WO2021079422A1 - 熱交換器及び冷凍サイクル装置 - Google Patents

熱交換器及び冷凍サイクル装置 Download PDF

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Publication number
WO2021079422A1
WO2021079422A1 PCT/JP2019/041453 JP2019041453W WO2021079422A1 WO 2021079422 A1 WO2021079422 A1 WO 2021079422A1 JP 2019041453 W JP2019041453 W JP 2019041453W WO 2021079422 A1 WO2021079422 A1 WO 2021079422A1
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WIPO (PCT)
Prior art keywords
heat exchanger
heat exchangers
heat
outdoor unit
housing
Prior art date
Application number
PCT/JP2019/041453
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English (en)
French (fr)
Japanese (ja)
Inventor
直渡 原
洋次 尾中
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2021553196A priority Critical patent/JP7158601B2/ja
Priority to PCT/JP2019/041453 priority patent/WO2021079422A1/ja
Publication of WO2021079422A1 publication Critical patent/WO2021079422A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • 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

  • the present invention relates to a heat exchanger and a refrigeration cycle device including a plurality of heat exchangers having a plurality of flat tubes extending in the vertical direction.
  • a heat exchanger having a plurality of flat tubes extending in the vertical direction, a gas header connected to the lower end of the heat exchanger and extending in the horizontal direction, and a gas header connected to the upper end of the heat exchanger in the horizontal direction.
  • Heat exchangers comprising an elongated liquid header are known (see, eg, Patent Document 1).
  • the liquid refrigerant does not easily rise in the plurality of flat pipes extending in the vertical direction during low flow rate heating, and the distribution of the refrigerant from the liquid header to the plurality of flat pipes is not stable. ..
  • uneven frost is generated during low-flow heating, residual frost is generated after defrosting operation in places where the amount of frost is large, and heat exchange capacity cannot be exhibited in places where residual frost is generated, resulting in heating capacity. descend.
  • the above-mentioned problems are solved, and a flooding phenomenon that raises the liquid refrigerant in a flat tube extending in the vertical direction can occur, the liquid refrigerant easily rises, and the original heating capacity is exhibited without any trouble. It is an object of the present invention to provide a heat exchanger and a refrigeration cycle device capable of providing the same.
  • the heat exchanger according to the present invention includes a heat exchanger having a plurality of flat tubes extending in the vertical direction, a gas header connected to the lower end of the heat exchanger and extending in the horizontal direction, and the heat exchanger.
  • a liquid header connected and extending in the horizontal direction is provided, and the heat exchanger is arranged at an angle ⁇ with respect to the upward vertical direction starting from the extending horizontal direction of the gas header. Satisfying 0 ° ⁇ ⁇ 90 °, C is a flooding constant [-] that is a reference for causing a flooding phenomenon that raises the liquid refrigerant in a flat tube extending in the vertical direction, and ⁇ L is the liquid density [kg].
  • ⁇ G is the gas density [kg / m 3 ]
  • g is the gravitational acceleration [m / s 2 ]
  • D is the hydraulic diameter [m]
  • v L is the liquid velocity.
  • the refrigeration cycle device includes the above heat exchanger.
  • the heat exchanger is tilted by an angle ⁇ .
  • the parameter that affects the flooding phenomenon that raises the liquid refrigerant in the plurality of flat tubes extending in the vertical direction is not the gravitational acceleration g that affects the vertically extending flat tubes, but is tilted by an angle ⁇ .
  • the gravitational acceleration g ⁇ cos ⁇ that affects the flat tube will be included. Therefore, it becomes easy to set a large flooding constant C of 1.5 or more, which is a reference for generating a flooding phenomenon in which the liquid refrigerant is raised in the flat tube extending in the vertical direction. Therefore, a flooding phenomenon that raises the liquid refrigerant can occur in the flat pipe extending in the vertical direction, the liquid refrigerant tends to rise, and the original heating capacity can be exhibited without any trouble.
  • FIG. It is a refrigerant circuit diagram which shows the air conditioner which concerns on Embodiment 1.
  • FIG. It is the schematic which shows the heat exchanger which concerns on Embodiment 1.
  • FIG. It is the schematic which shows the plurality of flat tubes and fins which concerns on Embodiment 1.
  • FIG. It is a figure which shows the relationship between the refrigerant flow rate, the hydraulic diameter in a flat pipe, and a flooding constant which concerns on Embodiment 1.
  • FIG. It is the schematic which shows the heat exchanger which concerns on the modification 1 of Embodiment 1.
  • FIG. It is the schematic which shows the heat exchanger of the prior art.
  • FIG. It is a schematic diagram which shows various heat exchangers functioning as a condenser of the prior art. It is a schematic diagram which shows various heat exchangers functioning as a condenser which concerns on Embodiment 1.
  • FIG. It is a schematic diagram which shows various heat exchangers functioning as a prior art evaporator. It is a schematic diagram which shows various heat exchangers functioning as an evaporator which concerns on Embodiment 1.
  • FIG. It is a figure which shows the relationship between the time which concerns on Embodiment 1 and the amount of water on a heat exchanger. It is a figure which shows the relationship between the inclined angle of the plurality of heat exchangers which concerns on Embodiment 1 and the terminal water retention amount of a fin.
  • FIG. 16A is a perspective view showing the outdoor unit according to the third embodiment
  • FIG. 16A is a perspective view of the outdoor unit viewed from the left
  • FIG. 16B is a perspective view of the outdoor unit viewed from the right.
  • FIG. 17A is a perspective view showing the outdoor unit according to the fourth embodiment
  • FIG. 17A is a perspective view of the outdoor unit viewed from the left
  • FIG. 17B is a perspective view of the outdoor unit viewed from the right.
  • FIG. 18A is a perspective view showing the outdoor unit according to the fifth embodiment
  • FIG. 18A is a perspective view of the outdoor unit viewed from the left
  • FIG. 18B is a perspective view of the outdoor unit viewed from the right.
  • FIG. 19A is a perspective view showing the outdoor unit according to the sixth embodiment
  • FIG. 19A is a perspective view of the outdoor unit viewed from the left
  • FIG. 19B is a perspective view of the outdoor unit viewed from the right.
  • FIG. 20A is a perspective view showing the outdoor unit according to the seventh embodiment
  • FIG. 20A is a perspective view of the outdoor unit viewed from the left
  • FIG. 20B is a perspective view of the outdoor unit viewed from the right.
  • FIG. 21 (a) is a perspective view showing the outdoor unit according to the eighth embodiment
  • FIG. 21 (a) is a perspective view of the outdoor unit viewed from the left
  • FIG. 21 (b) is a perspective view of the outdoor unit viewed from the right
  • Is. 9 is a perspective view showing the outdoor unit according to the ninth embodiment
  • FIG. 22A is a perspective view of the outdoor unit viewed from the left
  • FIG. 22B is a perspective view of the outdoor unit viewed from the right.
  • Is. It is a front view which shows the indoor unit which concerns on Embodiment 10.
  • FIG. 1 is a refrigerant circuit diagram showing an air conditioner 100 according to a first embodiment of the present invention.
  • the air conditioner 100 is an example of a refrigeration cycle device including the heat exchanger 1.
  • the air conditioner 100 shown in FIG. 1 includes an outdoor unit 101 and an indoor unit 102.
  • the outdoor unit 101 and the indoor unit 102 are connected by a gas refrigerant pipe 103 and a liquid refrigerant pipe 104.
  • the outdoor unit 101 includes a compressor 105, a four-way valve 106, a heat exchanger 1, and an expansion valve 108.
  • the compressor 105 compresses and discharges the sucked refrigerant.
  • the compressor 105 may arbitrarily change the operating frequency by, for example, an inverter circuit or the like, and change the capacity for delivering the refrigerant per unit time of the compressor 105.
  • the four-way valve 106 is a valve that switches the flow of the refrigerant depending on, for example, the cooling operation and the heating operation.
  • the heat exchanger 1 exchanges heat between the refrigerant and the outdoor air.
  • the heat exchanger 1 functions as a condenser during the cooling operation to condense and liquefy the refrigerant.
  • the heat exchanger 1 functions as an evaporator during the heating operation to evaporate and vaporize the refrigerant.
  • the heat exchanger 1 is called an outdoor heat exchanger or a heat source side heat exchanger. As described above, the heat exchanger 1 is mounted on the outdoor unit 101 constituting the air conditioner 100.
  • the heat exchanger 1 may function as at least one of a condenser and an evaporator.
  • the expansion valve 108 is a flow control valve, and decompresses the refrigerant to expand it.
  • the expansion valve 108 is composed of, for example, an electronic expansion valve, the opening degree can be adjusted based on an instruction from a control device (not shown) or the like.
  • the indoor unit 102 has an indoor heat exchanger 109.
  • the indoor heat exchanger 109 exchanges heat between, for example, air to be air-conditioned and a refrigerant.
  • the indoor heat exchanger 109 functions as an evaporator during the cooling operation to evaporate and vaporize the refrigerant.
  • the indoor heat exchanger 109 functions as a condenser during the heating operation to condense and liquefy the refrigerant.
  • the flow of the refrigerant is switched by the four-way valve 106 of the outdoor unit 101, and cooling operation or heating operation can be realized.
  • FIG. 2 is a schematic view showing the heat exchanger 1 according to the first embodiment.
  • the X direction in the figure represents a horizontal direction.
  • the Y direction represents a vertical direction orthogonal to the X direction.
  • the white arrows indicate the direction of the air flow through the heat exchanger 1.
  • the heat exchanger 1 includes a plurality of heat exchangers 10, a plurality of flat tubes 3, a gas header 4, a liquid header 2, fins 6, and a folded header 5. ..
  • the heat exchanger 1 may have only one heat exchanger 10.
  • the plurality of heat exchangers 10 are lined up with a plurality of flat tubes 3 extending in the vertical direction. In FIG. 2, an example including two heat exchangers 10 is given. However, the number of heat exchangers 10 may be 3 or more. Of the plurality of heat exchangers 10, the heat exchanger 10 connected to the gas header 4 is arranged on the outermost side of the outdoor unit 101.
  • Each of the plurality of heat exchangers 10 has front and back surfaces that intersect with respect to the arrangement direction for ventilation.
  • each heat exchanger 10 has the front side of the paper surface as the front surface and the back side of the paper surface as the back surface in the direction of the white arrow.
  • the front and back surfaces of adjacent heat exchangers 10 are arranged in parallel.
  • Each of the end portions on both sides of the plurality of heat exchangers 10 orthogonal to the direction in which the heat exchangers are to be ventilated are arranged so that the plurality of heat exchangers 10 are aligned with each other when viewed from the direction in which the white arrows are arranged.
  • the heights of the upper and lower ends of the plurality of heat exchangers 10 are arranged so as to match the heights of the plurality of heat exchangers 10 when viewed from the direction in which the white arrows are arranged. Therefore, in FIG. 2, the heat exchanger 10 on the front side of the paper surface is located at the lowermost position and the heat exchanger body 10 on the back side of the paper surface is located at the uppermost position in the plurality of heat exchangers 10.
  • FIG. 3 is a schematic view showing a plurality of flat tubes 3 and fins 6 according to the first embodiment.
  • the plurality of flat pipes 3 have pipes extended in the vertical direction and arranged at intervals in the X direction.
  • the heat exchanger 1 is also called a flat tube heat exchanger.
  • the gas header 4 is connected to the lower end of the heat exchanger 10 at one end of the plurality of heat exchangers 10 on the front side of the paper surface in FIG. 2 in the alignment direction and in the X direction. It is growing to.
  • the gas header 4 extends longitudinally in the X direction and allows the refrigerant to flow in the X direction.
  • the gas header 4 is connected to one end of a plurality of flat tubes 3 arranged at intervals in the X direction.
  • the gas header 4 is connected to a refrigerant pipe that allows hot gas refrigerant to flow into the plurality of flat pipes 3 when the heat exchanger 1 functions as a condenser.
  • the liquid header 2 is connected to the lower end of the heat exchanger 10 at the other end of the plurality of heat exchangers 10 in the arrangement direction on the back side of the paper surface in FIG. 2 in the X direction. It is growing to.
  • the type of the liquid header 2 is not particularly limited.
  • the height position of the liquid header 2 can be changed as appropriate as long as it is connected to the heat exchanger 10 at the other end of the plurality of heat exchangers 10 in the arrangement direction on the back side of the paper surface in FIG. is there.
  • the liquid header 2 is connected to a refrigerant pipe that allows the liquid refrigerant to flow out to the plurality of flat pipes 3 when the heat exchanger 1 functions as a condenser.
  • the fin 6 is a corrugated fin that is folded back at intervals in the Y direction between adjacent flat tubes 3 among a plurality of flat tubes 3.
  • the fin 6 is joined to the outer tube surface of each of the plurality of flat tubes 3.
  • the fin 6 may be a plate fin or the like, and the type is not limited.
  • the fins 6 are composed of plate fins or the like, the fins 6 extend in the X direction in the same manner as the gas header 4 or the liquid header 2.
  • the folded header 5 is inserted into the upper ends of the plurality of flat tubes 3 of the two heat exchangers 10, connected to the upper ends of the two heat exchangers 10, and extends in the X direction. There is. That is, the folded header 5 folds back the refrigerant flow path formed by the plurality of flat tubes 3 between the adjacent heat exchangers 10 among the plurality of heat exchangers 10. In the folded header 5, the refrigerant flowing out from one heat exchanger 10 is merged, and the refrigerant is distributed to the other heat exchanger 10 and discharged. In FIG.
  • the refrigerant rising in the plurality of flat tubes 3 of the heat exchanger 10 on the front side of the paper surface merges, and the refrigerant is folded back into the heat exchanger 10 on the back side of the paper surface and circulates downward to the plurality of flat tubes 3. Is distributed as such.
  • the hot gas state refrigerant flows into the gas header 4.
  • the refrigerant that has flowed into the gas header 4 is sequentially distributed from the flat pipe 3 that is close to the inflowing refrigerant pipe.
  • the refrigerant is distributed from the gas header 4 to the plurality of flat pipes 3.
  • the gas-state refrigerant distributed to each flat tube 3 exchanges heat with the surrounding air via the fins 6 to become a gas-liquid two-phase state or liquid state refrigerant, and flows into the liquid header 2.
  • Refrigerants flow into the liquid header 2 from the plurality of flat tubes 3 and merge with each other.
  • the merged refrigerant passes through the refrigerant pipe to be discharged and flows out from the heat exchanger 1.
  • the plurality of heat exchangers 10 are arranged at an angle ⁇ with respect to the upward Y direction starting from the extended X direction of the gas header 4.
  • the angle ⁇ satisfies 0 ° ⁇ ⁇ 90 °.
  • the angle ⁇ satisfies 7 ° ⁇ ⁇ 90 °.
  • the heat exchanger 10 connected to the gas header 4 among the plurality of heat exchangers 10 is arranged at the lowest position in the direction of the white arrows.
  • the heat exchanger 10 connected to the gas header 4 among the plurality of heat exchangers 10 may be arranged at the uppermost position in the direction of the white arrows.
  • FIG. 4 is a diagram showing the relationship between the refrigerant flow rate, the hydraulic diameter in the flat pipe, and the flooding constant according to the first embodiment. The inventors conducted experiments or verifications to obtain the data shown in FIG.
  • C is a flooding constant [ ⁇ ] that serves as a reference for generating a flooding phenomenon that raises the liquid refrigerant in the flat pipe 3 extending in the vertical direction.
  • ⁇ L is the density of the liquid [kg / m 3 ].
  • ⁇ G is the density of the gas [kg / m 3 ].
  • g is the gravitational acceleration [m / s 2 ].
  • D is the hydraulic diameter [m].
  • v L is the liquid velocity.
  • v G is the gas velocity.
  • the refrigerant flow rate levels A to D are regions that may be used under partial load conditions of different sizes. That is, under the operating conditions under the rated conditions, a sufficient refrigerant flow rate can be obtained, and the liquid refrigerant rises with the air flow due to the flooding phenomenon, so that the liquid refrigerant does not stay.
  • the refrigerant flow rate levels A to D the refrigerant flow rate is small and the refrigerant speed without the flat tube 3 becomes low, the liquid refrigerant does not rise due to the flooding phenomenon, the liquid refrigerant stays, and the capacity is reduced accordingly. Adverse effects can occur. Therefore, the levels A to D of the refrigerant flow rate are set for each amount.
  • FIG. 5 is a schematic view showing the heat exchanger 1 according to the first modification of the first embodiment.
  • the heat exchanger 1 includes a U-shaped tube 8 that folds back a plurality of flat tubes 3 among adjacent heat exchangers 10 among the plurality of heat exchangers 10.
  • the heights of the upper and lower ends of the plurality of heat exchangers 10 are arranged so as to be staggered in order when the plurality of heat exchangers 10 are arranged and viewed from the direction. As a result, the heights of the upper and lower ends of the plurality of heat exchangers 10 are arranged at the same height from the lower end h1 to the upper end h2 by shifting the plurality of heat exchangers 10 in order when viewed from the arranging direction. ing.
  • FIG. 6 is a schematic view showing the effectiveness of the heat exchanger 1 according to the first modification of the first embodiment.
  • the heat exchanger 1 of the first embodiment is shown as a heat exchanger 1a
  • the heat exchanger 1 to be compared with the modified example 1 is shown as a heat exchanger 1b, showing the effectiveness of the modified example 1.
  • the target heat exchanger 1 is shown as the heat exchanger 1c.
  • the heat exchanger 1 of the modified example 1 is configured by the flat tube 3 having the length of the heat exchanger 1a, the heat is smaller than that of the heat exchanger 1a like the heat exchanger 1b.
  • the exchanger 1 can be formed.
  • the heat exchanger 1 can be enlarged like the heat exchanger 1c, and the heat transfer area is increased.
  • the heat exchange efficiency can be improved.
  • the overall size of the heat exchanger 1c is substantially equal to the overall size of the heat exchanger 1a, and the aggregation efficiency at the installation location is high.
  • FIG. 7 is a schematic view showing the heat exchanger 201 of the prior art. As shown in FIG. 7, the plurality of heat exchangers 10 in the heat exchanger 201 of the prior art are arranged so as not to be tilted straight in the upward Y direction starting from the extended X direction of the gas header 4.
  • FIG. 8 is a schematic view showing various heat exchangers 201 functioning as a conventional condenser.
  • the liquid refrigerant rises from the heat exchanger 10 connected to the gas header 4 in the plurality of flat tubes 3 extending in the vertical direction. It's hard to do. Therefore, the liquid refrigerant collects in the lower part of the heat exchanger 10 connected to the gas header 4 in the heat exchanger 201.
  • the heat transfer coefficient through the refrigerant flowing through the heat exchanger 201 decreases, the defrosting ability of the heat exchanger 201 decreases, the defrosting time during defrosting becomes longer, and the longer defrosting time is spent. Only the heating capacity is reduced.
  • FIG. 9 is a schematic view showing various heat exchangers 1 functioning as the condenser according to the first embodiment.
  • the liquid refrigerant can rise in a plurality of flat tubes 3 extending in the vertical direction and is connected to the gas header 4 in the heat exchanger 1. Liquid refrigerant does not collect in the lower part of the heat exchanger 10.
  • the heat transfer coefficient through the refrigerant flowing through the heat exchanger 1 can be improved, the defrosting ability of the heat exchanger 1 can be improved, the defrosting time at the time of defrosting becomes shorter than before, and the defrosting occurs. By shortening the time, the original heating capacity can be exhibited without any trouble.
  • FIG. 10 is a schematic view showing various heat exchangers 201 functioning as a prior art evaporator.
  • various heat exchangers 201 functioning as a prior art evaporator it is difficult for the liquid refrigerant to rise in the plurality of flat tubes 3 extending in the vertical direction during low flow rate heating.
  • the distribution of the refrigerant from the liquid header 2 to the plurality of flat tubes 3 is not stable.
  • uneven frost is generated during low-flow heating
  • residual frost is generated after defrosting operation in places where the amount of frost is large, and heat exchange capacity cannot be exhibited in places where residual frost is generated, resulting in heating capacity. descend.
  • FIG. 11 is a schematic view showing various heat exchangers 1 functioning as the evaporator according to the first embodiment.
  • the liquid refrigerant can rise in the plurality of flat tubes 3 extending in the vertical direction, and the refrigerant from the liquid header 2 to the plurality of flat tubes 3 can be raised. Distribution is stable. As a result, uneven frost does not occur during low-flow heating, and there are no places where the amount of frost is large and the frost is almost even. Therefore, residual frost does not occur after the defrosting operation, and the original heating capacity can be exhibited without any trouble.
  • FIG. 12 is a diagram showing the relationship between the time according to the first embodiment and the amount of water on the heat exchanger 1. As shown in FIG. 12, the amount of water on the heat exchanger 1 decreases until a predetermined time, but then changes to a steady state.
  • FIG. 13 is a diagram showing the relationship between the inclined angle ⁇ of the plurality of heat exchangers 10 according to the first embodiment and the terminal water retention amount of the fins 6.
  • the tilt angle of the heat exchanger 10 is set to 7 ° ⁇ ⁇ 90 °.
  • the tilt angle ⁇ is 3 ° or 5 °, the amount of water retained at the end of the fin 6 is increased, and experimental results have been obtained in which the effect of improving drainage is not always obtained even if the fin 6 is tilted.
  • the inclination angle ⁇ is 10 °, the amount of water retained at the end of the fin 6 is reduced, and the experimental result that the effect of improving the drainage property is surely obtained has been obtained.
  • the tilt angle ⁇ which is a state in which the component parallel to the fin surface is large among the gravitational components of the tilt angle ⁇ , is set.
  • the state of 7 ° is set as the critical value.
  • the tilt angle ⁇ of the heat exchanger 10 exceeds 90 °, the heat exchanger 1 is not in a realistic installation state.
  • a state in which the tilt angle ⁇ that satisfies the practical installation state of the heat exchanger 1 is 90 ° is set as the critical value.
  • the surface of the fin 6 is tilted by 7 ° or more with respect to the horizontal direction, the moisture on the surface of the fin 6 is less likely to stay, the drainage property is improved, the freezing of the residual water during heating is suppressed, and the heating capacity is increased. improves.
  • FIG. 14 is a diagram showing the effect of the heat exchanger 1 according to the first embodiment.
  • an effect 1 As shown in FIG. 14, as a result of satisfying 0 ° ⁇ ⁇ 90 ° for the angle ⁇ , as an effect 1, a flooding phenomenon that raises the liquid refrigerant in the flat tube 3 extending in the vertical direction can occur, and the liquid can be generated. The refrigerant tends to rise, and the original heating capacity can be exhibited without any trouble.
  • the effect 2 is that the surface of the fin 6 is tilted by 7 ° or more with respect to the horizontal direction, the water on the surface of the fin 6 is less likely to stay, and the drainage property is improved. However, freezing of residual water during heating is suppressed, and heating capacity is improved.
  • the heat exchanger 1 includes a plurality of heat exchangers 10 arranged side by side with a plurality of flat tubes 3 extending in the vertical direction.
  • the heat exchanger 1 includes a gas header 4 connected to the lower end of the heat exchanger 10 at one end in the alignment direction among the plurality of heat exchangers 10 and extending in the X direction.
  • the heat exchanger 1 includes a liquid header 2 connected to the heat exchanger 10 at the other end of the plurality of heat exchangers 10 in the alignment direction and extending in the X direction.
  • the plurality of heat exchangers 10 are arranged at an angle ⁇ with respect to the upward Y direction, which is the upward vertical direction, starting from the extended X direction of the gas header 4.
  • the angle ⁇ satisfies 0 ° ⁇ ⁇ 90 °.
  • C is a flooding constant [ ⁇ ] that serves as a reference for generating a flooding phenomenon that raises the liquid refrigerant in the flat tube 3 extending in the vertical direction.
  • ⁇ L is the density of the liquid [kg / m 3 ].
  • ⁇ G is the density of the gas [kg / m 3 ].
  • g is the gravitational acceleration [m / s 2 ].
  • D is the hydraulic diameter [m].
  • v L is the liquid velocity.
  • v G is the gas velocity.
  • the plurality of heat exchangers 10 are tilted by an angle ⁇ .
  • the parameter that affects the flooding phenomenon that raises the liquid refrigerant in the plurality of flat tubes 3 extending in the vertical direction is not the gravitational acceleration g that affects the flat tubes 3 extending in the Y direction, but only the angle ⁇ .
  • the gravitational acceleration g ⁇ cos ⁇ that affects the tilted flat tube 3 is included. Therefore, it becomes easy to set a large flooding constant C of 1.5 or more, which is a reference for generating a flooding phenomenon in which the liquid refrigerant is raised in the flat pipe 3 extending in the vertical direction. Therefore, a flooding phenomenon that raises the liquid refrigerant can occur in the flat pipe 3 extending in the vertical direction, the liquid refrigerant tends to rise, and the original heating capacity can be exhibited without any trouble.
  • the liquid refrigerant can rise in the plurality of flat tubes 3 extending in the vertical direction, and the liquid refrigerant does not collect in the lower part of the heat exchanger 1.
  • the heat transfer coefficient through the refrigerant flowing through the heat exchanger 1 can be improved, the defrosting ability of the heat exchanger 1 can be improved, the defrosting time at the time of defrosting becomes shorter than before, and the defrosting occurs. By shortening the time, the original heating capacity can be exhibited without any trouble.
  • the liquid refrigerant can rise in the plurality of flat pipes 3 extending in the vertical direction, and the distribution of the refrigerant from the liquid header 2 to the plurality of flat pipes 3 is stable.
  • uneven frost does not occur during low-flow heating, and there are no places where the amount of frost is large and the frost is almost even. Therefore, residual frost does not occur after the defrosting operation, and the original heating capacity can be exhibited without any trouble.
  • a plurality of heat exchangers 10 are provided.
  • the angle ⁇ is an angle at which the heat exchanger 10 connected to the gas header 4 among the plurality of heat exchangers 10 is arranged at the lowest position in the arrangement direction of the white arrows in FIG.
  • the liquid refrigerant rises in the flat pipe 3 extending in the vertical direction in the plurality of heat exchangers 10 due to the flooding phenomenon in which the liquid refrigerant rises in the flat pipe 3 extending in the vertical direction. Repeat the descent.
  • the liquid refrigerant is the heat arranged at the highest position in the direction of the white arrows in FIG. 2 among the plurality of heat exchangers 10 from the gas header 4 located at the lower part of the heat exchanger 10 at the lowest position. It can be distributed to the liquid header 2 connected to the exchanger 10.
  • the angle ⁇ satisfies 7 ° ⁇ ⁇ 90 °.
  • the surface of the fin 6 is tilted by 7 ° or more with respect to the horizontal direction, the moisture on the surface of the fin 6 is less likely to stay, the drainage property is improved, and the freezing of the residual water during heating is suppressed.
  • the heating capacity is improved.
  • the fin 6 is a corrugated fin.
  • the fin 6 the drainage property is improved, the freezing of the residual water during heating is suppressed, and the heating capacity can be improved.
  • the heat exchanger 1 functions as at least one of a condenser and an evaporator.
  • the heat exchanger 1 when the heat exchanger 1 functions as a condenser during defrosting, the liquid refrigerant can rise in the plurality of flat tubes 3 extending in the vertical direction, and the liquid refrigerant is below the heat exchanger 1. Does not collect.
  • the heat transfer coefficient through the refrigerant flowing through the heat exchanger 1 can be improved, the defrosting ability of the heat exchanger 1 can be improved, the defrosting time at the time of defrosting becomes shorter than before, and the defrosting occurs. By shortening the time, the original heating capacity can be exhibited without any trouble.
  • the heat exchanger 1 when the heat exchanger 1 functions as an evaporator during heating at a low flow rate, the liquid refrigerant can rise in the plurality of flat pipes 3 extending in the vertical direction, and the refrigerant from the liquid header 2 to the plurality of flat pipes 3 can be raised. Distribution is stable. As a result, uneven frost does not occur during low-flow heating, and there are no places where the amount of frost is large and the frost is almost even. Therefore, residual frost does not occur after the defrosting operation, and the original heating capacity can be exhibited without any trouble.
  • each of the plurality of heat exchangers 10 has front and back surfaces that intersect with each other in the direction of arrangement of the white arrows in FIG.
  • the front and back surfaces of adjacent heat exchangers 10 are arranged in parallel.
  • the gaps between the adjacent heat exchangers 10 are not biased and become uniform.
  • the amount of ventilation is not biased as a whole.
  • uneven frost is unlikely to occur partially.
  • each of the plurality of heat exchangers 10 is ventilated, and the plurality of heat exchangers 10 are outlined in FIG. 2 at each of the both end portions orthogonal to the arrangement direction of the white arrows in FIG. They are arranged so that they match when viewed from the direction in which the arrows are arranged.
  • each of the both end portions orthogonal to the ventilation direction of the heat exchanger 1 does not cause unevenness.
  • the configuration of the heat exchanger 1 can be simplified, and the arrangement design or the installation work becomes easy.
  • the heights of the upper and lower ends of the plurality of heat exchangers 10 are arranged so as to match the heights of the plurality of heat exchangers 10 when viewed from the direction of the white arrows in FIG. It is the height.
  • the heat exchanger 1 itself is easy to manufacture.
  • the heights of the upper and lower ends of the plurality of heat exchangers 10 are arranged so as to be shifted in order when the plurality of heat exchangers 10 are arranged in the direction of the white arrows in FIG. It is the height that was made.
  • the heat exchanger 1 can be further enlarged by the amount that the heat exchanger 1 is tilted to reduce the height, the heat transfer area can be increased, and the heat exchange efficiency can be improved.
  • the heights of the upper and lower ends of the plurality of heat exchangers 10 are the same as the plurality of heat exchangers 10 are shifted in order from the arrangement direction of the white arrows in FIG. It is the height arranged at the height.
  • the heights of the upper and lower ends of the heat exchanger 1 do not cause unevenness.
  • the configuration of the heat exchanger 1 can be simplified, and the arrangement design or the installation work becomes easy.
  • the heat exchanger 1 includes a folded header 5 that folds back a refrigerant flow path formed by a plurality of flat tubes 3 in adjacent heat exchangers 10 among the plurality of heat exchangers 10.
  • the folded header 5 once collects the refrigerants from the plurality of flat tubes 3 of the heat exchanger 10 on the upstream side and then disperses them in the plurality of flat tubes 3 of the heat exchanger 10 on the downstream side. ..
  • the state of the refrigerant flowing through the plurality of heat exchangers 10 can be easily made uniform.
  • the number of the plurality of refrigerant flow paths of the heat exchanger 1 can be increased, the lengths of the plurality of refrigerant flow paths can be shortened, the pressure loss of the heat exchanger 1 can be reduced, and the performance associated therewith can be improved.
  • the heat exchanger 1 includes a U-shaped tube 8 that folds back a plurality of flat tubes 3 among adjacent heat exchangers 10 among the plurality of heat exchangers 10.
  • the distance between each refrigerant flow path in which the refrigerant in the heat exchanger 1 is circulated can be increased, and the heat exchange efficiency can be improved.
  • the heat exchanger 1 is mounted on the outdoor unit 101 constituting the air conditioner 100.
  • the heat exchanger 1 can be arranged outdoors as at least one of a condenser and an evaporator.
  • the heat exchanger 10 connected to the gas header 4 is arranged on the outermost side of the outdoor unit 101.
  • the heat exchanger 1 when the heat exchanger 1 functions as a condenser, the high-temperature and high-pressure refrigerant flowing from the gas header 4 can efficiently exchange heat on the windward side of the outermost side of the outdoor unit 101.
  • the air conditioner 100 as a refrigeration cycle device includes a heat exchanger 1.
  • FIG. 15 is a perspective view showing the outdoor unit 101 according to the second embodiment.
  • the description of the same items as in the first embodiment is omitted, and only the characteristic portion thereof is described.
  • the outdoor unit 101 is a model having a plurality of tilted heat exchangers 10.
  • the plurality of heat exchangers 10 mounted on the outdoor unit 101 are arranged at an angle ⁇ with respect to the upward Y direction starting from the extended X direction of the gas header 4.
  • Embodiment 3. 16A and 16B are perspective views showing the outdoor unit 101 according to the third embodiment, FIG. 16A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 16B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the description of the same items as those in the first and second embodiments is omitted, and only the characteristic portions thereof are described.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on two front and back sides of the four sides of the housing. Specifically, the heat exchanger 1 is arranged on two side surfaces, that is, the front direction F side and the back direction B side in FIG.
  • the housing side surfaces 7 are arranged in the right direction R and the left direction L, respectively.
  • Each heat exchanger 1 has its upper side as a starting point and its lower side inclined toward the inside of the housing of the outdoor unit 101. Therefore, a concave space region is formed in the region of the lower body of the heat exchanger 1 in the outdoor unit 101.
  • the heat exchanger 1 has the upper side as a starting point and the lower side is inclined toward the inside of the housing of the outdoor unit 101.
  • the heat exchanger 1 can be tilted while maintaining the existing housing size.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on two front and back sides of the four sides of the housing.
  • the heat exchange efficiency of the outdoor unit 101 does not decrease even if the housing is connected to other housings other than the two front and back sides.
  • Embodiment 4. 17A and 17B are perspective views showing the outdoor unit 101 according to the fourth embodiment, FIG. 17A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 17B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the description of the same matters as those of the first embodiment, the second embodiment and the third embodiment is omitted, and only the characteristic portion thereof is described.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on two front and back sides of the four sides of the housing. Specifically, the heat exchanger 1 is arranged on two side surfaces, an R side in the right direction and an L side in the left direction in FIG.
  • the housing side surfaces 7 are arranged in the front direction F and the back direction B, respectively.
  • Each heat exchanger 1 has its upper side inclined to the outside of the housing of the outdoor unit 101 with the lower side as the starting point. Therefore, the region of the upper half of the heat exchanger 1 in the outdoor unit 101 is formed with a convex region protruding from the housing.
  • the heat exchanger 1 has its upper side inclined to the outside of the housing of the outdoor unit 101 with the lower side as the starting point.
  • the upper part of the heat exchanger 1 can be projected from the existing housing, the heat exchanger 1 can be enlarged, the heat transfer area can be increased, and the heat exchange efficiency can be improved.
  • Embodiment 5 are perspective views showing the outdoor unit 101 according to the fifth embodiment, FIG. 18A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 18B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the same items as those in the first embodiment, the second embodiment, the third embodiment and the fourth embodiment are omitted, and only the characteristic portions thereof are described.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on three side surfaces excluding one side surface out of the four side surfaces of the housing. Specifically, the heat exchanger 1 is arranged on three side surfaces in the front direction F side, the right direction R side, and the left direction L side in FIG. A side surface 7 of the housing is arranged in the back direction B.
  • Each heat exchanger 1 has its upper side as a starting point and its lower side inclined toward the inside of the housing of the outdoor unit 101. Therefore, a concave space region is formed in the region of the lower body of the heat exchanger 1 in the outdoor unit 101.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on three side surfaces excluding one side surface out of the four side surfaces of the housing.
  • the heat exchange efficiency of the outdoor unit 101 does not decrease even if the housing is connected to other housings other than the three sides.
  • Embodiment 6 19A and 19B are perspective views showing the outdoor unit 101 according to the sixth embodiment, FIG. 19A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 19B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the same items as those in the first embodiment, the second embodiment, the third embodiment, the fourth embodiment and the fifth embodiment are omitted, and only the characteristic portions thereof are described.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on three side surfaces excluding one side surface out of the four side surfaces of the housing. Specifically, the heat exchanger 1 is arranged on three side surfaces in the front direction F side, the right direction R side, and the left direction L side in FIG. A side surface 7 of the housing is arranged in the back direction B.
  • Each heat exchanger 1 has its upper side inclined to the outside of the housing of the outdoor unit 101 with the lower side as the starting point. Therefore, the region of the upper half of the heat exchanger 1 in the outdoor unit 101 is formed with a convex region protruding from the housing.
  • Embodiment 7. 20A and 20B are perspective views showing the outdoor unit 101 according to the seventh embodiment, FIG. 20A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 20B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the seventh embodiment the description of the same matters as those of the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment and the sixth embodiment is omitted, and only the characteristic portions thereof will be described. Has been done.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on three of the four side surfaces of the housing and the vertical half of the remaining one side surface. Specifically, the heat exchanger 1 is arranged on the entire three side surfaces of the front direction F side, the right direction R side, and the left direction L side in FIG.
  • the heat exchanger 1 is arranged in the vertical half on the back side B side.
  • the side surface 7 of the housing is arranged in the remaining vertical half in the back direction B.
  • Each heat exchanger 1 has its upper side inclined to the outside of the housing of the outdoor unit 101 with the lower side as the starting point. Therefore, the region of the upper half of the heat exchanger 1 in the outdoor unit 101 is formed with a convex region protruding from the housing.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on three of the four side surfaces of the housing and the vertical half of the remaining one side surface.
  • each pair of connected outdoor units 101 can be arranged in an integrated state. Further, in each heat exchanger 1, even if the upper side is inclined to the outside of the housing of the outdoor unit 101 starting from the lower side, the housing is the vertical half of one side surface other than the vertical half of the three side surfaces and the remaining one side surface. Can be connected to one housing.
  • Embodiment 8. 21 is a perspective view showing the outdoor unit 101 according to the eighth embodiment, FIG. 21A is a perspective view of the outdoor unit 101 viewed from the left L, and FIG. 21B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the description of the same matters as those of the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment, the sixth embodiment and the seventh embodiment is omitted. Only the feature parts are explained.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on all four side surfaces of the four side surfaces of the housing. Specifically, the heat exchanger 1 is arranged on the entire four side surfaces of the front direction F side, the back direction B, the right direction R side, and the left direction L side in FIG. 21.
  • Each heat exchanger 1 has its upper side as a starting point and its lower side inclined toward the inside of the housing of the outdoor unit 101. Therefore, a concave space region is formed in the region of the lower body of the heat exchanger 1 in the outdoor unit 101.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on all four side surfaces of the four side surfaces of the housing.
  • one outdoor unit 101 can maximize the heat exchange performance by itself.
  • Embodiment 9. 22 is a perspective view showing the outdoor unit 101 according to the ninth embodiment
  • FIG. 22A is a perspective view of the outdoor unit 101 viewed from the left L
  • FIG. 22B is an outdoor unit 101. Is a perspective view seen from the right direction R.
  • the same matters as those of the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment, the sixth embodiment, the seventh embodiment and the eighth embodiment will be described. Is omitted, and only its characteristic part is explained.
  • the outdoor unit 101 has a housing configured on four side surfaces.
  • the heat exchanger 1 is arranged on all four side surfaces of the four side surfaces of the housing. Specifically, the heat exchanger 1 is arranged on the entire four side surfaces of the front direction F side, the back direction B, the right direction R side, and the left direction L side in FIG. 22.
  • Each heat exchanger 1 has its upper side inclined to the outside of the housing of the outdoor unit 101 with the lower side as the starting point. Therefore, the region of the upper half of the heat exchanger 1 in the outdoor unit 101 is formed with a convex region protruding from the housing.
  • FIG. 23 is a front view showing the indoor unit 102 according to the tenth embodiment.
  • the first embodiment, the second embodiment, the third embodiment, the fourth embodiment, the fifth embodiment, the sixth embodiment, the seventh embodiment, the eighth embodiment and the ninth embodiment The explanation of the same matter is omitted, and only the characteristic part is explained.
  • the indoor unit 102 constituting the air conditioner 100 is equipped with the heat exchanger 11 as the indoor heat exchanger 109.
  • the heat exchanger 11 has the same configuration as the heat exchanger 1 of FIG. 2 shown in the first embodiment.
  • the heat exchanger 11 is smaller than the heat exchanger 1, and the length extending in the vertical direction of the plurality of flat tubes 3 in the plurality of heat exchangers 10 is shorter than that in the case where the outdoor unit 101 is mounted. ..
  • the heat exchanger 1 is mounted on the indoor unit 102 constituting the air conditioner 100.
  • a plurality of refrigerant flow paths flowing through the plurality of heat exchangers 10 can be configured, the number of the plurality of refrigerant flow paths of the heat exchanger 1 mounted on the indoor unit 102 can be increased, and a plurality of refrigerant flow paths can be increased.
  • the length of the refrigerant flow path is shortened, the pressure loss of the heat exchanger 1 can be reduced, and the performance associated therewith can be improved.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
PCT/JP2019/041453 2019-10-23 2019-10-23 熱交換器及び冷凍サイクル装置 WO2021079422A1 (ja)

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WO2022249425A1 (ja) * 2021-05-28 2022-12-01 三菱電機株式会社 熱交換器、熱交換器を備えた空気調和装置の室外機、および、空気調和装置の室外機を備えた空気調和装置
JP2024530124A (ja) * 2021-08-31 2024-08-16 浙江盾安人工環境股▲ふん▼有限公司 熱交換器

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JPH0611280A (ja) * 1992-03-11 1994-01-21 Modine Mfg Co 蒸発器又は蒸発器兼凝縮器
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JP2024530124A (ja) * 2021-08-31 2024-08-16 浙江盾安人工環境股▲ふん▼有限公司 熱交換器

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