction having a vector component perpendicular to the direction of gravity, that is, parallel to the horizontal plane.
  • the protrusion 8 is provided at the top of the inner wall surface of the flow path in the refrigerant flow path section 33 in the vertical direction of the gas-liquid refrigerant distributor 3.
  • One end of the inner pipe 30 is provided with a pipe connection port for connecting a pipe.
  • the protrusions 8 are provided on the inner wall surface closer to the inlet than the multiple refrigerant holes 7. A space for the refrigerant to flow is provided between the inner tube 30 and the protrusions 8.
  • the peeling phenomenon generates pressure resistance, which increases pressure loss and affects the flow rate of the liquid refrigerant.
  • the dimensions of the protrusions 8 are set to a certain level or less.
  • the size of the protrusions 8 protruding from the inner wall surface of the flow passage of the refrigerant flow passage 33 is set to be smaller than the diameter of the refrigerant holes 7. If the height of the protrusions 8 is lower than the diameter of the refrigerant holes 7, the pressure loss caused by the protrusions 8 is reduced. The reduced pressure loss prevents the liquid refrigerant from concentrating around the refrigerant holes 7 on the inlet side. If the refrigerant holes 7 have a shape such that the diameter varies depending on the direction of measurement, such as an ellipse, the diameter of the refrigerant holes 7 is the diameter when measured in the direction in which the diameter is the longest.
  • the surface of the tip of the protrusion 8 facing the refrigerant flow is a curved surface.
  • the tip of the protrusion 8 of the refrigeration cycle device 1 of embodiment 1 is hemispherical.
  • the tip of the protrusion 8 of the refrigeration cycle device 1 of embodiment 1 is spherical, but the hemispherical shape in this disclosure is not limited to a spherical shape, and also includes, for example, an elliptical shape.
  • the shape of the protrusion 8 may be a streamlined shape that is less likely to generate vortexes.
  • the surface of the protrusion 8 may be processed to have a rough surface. By making the surface rough, it becomes less likely to peel off, and the pressure resistance generated in the refrigerant can be reduced.
  • the flat tubes 4 correspond to heat transfer tubes, and are arranged so that the longitudinal direction of the flat tubes 4 is perpendicular to the longitudinal direction of the gas-liquid refrigerant distributor 3.
  • the flat tubes 4 also have a plurality of refrigerant flow paths inside, which are connected to the internal space of the gas refrigerant distributor 2 or the internal space of the outer tube 31 of the gas-liquid refrigerant distributor 3, and the internal space of the turn-back section 10.
  • the flat tube 4 that connects the internal space of the outer tube 31 to the internal space of the turn-back section 10 is called the first flat tube 4a
  • the flat tube 4 that connects the internal space of the gas refrigerant distributor 2 to the internal space of the turn-back section 10 is called the second flat tube 4b.
  • the first flat tube 4a is located on the windward side of the second flat tube 4b.
  • the fins 5 are provided on the flat surfaces of the flat tubes 4.
  • the fins 5 are, for example, corrugated fins.
  • the partition section 9 is located between the outer wall surface of the inner pipe 30 and the inner wall surface of the outer pipe 31 of the gas-liquid refrigerant distributor 3, and is provided perpendicular to the longitudinal direction of the gas-liquid refrigerant distributor 3.
  • the partition section 9 is also provided so that the number of small compartments in the outer pipe 31 is the same as the number of refrigerant holes 7 provided in the inner pipe 30.
  • the folded portion 10 is connected to multiple flat tubes 4, and the longitudinal direction of the folded portion 10 is parallel to the horizontal plane.
  • the refrigerant in a gas-liquid two-phase state that flows into the heat source side heat exchanger 14 during heating operation is often annular flow or annular mist flow.
  • An annular flow is a flow in which a liquid film flow, which is a film of liquid refrigerant, exists on the tube wall and a large number of droplets are entrained in the center of the tube cross section of the gas phase refrigerant.
  • An annular mist flow is a flow in which there are many droplets in the air flow, among the annular flows.
  • An annular flow and annular mist flow are flows consisting of a liquid film flow that flows along the channel wall surface and droplets entrained in the air flow flowing in the center of the channel.
  • the flow in the upper vertical part collides with the protrusion 8 and then flows in a flow direction having a vector component perpendicular to the direction of gravity in the refrigerant channel part 33.
  • the flows other than the upper vertical part flow in a flow direction having a vector component perpendicular to the direction of gravity in the refrigerant channel part 33 without colliding with the protrusion 8.
  • the refrigerant that flows in from the piping connected to the end of the inner tube 30 of the gas-liquid refrigerant distributor 3 flows out to the outer tube 31 through the refrigerant hole 7.
  • the gas-liquid two-phase refrigerant then flows vertically upward inside the first flat tube 4a on the gas-liquid refrigerant distributor 3 side of the multiple connected flat tubes 4.
  • the refrigerant and the outdoor air exchange heat via the outdoor fan 13, and the refrigerant becomes a low-pressure gas.
  • the refrigerant that flows out of the flat tubes 4 flows into the turn-back section 10.
  • the refrigerant that passes through the turn-back section 10 flows vertically downward inside the second flat tube 4b of the flat tubes 4 and flows into the gas refrigerant distributor 2.
  • the gas refrigerant then flows out of the gas refrigerant distributor 2 and out of the heat source side heat exchanger 14.
  • Figure 5 is a cross section taken along line D-D in Figure 4 of the gas-liquid refrigerant distributor of the refrigeration cycle device according to embodiment 1.
  • the end side of the inner pipe 30 of the gas-liquid refrigerant distributor 3 that is closed in the longitudinal direction is designated as A, and the inlet side that is open in the longitudinal direction is designated as B.
  • the arrows in Figure 5 indicate the direction in which the refrigerant flows in the flow path formed by the refrigerant flow path section 33 of the inner pipe 30.
  • the protrusion 8 is provided at the top of the inner wall surface of the inner pipe 30 on the B side of the refrigerant hole 7.
  • the vertical upper flow of the liquid film of the gas-liquid two-phase refrigerant of the annular flow flowing into the inner pipe 30 collides with the protrusion 8 provided on the inner wall surface of the refrigerant flow path section 33 of the inner pipe 30.
  • the liquid refrigerant that collides with the protrusion 8 is smoothly guided to the vertical lower part of the liquid film along the wall surface of the inner pipe while flowing horizontally.
  • the liquid refrigerant in the refrigerant flow path section 33 is affected by gravity and inertial forces due to the flow. In particular, when the refrigerant flow rate is high and the liquid film height of the annular flow is high, the effect of inertia on the liquid refrigerant is greater than the effect of gravity.
  • the liquid refrigerant tends to concentrate at the end without flowing out of the refrigerant hole 7 of the inner tube.
  • the configuration of embodiment 1 in which the liquid refrigerant collides with the protrusion 8 can reduce the effect of inertia on the liquid refrigerant. Therefore, the distribution of the refrigerant flowing out of the refrigerant hole 7 of the inner tube 30 and the bias of the liquid refrigerant flowing through the multiple flat tubes 4 are suppressed, and the heat transfer efficiency is expected to improve.
  • the inflowing gas-liquid two-phase refrigerant can be collided with the protrusions 8 to reduce the effect of the inertial force of the refrigerant, thereby suppressing refrigerant bias.
  • FIG. 6 is a cross-sectional view of the heat source side heat exchanger of the refrigeration cycle device according to the first comparative example, corresponding to the cross section C-C in FIG. 3.
  • FIG. 7 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle device according to the first comparative example, corresponding to the cross section E-E in FIG. 6. Specifically, FIG. 7 shows the inner pipe 61 of the gas-liquid refrigerant distributor 60 according to the comparative example when the refrigerant flow rate is large.
  • the gas-liquid refrigerant distributor 60 according to the comparative example differs from the gas-liquid refrigerant distributor 3 of the refrigeration cycle device according to the first embodiment only in that it does not have the protrusion 8.
  • the end side of the gas-liquid refrigerant distributor 60 according to the comparative example is designated K, and the inlet side is designated L.
  • the arrows in FIG. 7 indicate the direction in which the refrigerant flows through the refrigerant flow passage portion 64 of the gas-liquid refrigerant distributor 60 according to the comparative example during heating operation. Using FIG. 7, the effect of the protrusion 8 of the gas-liquid refrigerant distributor 3 of the first embodiment will be explained in comparison with the comparative example.
  • the gas-liquid refrigerant distributor 3 of embodiment 1 which is provided with the protrusion 8, the difference between the amount of liquid refrigerant near the refrigerant hole on side A and the amount of liquid refrigerant near the refrigerant hole on side B is smaller than in the comparative example due to the protrusion 8. Therefore, the gas-liquid refrigerant distributor 3 of embodiment 1 has improved horizontal distribution compared to comparative example 1, and the bias of the liquid refrigerant is suppressed.
  • the refrigeration cycle device 1 is configured to include a compressor 11 that compresses a refrigerant, a load-side heat exchanger 20 into which the refrigerant compressed by the compressor 11 flows and into which heat is exchanged between the flowing-in refrigerant and a load-side heat medium, a pressure reducing device (corresponding to an expansion valve 18) that reduces the pressure of the refrigerant that has undergone heat exchange in the load-side heat exchanger 20, and a heat-source-side heat exchanger 14 into which the refrigerant that has been depressurized by the pressure reducing device flows and into which heat is exchanged between the flowing-in refrigerant and a heat-source-side heat medium, and the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger 14 is compressed by the compressor 11 and flows into the heat-source-side heat exchanger 14.
  • the refrigerant is in a gas-liquid two-phase state
  • the heat source side heat exchanger 14 is configured to include a refrigerant flow path section 33 that forms a flow path in which the refrigerant in the gas-liquid two-phase state flows in a flow direction having a vector component perpendicular to the gravity direction, a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) that has a plurality of refrigerant outlet holes (corresponding to the refrigerant holes 7) that are arranged along the flow direction so that the refrigerant flowing through the refrigerant flow path section 33 flows out, and a protrusion 8 that protrudes from the inner wall surface of the flow path of the refrigerant flow path section 33, and a plurality of heat transfer tubes (corresponding to the flat tubes 4) through which the refrigerant flowing out of the refrigerant outlet holes of the refrigerant distributor flows.
  • the refrigeration cycle device 1 according to embodiment 1 has the effect of suppressing bias in the liquid refrig
  • the refrigeration cycle device 1 according to embodiment 1 has a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) that includes an outer pipe 31 and an inner pipe 30 provided within the outer pipe 31, and the inner pipe 30 has a refrigerant flow passage portion 33, a refrigerant outlet hole portion (corresponding to the refrigerant hole 7), and a protrusion portion 8, and the refrigerant that flows out from the refrigerant outlet hole portion flows through the space between the inner pipe 30 and the outer pipe 31, and flows out from the space between the inner pipe 30 and the outer pipe 31 to a plurality of heat transfer tubes (corresponding to the flat tubes 4).
  • the refrigeration cycle device 1 according to embodiment 1 has the effect of being able to reduce the amount of refrigerant in the refrigeration cycle device 1.
  • the refrigeration cycle device 1 according to embodiment 1 has a long refrigerant distributor (corresponding to gas-liquid refrigerant distributor 3), and protrusion 8 is provided on the opening side of the refrigerant distributor relative to the multiple refrigerant outlet holes (corresponding to refrigerant holes 7) in the longitudinal direction parallel to the refrigerant flow direction of the refrigerant distributor.
  • the refrigeration cycle device 1 according to embodiment 1 has the effect of effectively weakening the influence of the inertial force of the liquid refrigerant.
  • the refrigeration cycle device 1 according to the first embodiment has an additional configuration in which a partition section 9 that divides the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) in the longitudinal direction is provided between the outer pipe 31 and the inner pipe 30 of the refrigerant flow path section 33.
  • the refrigeration cycle device 1 according to the first embodiment has the effect of effectively suppressing bias in the refrigerant distribution in the refrigeration cycle device 1.
  • the refrigeration cycle device 1 according to the first embodiment has an additional configuration in which the surface of the protrusion 8 that faces the flow of the refrigerant is curved. With this additional configuration, the refrigeration cycle device 1 according to the first embodiment has the effect of suppressing turbulence of the liquid refrigerant and suppressing pressure loss.
  • the refrigeration cycle device 1 according to the first embodiment has an additional configuration in which the refrigerant outlet hole portion (corresponding to the refrigerant hole 7) is provided vertically below half the height of the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3).
  • the refrigeration cycle device 1 according to the first embodiment has the effect of allowing the refrigerant to efficiently flow out of the refrigerant outlet hole portion even when the refrigerant flow rate is high.
  • the refrigeration cycle device 1 according to the first embodiment has an additional configuration in which the protrusion 8 is provided at the top of the inner wall surface of the flow path in the refrigerant flow path portion 33 in the vertical direction.
  • the refrigeration cycle device 1 according to the first embodiment has the effect of reducing the influence of the inertial force of the liquid refrigerant, and dispersing the liquid refrigerant flowing above the refrigerant flow path portion 33 relatively downward.
  • the refrigeration cycle device 1 according to embodiment 1 has an additional configuration in which the size by which the protrusion 8 protrudes from the inner wall surface of the flow passage of the refrigerant flow passage portion 33 is smaller than the diameter of the refrigerant outflow hole portion (corresponding to the refrigerant hole 7). With this additional configuration, the refrigeration cycle device 1 according to embodiment 1 has the effect of reducing the pressure loss caused by the protrusion 8.
  • the heat source side heat exchanger includes a refrigerant flow path section 33 that forms a flow path through which a gas-liquid two-phase refrigerant flows in a flow direction having a vector component perpendicular to the direction of gravity, a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) having a plurality of refrigerant outlet holes (corresponding to the refrigerant holes 7) that are arranged along the flow direction so that the refrigerant flowing through the refrigerant flow path section 33 flows out, and a protrusion 8 that protrudes from the inner wall surface of the flow path of the refrigerant flow path section 33, and a plurality of heat transfer tubes (corresponding to the flat tubes 4) through which the refrigerant flowing out of the refrigerant outlet holes of the refrigerant distributor flows.
  • the heat source side heat exchanger 14 according to the first embodiment has the effect of suppressing the uneven distribution of the liquid refrigerant.
  • the refrigerant distributor according to embodiment 1 (corresponding to gas-liquid refrigerant distributor 3) includes a refrigerant flow path section 33 that forms a flow path through which refrigerant in a two-phase gas-liquid state flows in a flow direction having a vector component perpendicular to the direction of gravity, a plurality of refrigerant outlet holes (corresponding to refrigerant holes 7) that are provided so that the refrigerant flowing through the refrigerant flow path section 33 flows out and is aligned along the flow direction, and a protrusion 8 that protrudes from the inner wall surface of the flow path of the refrigerant flow path section 33.
  • the refrigerant distributor according to embodiment 1 has the effect of suppressing uneven distribution of the liquid refrigerant.
  • the heat source side heat exchanger 14 and the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) in the first embodiment may include additional components of the refrigeration cycle device 1 in the first embodiment described above.
  • the gas-liquid refrigerant distributor in the first embodiment has a double-tube structure with an inner tube and an outer tube, but it does not have to have a double-tube structure.
  • the refrigerant flow path of the gas-liquid refrigerant distributor is connected to the flat tubes, and the refrigerant moves directly from the refrigerant flow path to the flat tubes.
  • gas-liquid refrigerant distributor in embodiment 1 has a partition between the inner and outer pipes, but this is not essential.
  • the gas-liquid refrigerant distributor of the heat source side heat exchanger in embodiment 1 is arranged in a horizontal direction, this is not limited to this. Specifically, it is sufficient that the gas-liquid refrigerant distributor is arranged so that a flow path is formed so that the gas-liquid two-phase refrigerant flows in a direction having a vector component perpendicular to the direction of gravity.
  • the inlet side of the gas-liquid refrigerant distributor may be installed lower than the terminal side, so that the gas-liquid two-phase refrigerant flowing through the refrigerant flow path is inclined at an angle greater than 0 degrees and less than 90 degrees with respect to the horizontal plane. With this configuration, it is possible to reduce the effect of the inertial force of the liquid refrigerant and reduce the amount of refrigerant concentrating at the terminal portion.
  • the surface of the protrusion of the gas-liquid refrigerant distributor in embodiment 1 that faces the refrigerant flow is a curved surface, but this is not limited to this.
  • the protrusion may have a shape in which the surface that faces the refrigerant flow is flat, such as an angular or semicircular shape. Such a shape of the protrusion makes the shape of the protrusion simple, which makes it possible to reduce manufacturing costs.
  • the protrusions of the gas-liquid refrigerant distributor in embodiment 1 are provided on the inlet side of the multiple refrigerant holes in the longitudinal direction of the gas-liquid refrigerant distributor, but this is not limited to this. It is sufficient that the protrusions are provided on the refrigerant flow path of the gas-liquid refrigerant distributor.
  • the protrusions may be provided between the refrigerant holes in the longitudinal direction of the gas-liquid refrigerant distributor.
  • the protrusions may be provided on the terminal side of the multiple refrigerant holes in the longitudinal direction of the gas-liquid refrigerant distributor. In either case, the protrusions can weaken the effect of the inertial force of the liquid refrigerant and reduce the amount of refrigerant concentrating at the terminal end.
  • FIG. 1 A modified example of embodiment 1.
  • the refrigeration cycle apparatus 6 according to a modification of embodiment 1 includes a four-way valve 12 and a second expansion valve 15.
  • the configurations of the compressor 11, the heat source side heat exchanger 14, the outdoor fan 13, the load side heat exchanger 20, the expansion valve 18, and the indoor fan 19 in the refrigeration cycle apparatus 6 are similar to those of the refrigeration cycle apparatus 1 according to embodiment 1, and therefore description thereof will be omitted.
  • FIG. 8 is a refrigerant circuit diagram showing a refrigerant circuit of a refrigeration cycle device according to a modified example of the first embodiment.
  • the refrigeration cycle device 6 includes an outdoor unit 101 and an indoor unit 102, as in the first embodiment.
  • the outdoor unit 101 and the indoor unit 102 are connected by a first external pipe 17 and a second external pipe 21.
  • the outdoor unit 101 includes a compressor 11, a four-way valve 12, a second expansion valve 15, a heat source side heat exchanger 14, and an outdoor fan 13, which are all connected by an outdoor unit refrigerant pipe 23.
  • the indoor unit includes an indoor fan 19, a load side heat exchanger 20, and an expansion valve 18, which are all connected by an indoor unit refrigerant pipe 24.
  • the four-way valve 12 switches between the refrigerant circuit during heating operation and the refrigerant circuit during cooling operation.
  • the four-way valve 12 has a first connection port 12a on the high temperature side that communicates with the compressor's discharge port, a second connection port 12b on the low temperature side that communicates with the compressor's suction port, a third connection port 12c on the load side that communicates with the load side heat exchanger, and a fourth connection port 12d on the heat source side that communicates with the heat source side heat exchanger.
  • the four-way valve 12 is, for example, a differential pressure driven four-way valve equipped with a piston member that slides within a valve chamber, a main valve fixed between both ends of the piston member, and a differential pressure drive mechanism that generates a pressure difference between both ends of the piston member to switch the position of the main valve.
  • the second expansion valve 15 is used to control the pressure of the expansion valve 18 during the transitional period at startup, and is fully open in the steady state.
  • FIG. 8 the flow of refrigerant during heating operation is indicated by solid arrows.
  • the function of the four-way valve 12 during heating operation will be described.
  • the flow of refrigerant during heating operation, excluding the four-way valve 12, is the same as in embodiment 1, so it will be omitted.
  • High-pressure gas refrigerant discharged from the compressor 11 flows into the four-way valve 12 from the first connection port 12a.
  • the refrigerant that flows into the four-way valve 12 flows out from the third connection port 12c and flows into the second external piping.
  • low-pressure gas refrigerant that flows out from the heat source side heat exchanger 14 flows into the four-way valve 12 from the fourth connection port 12d.
  • the refrigerant that flows into the four-way valve 12 flows out of the four-way valve 12 from the second connection port 12b and flows into the compressor 11.
  • FIG. 8 the flow of refrigerant during cooling operation in the refrigeration cycle device 6 is indicated by dotted arrows.
  • the function of the four-way valve 12 and the flow of refrigerant during cooling operation will be described.
  • High-pressure gas refrigerant discharged from the compressor 11 flows into the four-way valve 12 from the first connection port 12a.
  • the refrigerant that flows into the four-way valve 12 flows out from the fourth connection port 12d and flows into the heat source side heat exchanger 14 from the gas refrigerant distributor 2.
  • the high-pressure gas refrigerant that flows into the heat source side heat exchanger 14 is condensed and becomes liquid refrigerant.
  • the liquid refrigerant that flows out of the heat source side heat exchanger 14 from the gas-liquid refrigerant distributor 3 flows into the indoor unit 102 through the second external piping 21 and flows into the expansion valve 18.
  • the liquid refrigerant that flows into the expansion valve 18 is decompressed and expanded to become a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant that flows out of the expansion valve 18 flows into the load side heat exchanger 20.
  • the low-pressure gas refrigerant that flows out of the load-side heat exchanger 20 flows into the four-way valve 12 from the third connection port 12c.
  • the refrigerant that flows into the four-way valve 12 flows out of the four-way valve 12 from the second connection port 12b and into the compressor 11.
  • the refrigerant flowing into the gas-liquid refrigerant distributor 3 is a single-layer liquid refrigerant condensed in the heat source side heat exchanger 14. Therefore, the effect of the protrusions 8 on the pressure loss inside the pipe is small. As a result, the heat source side heat exchanger 14 of the modified example is configured to be usable without any problems even when switching between heating and cooling operation.
  • the configuration of the refrigeration cycle device 6 according to the modified embodiment 1 is similar to that of the refrigeration cycle device 1 according to embodiment 1, and includes a compressor 11 that compresses a refrigerant, a load side heat exchanger 20 into which the refrigerant compressed by the compressor 11 flows and into which heat exchange is performed between the inflowing refrigerant and the load side heat medium, a pressure reduction device (corresponding to the expansion valve 18) that reduces the pressure of the refrigerant that has undergone heat exchange in the load side heat exchanger 20, and a heat source side heat exchanger 14 into which the refrigerant depressurized by the pressure reduction device flows and into which heat exchange is performed between the inflowing refrigerant and the heat source side heat medium, and the refrigerant that has undergone heat exchange in the heat source side heat exchanger 14 is compressed by the compressor 11,
  • the refrigerant flowing into the heat source side heat exchanger 14 is in a gas-liquid two-phase state, and the heat source side heat exchanger 14 is configured to include a refrigerant
  • the refrigeration cycle device 6 also has, as an additional component, a valve (corresponding to the four-way valve 12) that switches between a refrigerant circuit during heating operation in which the refrigerant circulates through the compressor 11, the load side heat exchanger 20, the pressure reducing device (corresponding to the expansion valve 18), the heat source side heat exchanger 14, and the compressor 11 in that order, and a refrigerant circuit during cooling operation in which the refrigerant circulates through the compressor 11, the heat source side heat exchanger 14, the pressure reducing device, the load side heat exchanger 20, and the compressor 11 in that order.
  • the additional component has the effect of switching between the refrigerant circuit during heating operation and the refrigerant circuit during cooling operation.
  • Embodiment 2 A refrigeration cycle apparatus 40 according to embodiment 2 will be described.
  • the refrigeration cycle apparatus 40 according to embodiment 2 is different from embodiment 1 in the position of the protrusion 28 of the gas-liquid refrigerant distributor 43 in the heat source side heat exchanger 34.
  • the structure of the refrigeration cycle apparatus 40 according to embodiment 2, excluding the heat source side heat exchanger 34, is similar to that of embodiment 1, and therefore description thereof will be omitted.
  • FIG. 9 is a cross-sectional view of the heat source side heat exchanger according to the second embodiment, taken along the line C-C in FIG. 3.
  • the heat source side heat exchanger 34 according to the second embodiment has a gas-liquid refrigerant distributor 43, flat tubes 4, a folded portion 10, a gas refrigerant distributor 2, and fins 5.
  • the gas-liquid refrigerant distributor 43 according to the second embodiment has a double-tube structure having an inner tube 71 and an outer tube 41.
  • the refrigerant hole 27 of the gas-liquid refrigerant distributor 43 is provided below half the height of the gas-liquid refrigerant distributor 43 in the vertical direction, as in the first embodiment.
  • the protrusion 28 is provided on the inner wall surface facing the refrigerant hole 27 of the inner tube 71 of the gas-liquid refrigerant distributor 43.
  • FIG. 10 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle device according to the second embodiment taken along the line F-F in FIG. 9.
  • the arrows in FIG. 10 indicate the direction in which the refrigerant flows through the gas-liquid refrigerant distributor 43.
  • the protrusion 28 is located on the inlet side of the refrigerant hole 27 in the longitudinal direction and is located above half the height of the gas-liquid refrigerant distributor 43 in the vertical direction.
  • the liquid film of the gas-liquid two-phase refrigerant of the annular flow flowing into the inner pipe 71 of the gas-liquid refrigerant distributor 43 collides with the protrusions provided on the inner wall surface of the refrigerant flow path portion 53 in the inner pipe 71.
  • the liquid refrigerant that collides with the protrusions 28 flows horizontally and is smoothly guided along the wall surface of the inner pipe 71 in the direction opposite the protrusions 28, that is, in the direction of the refrigerant hole 27.
  • the effect of the inertial force on the liquid refrigerant is greater than the effect of gravity.
  • the configuration of the refrigeration cycle device 40 according to the second embodiment is similar to that of the refrigeration cycle device 1 according to the first embodiment, and includes a compressor 11 that compresses a refrigerant, a load-side heat exchanger 20 into which the refrigerant compressed by the compressor 11 flows and into which heat is exchanged between the flowing-in refrigerant and the load-side heat medium, a pressure reducing device (corresponding to the expansion valve 18) that reduces the pressure of the refrigerant that has undergone heat exchange in the load-side heat exchanger 20, and a heat-source-side heat exchanger 34 into which the refrigerant that has been depressurized by the pressure reducing device flows and into which heat is exchanged between the flowing-in refrigerant and the heat-source-side heat medium, and the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger 34 is compressed by the compressor 11 and is then transferred to the heat-source-side heat exchanger 34.
  • the refrigerant flowing into the heat exchanger 34 is in a gas-liquid two-phase state
  • the heat source side heat exchanger 34 is configured to include a refrigerant flow path portion 53 that forms a flow path in which the refrigerant in the gas-liquid two-phase state flows in a flow direction having a vector component perpendicular to the gravity direction, a refrigerant outlet hole portion (corresponding to the refrigerant hole 27) that is provided in a plurality of positions so that the refrigerant flowing through the refrigerant flow path portion 53 flows out and is aligned along the flow direction, a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 43) that has a protrusion portion 28 that protrudes from the inner wall surface of the flow path of the refrigerant flow path portion 53, and a plurality of heat transfer tubes (corresponding to the flat tubes 4) through which the refrigerant flowing out of the refrigerant outlet hole portion of the refrigerant distributor flows.
  • the refrigeration cycle device
  • the refrigeration cycle device 40 according to the second embodiment has a configuration in which the protrusion 28 faces the refrigerant hole 27 and is provided above half the height of the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 43) in the vertical direction.
  • the refrigeration cycle device 40 according to the second embodiment has the effect of stabilizing the distribution state of the liquid refrigerant in the heat source side heat exchanger 34, especially when the amount of liquid refrigerant is large.
  • the additional configuration of the refrigeration cycle device 40 according to the second embodiment may be added to the heat source side heat exchanger 14 and the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) of the first embodiment.
  • Embodiment 3 A refrigeration cycle apparatus 50 according to embodiment 3 will be described.
  • the refrigeration cycle apparatus 50 according to embodiment 3 is different from embodiment 1 in the positions of the protrusions 38 of the gas-liquid refrigerant distributor 63 in the heat source side heat exchanger 44, the number of the protrusions 38, and the positions of the refrigerant holes 37.
  • the structure of the refrigeration cycle apparatus 50 according to embodiment 3, excluding the heat source side heat exchanger 44, is the same as that of embodiment 1, and therefore description thereof will be omitted.
  • FIG. 11 is a cross-sectional view of the heat source side heat exchanger of the refrigeration cycle device according to embodiment 3 at a cross section corresponding to the C-C cross section.
  • the heat source side heat exchanger 44 according to embodiment 3 has a gas-liquid refrigerant distributor 63, flat tubes 4, a folded portion 10, a gas refrigerant distributor 2, and fins 5.
  • the gas-liquid refrigerant distributor 63 according to embodiment 3 has a double structure having an inner tube 81 and an outer tube 51.
  • the refrigerant hole 37 of the gas-liquid refrigerant distributor 63 according to embodiment 2 is provided at the bottom of the refrigerant flow path portion 73 in the vertical direction.
  • Two protrusions 38 are provided on the inner wall surface of the gas-liquid refrigerant distributor 63.
  • FIG. 12 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle device according to the third embodiment taken along the line G-G in FIG. 11.
  • the arrows in FIG. 12 indicate the direction in which the refrigerant flows through the gas-liquid refrigerant distributor 63.
  • the two protrusions 38 are provided on the inlet side of the refrigerant hole 37 in the longitudinal direction of the gas-liquid refrigerant distributor 63.
  • the two protrusions 38 are provided above half the height of the gas-liquid refrigerant distributor 63 in the vertical direction.
  • the liquid film flow of the annular gas-liquid two-phase refrigerant flowing into the inner tube 81 collides with the protrusions 38 provided on the inner wall surface of the refrigerant flow path portion 73 in the inner tube 81.
  • the liquid refrigerant that collides with the protrusions 38 is smoothly guided to the opposite side of the protrusions 38 along the wall surface of the inner tube 81 while flowing in the horizontal direction. Therefore, the distribution of the refrigerant flowing out of the refrigerant hole 37 of the inner tube 81 and the bias of the liquid refrigerant flowing through the multiple flat tubes 4 are suppressed, and the heat transfer efficiency is expected to improve.
  • the configuration of the refrigeration cycle device 50 according to the third embodiment is similar to that of the refrigeration cycle device 1 according to the first embodiment, and includes a compressor 11 that compresses a refrigerant, a load-side heat exchanger 20 into which the refrigerant compressed by the compressor 11 flows and into which heat is exchanged between the flowing-in refrigerant and the load-side heat medium, a pressure reducing device (corresponding to the expansion valve 18) that reduces the pressure of the refrigerant that has undergone heat exchange in the load-side heat exchanger 20, and a heat-source-side heat exchanger 44 into which the refrigerant that has been depressurized by the pressure reducing device flows and into which heat is exchanged between the flowing-in refrigerant and the heat-source-side heat medium, and the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger 44 is compressed by the compressor 11 and is then transferred to the heat-source-side heat exchanger 44.
  • a compressor 11 that compresses a refrigerant
  • the refrigerant flowing into the heat exchanger 44 is in a gas-liquid two-phase state
  • the heat source side heat exchanger 44 is configured to include a refrigerant flow path portion 73 that forms a flow path in which the refrigerant in the gas-liquid two-phase state flows in a flow direction having a vector component perpendicular to the gravity direction, a refrigerant outlet hole portion (corresponding to the refrigerant hole 37) that is provided so that the refrigerant flowing through the refrigerant flow path portion 73 flows out and is aligned along the flow direction, a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 63) that has a protrusion portion 38 that protrudes from the inner wall surface of the flow path of the refrigerant flow path portion 73, and a plurality of heat transfer tubes (corresponding to the flat tubes 4) through which the refrigerant flowing out of the refrigerant outlet hole portion of the refrigerant distributor flows.
  • the refrigeration cycle device 50 according to include
  • the refrigeration cycle device 50 according to the third embodiment has a configuration in which a plurality of protrusions 38 are provided in the refrigerant flow passage portion 73. With this configuration, the refrigeration cycle device 50 according to the third embodiment has the effect of suppressing uneven distribution of the liquid refrigerant in the heat source side heat exchanger 44, particularly when the amount of liquid refrigerant is large.
  • the refrigeration cycle device 50 has a configuration in which the refrigerant outflow hole portion (corresponding to the refrigerant hole 37) is provided at the bottom of the refrigerant flow path portion 73 in the vertical direction.
  • This configuration has the effect of suppressing the deviation of the liquid refrigerant that is strongly affected by gravity.
  • embodiment 3 is an example in which multiple protrusions are provided on the gas-liquid refrigerant distributor, and the number of protrusions is not limited to two.
  • one protrusion may be provided at the top of the gas-liquid refrigerant distributor in the vertical direction, and two protrusions may be provided above half the height of the refrigerant distributor in the vertical direction.
  • the two protrusions in the third embodiment are provided at the same position in the longitudinal direction of the gas-liquid refrigerant distributor, this is not limited to this. There may be a gap between the protrusions 38 in the longitudinal direction of the gas-liquid refrigerant distributor.
  • the additional configuration of the refrigeration cycle device 50 according to embodiment 3 may be added to the heat source side heat exchanger 14 and the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) of embodiment 1.
  • Embodiment 4 A refrigeration cycle apparatus 80 according to embodiment 4 will be described.
  • the refrigeration cycle apparatus 80 according to embodiment 4 is different from embodiment 1 in the positions of the protrusions 48 and the positions of the refrigerant holes 47 of the gas-liquid refrigerant distributor 83 in the heat source side heat exchanger 54.
  • the structure of the refrigeration cycle apparatus 80 according to embodiment 4, excluding the heat source side heat exchanger 54, is similar to that of embodiment 1, and therefore description thereof will be omitted.
  • FIG. 13 is a cross-sectional view of the heat source side heat exchanger of the refrigeration cycle device according to embodiment 4 at a cross section corresponding to the C-C cross section.
  • the heat source side heat exchanger 54 according to embodiment 4 has a gas-liquid refrigerant distributor 83, flat tubes 4, a folded portion 10, a gas refrigerant distributor 2, and fins 5.
  • the gas-liquid refrigerant distributor 83 according to embodiment 4 has a double structure having an inner tube 91 and an outer tube 65.
  • the refrigerant hole 47 of the gas-liquid refrigerant distributor 83 according to embodiment 4 is provided at the bottom of the refrigerant flow path portion 93 in the vertical direction.
  • the protrusion portion 48 is provided at the bottom of the inner wall surface of the flow path in the refrigerant flow path portion 93 in the vertical direction.
  • FIG. 14 is a cross-sectional view of the gas-liquid refrigerant distributor of the refrigeration cycle device according to embodiment 4 taken along the line H-H in FIG. 13.
  • the end side of the inner pipe 91 of the gas-liquid refrigerant distributor 83 is indicated by I, and the inlet side is indicated by J.
  • the arrows in FIG. 14 indicate the direction in which the refrigerant flows through the gas-liquid refrigerant distributor 83.
  • the protrusion 48 is located on the J side of the refrigerant hole in the longitudinal direction, and is provided at the lowermost part of the inner wall surface of the flow path in the refrigerant flow path portion 93 in the vertical direction.
  • the effect of gravity on the liquid refrigerant is greater than the effect of inertia.
  • the liquid refrigerant tends to concentrate on the J side due to the flow being stagnated midway through the refrigerant flow path 93.
  • the protrusion 48 provided at the bottom of the inner wall surface of the flow path in the refrigerant flow path 93 in the vertical direction and peeling it off from the inner wall surface, the distribution of the liquid refrigerant flowing out of the refrigerant hole 47 of the inner tube 91 and the bias of the liquid refrigerant flowing through the multiple flat tubes 4 are suppressed, and the heat transfer efficiency is expected to improve.
  • Figure 15 is a cross-sectional view taken along the line E-E of Figure 6 of the gas-liquid refrigerant distributor of a refrigeration cycle device according to a second comparative example. Specifically, Figure 15 shows the inner pipe 61 of the gas-liquid refrigerant distributor 60 according to the comparative example when the refrigerant flow rate is low. Using Figure 15, the effect of the protrusion 48 of the gas-liquid refrigerant distributor 83 of embodiment 4 will be explained in comparison with the comparative example.
  • the difference between the amount of refrigerant near the refrigerant hole on the I side and the amount of liquid refrigerant near the refrigerant hole on the J side is smaller than in the comparative example due to the protrusion 48. Therefore, horizontal distribution is improved.
  • the configuration of the refrigeration cycle device 80 according to embodiment 4 is similar to that of the refrigeration cycle device 1 according to embodiment 1, and includes a compressor 11 that compresses a refrigerant, a load-side heat exchanger 20 into which the refrigerant compressed by the compressor 11 flows and into which heat is exchanged between the flowing-in refrigerant and the load-side heat medium, a pressure reducing device (corresponding to the expansion valve 18) that reduces the pressure of the refrigerant that has undergone heat exchange in the load-side heat exchanger 20, and a heat-source-side heat exchanger 54 into which the refrigerant that has been depressurized by the pressure reducing device flows and into which heat is exchanged between the flowing-in refrigerant and the heat-source-side heat medium, and the refrigerant that has undergone heat exchange in the heat-source-side heat exchanger 54 is compressed by the compressor 11 and is then transferred to the heat-source-side heat exchanger 54.
  • a compressor 11 that compresses a refrigerant
  • the refrigerant flowing into the heat exchanger 54 is in a gas-liquid two-phase state
  • the heat source side heat exchanger 54 is configured to include a refrigerant flow path portion 93 that forms a flow path in which the refrigerant in the gas-liquid two-phase state flows in a flow direction having a vector component perpendicular to the gravity direction, a refrigerant outlet hole portion (corresponding to the refrigerant hole 47) that is provided so that the refrigerant flowing through the refrigerant flow path portion 93 flows out and is aligned along the flow direction, a refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 83) that has a protrusion portion 48 that protrudes from the inner wall surface of the flow path of the refrigerant flow path portion 93, and a plurality of heat transfer tubes (corresponding to the flat tubes 4) through which the refrigerant flowing out of the refrigerant outlet hole portion of the refrigerant distributor flows.
  • the refrigeration cycle device 80 according to include
  • the refrigeration cycle device 80 according to the fourth embodiment has an additional configuration in which the protrusion 48 is provided at the lowermost part of the inner wall surface of the flow path in the refrigerant flow path portion 93 in the vertical direction.
  • the refrigeration cycle device 80 according to the fourth embodiment has the effect of suppressing the bias of the refrigerant in the heat source side heat exchanger 54, especially when the amount of refrigerant is small.
  • the additional configuration of the refrigeration cycle device 80 according to embodiment 4 may be added to the heat source side heat exchanger 14 and the refrigerant distributor (corresponding to the gas-liquid refrigerant distributor 3) of embodiment 1.
  • the cycle devices according to embodiments 1 to 4 can be applied not only to air conditioners, but also to any equipment that uses a refrigeration cycle, such as water heaters.
  • Refrigeration cycle device 2 Gas refrigerant distributor, 3 Gas-liquid refrigerant distributor, 4 Flat tube, 4a First flat tube, 4b Second flat tube, 5 Fin, 6 Refrigeration cycle device, 7 Refrigerant hole, 8 Projection, 9 Partition, 10 Folded portion, 11 Compressor, 12 Four-way valve, 12a First connection port, 12b Second connection port, 12c Third connection port, 12d Fourth connection port, 13 Outdoor fan, 14 Heat source side heat exchanger, 15 Second expansion valve, 17 First external piping, 18 Expansion valve, 19 Indoor fan, 20 Load side heat exchanger, 21 Second external piping, 23 Outdoor unit refrigerant piping, 24 Indoor unit refrigerant piping, 27 Refrigerant hole, 28 Projection, 30 Inner tube, 31 Outer tube, 33 Refrigerant flow path portion, 34 Heat source side heat exchanger, 37 refrigerant hole, 38 protrusion, 40 refrigeration cycle device, 41 outer pipe, 43 gas-liquid refrigerant distributor, 44 heat source side heat exchanger, 47

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

Abstract

La divulgation concerne un dispositif à cycle de réfrigération avec un déséquilibre supprimé d'un fluide frigorigène liquide.　Un dispositif à cycle de réfrigération (1) selon la présente divulgation comprend un compresseur, un échangeur thermique côté charge, un dispositif de décompression et un échangeur thermique côté source de chaleur. Un fluide frigorigène soumis à un échange de chaleur par l'échangeur thermique côté source de chaleur est comprimé par le compresseur et l'état du fluide frigorigène s'écoulant dans l'échangeur thermique côté source de chaleur est un état à deux phases de gaz et de liquide. L'échangeur thermique côté source de chaleur comprend : une section de canal d'écoulement de fluide frigorigène qui forme un canal d'écoulement à travers lequel s'écoule, dans la direction d'écoulement avec une composante vectorielle de la direction perpendiculaire à la direction de gravité, le fluide frigorigène dans l'état diphasique de gaz et de liquide ; un distributeur de fluide frigorigène ayant une pluralité de trous de sortie de fluide frigorigène disposés de telle sorte que le fluide frigorigène s'écoulant à travers la section de canal d'écoulement de fluide frigorigène s'écoule vers l'extérieur et est aligné le long de la direction d'écoulement, ainsi qu'une saillie, faisant saillie à partir d'une surface de paroi interne du canal d'écoulement de la section de canal d'écoulement de fluide frigorigène ; et une pluralité de tubes de transfert de chaleur à travers lesquels s'écoule le fluide frigorigène qui s'est écoulé à partir des trous de sortie de fluide frigorigène du distributeur de fluide frigorigène.
PCT/JP2022/038548 2022-10-17 2022-10-17 Dispositif à cycle de réfrigération, échangeur thermique et distributeur de fluide frigorigène WO2024084543A1 (fr)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1798507A2 (fr) * 2005-12-13 2007-06-20 Behr GmbH & Co. KG Echangeur de chaleur, en particulier évaporateur
US20100252243A1 (en) * 2009-04-03 2010-10-07 Liu Huazhao Refrigerant distributor for heat exchanger and heat exchanger
JP2013537298A (ja) * 2010-09-13 2013-09-30 三花控股集▲団▼有限公司 冷媒導管とその冷媒導管を備えた熱交換器
JP2015203506A (ja) * 2014-04-11 2015-11-16 パナソニックＩｐマネジメント株式会社 熱交換器
WO2019239446A1 (fr) * 2018-06-11 2019-12-19 三菱電機株式会社 Unité extérieure de climatiseur et climatiseur associé
WO2021074950A1 (fr) * 2019-10-15 2021-04-22 三菱電機株式会社 Échangeur de chaleur et climatiseur recevant un échangeur de chaleur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1798507A2 (fr) * 2005-12-13 2007-06-20 Behr GmbH & Co. KG Echangeur de chaleur, en particulier évaporateur
US20100252243A1 (en) * 2009-04-03 2010-10-07 Liu Huazhao Refrigerant distributor for heat exchanger and heat exchanger
JP2013537298A (ja) * 2010-09-13 2013-09-30 三花控股集▲団▼有限公司 冷媒導管とその冷媒導管を備えた熱交換器
JP2015203506A (ja) * 2014-04-11 2015-11-16 パナソニックＩｐマネジメント株式会社 熱交換器
WO2019239446A1 (fr) * 2018-06-11 2019-12-19 三菱電機株式会社 Unité extérieure de climatiseur et climatiseur associé
WO2021074950A1 (fr) * 2019-10-15 2021-04-22 三菱電機株式会社 Échangeur de chaleur et climatiseur recevant un échangeur de chaleur

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