WO2021079422A1 - Heat exchanger and refrigeration cycle apparatus - Google Patents

Heat exchanger and refrigeration cycle apparatus 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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WO
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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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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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2019/041453 priority Critical patent/WO2021079422A1/en
Priority to JP2021553196A priority patent/JP7158601B2/en
Publication of WO2021079422A1 publication Critical patent/WO2021079422A1/en

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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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Abstract

The purpose of the present invention is to provide a heat exchanger and a refrigeration cycle apparatus capable of generating a flooding phenomenon in which a liquid refrigerant is moved upward in flat tubes extending in a vertical direction, and capable of, as result of the liquid refrigerant being moved upward easily, exhibiting an inherent heating capacity without hindrance. This heat exchanger is provided with a heat exchange body having a plurality of flat tubes extended in a vertical direction, a gas header that is connected to a lower end part of the heat exchange body and that extends in a horizontal direction, and a liquid header that is connected to the heat exchange body and that extends in a horizontal direction. The heat exchange body is disposed to be inclined by an angle θ with respect to the upward vertical direction when the horizontal direction in which the gas header extends is defined as a start point; the angle θ satisfies 0°<θ<90°. A predetermined formula is satisfied and C≥1.5 is satisfied when C represents a flooding constant [-] that serves as a reference for generating the flooding phenomenon in which the liquid refrigerant is moved upward in the flat tubes extending in the up-down direction, ρL represents a liquid density [kg/m3], ρG represents gas density [kg/m3], g represents a gravitational acceleration [m/s2], D represents a hydraulic diameter [m], vL represents a liquid velocity, and vG represents a gas velocity.

Description

熱交換器及び冷凍サイクル装置Heat exchanger and refrigeration cycle equipment
　本発明は、上下方向に伸びた複数の扁平管を有する複数の熱交換体を備える熱交換器及び冷凍サイクル装置に関する。 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.
　従来、上下方向に伸びた複数の扁平管を有する熱交換体と、熱交換体の下端部に接続されて水平方向に伸びたガスヘッダーと、熱交換体の上端部に接続されて水平方向に伸びた液ヘッダーと、を備える熱交換器が知られている（たとえば、特許文献１参照）。 Conventionally, 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).
特開２０００－１５４９８９号公報Japanese Unexamined Patent Publication No. 2000-154989
　特許文献１の熱交換器では、除霜時に、上下方向に伸びた複数の扁平管内にて液冷媒が上昇し難く、熱交換器の下部には液冷媒が溜まる。これにより、熱交換器を流通する冷媒を通しての熱伝達率が低下し、熱交換器の除霜能力が低下し、除霜時の除霜時間が長くなり、長い除霜時間を費やす分だけ暖房能力が低下する。 In the heat exchanger of Patent Document 1, when defrosting, the liquid refrigerant does not easily rise in the plurality of flat tubes extending in the vertical direction, and the liquid refrigerant collects in the lower part of the heat exchanger. As a result, the heat transfer coefficient through the refrigerant flowing through the heat exchanger decreases, the defrosting capacity of the heat exchanger decreases, the defrosting time during defrosting becomes longer, and heating is performed by the amount of the longer defrosting time. Ability is reduced.
　また、特許文献１の熱交換器では、低流量の暖房時に、上下方向に伸びた複数の扁平管内にて液冷媒が上昇し難く、液ヘッダーから複数の扁平管への冷媒の分配が安定しない。これにより、低流量の暖房時に偏着霜が生じ、着霜量が多い箇所にて除霜運転後に残霜が生じ、残霜が生じた箇所にて熱交換能力が発揮できずに暖房能力が低下する。 Further, in the heat exchanger of 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. .. As a result, 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.
　本発明では、上記課題が解決されるものであり、上下方向に伸びた扁平管内にて液冷媒を上昇させるフラッディング現象が発生でき、液冷媒が上昇し易くなり、本来の暖房能力が支障なく発揮できる熱交換器及び冷凍サイクル装置を提供することが目的である。 In the present invention, 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.
　本発明に係る熱交換器は、上下方向に伸びた複数の扁平管を有する熱交換体と、前記熱交換体の下端部に接続されて水平方向に伸びたガスヘッダーと、前記熱交換体に接続されて水平方向に伸びた液ヘッダーと、を備え、前記熱交換体は、前記ガスヘッダーの伸びた水平方向を起点として上向き鉛直方向に対して角度θ傾けて配置され、前記角度θは、０°＜θ＜９０°を満たし、Ｃが上下方向に伸びた扁平管内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数［－］であり、ρＬが液体の密度［ｋｇ／ｍ３］であり、ρＧが気体の密度［ｋｇ／ｍ３］であり、ｇが重力加速度［ｍ／ｓ２］であり、Ｄが水力直径［ｍ］であり、ｖＬが液速度であり、ｖＧが気体速度であるとき、
Figure JPOXMLDOC01-appb-M000004
Figure JPOXMLDOC01-appb-M000005
Figure JPOXMLDOC01-appb-M000006
 　上記式（１）、式（２）及び式（３）が満たされるとともに、Ｃ≧１．５が満たされるものである。 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 θ with respect to the upward vertical direction starting from the extending horizontal direction of the gas header. Satisfying 0 ° <θ <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 ρ L is the liquid density [kg]. / M 3 ], ρ G is the gas density [kg / m 3 ], g is the gravitational acceleration [m / s 2 ], D is the hydraulic diameter [m], and v L is the liquid velocity. And when v G is the gas velocity,
Figure JPOXMLDOC01-appb-M000004
Figure JPOXMLDOC01-appb-M000005
Figure JPOXMLDOC01-appb-M000006
 The above equations (1), (2) and (3) are satisfied, and C ≧ 1.5 is satisfied.
　本発明に係る冷凍サイクル装置は、上記の熱交換器を備えるものである。 The refrigeration cycle device according to the present invention includes the above heat exchanger.
　本発明に係る熱交換器及び冷凍サイクル装置によれば、熱交換体が角度θだけ傾けられている。これにより、上下方向に伸びた複数の扁平管内にて液冷媒を上昇させるフラッディング現象に影響するパラメーターには、鉛直に伸びた扁平管に影響を与える重力加速度ｇではなく、角度θだけ傾けられた扁平管に影響を与える重力加速度ｇ×ｃｏｓθが含まれることになる。そのため、上下方向に伸びた扁平管内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数Ｃが１．５以上に大きく設定し易くなる。したがって、上下方向に伸びた扁平管内にて液冷媒を上昇させるフラッディング現象が発生でき、液冷媒が上昇し易くなり、本来の暖房能力が支障なく発揮できる。 According to the heat exchanger and the refrigeration cycle apparatus according to the present invention, the heat exchanger is tilted by an angle θ. As a result, 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 θ. The gravitational acceleration g × cos θ 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.
実施の形態１に係る空気調和装置を示す冷媒回路図である。It is a refrigerant circuit diagram which shows the air conditioner which concerns on Embodiment 1. FIG. 実施の形態１に係る熱交換器を示す概略図である。It is the schematic which shows the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態１に係る複数の扁平管とフィンとを示す概略図である。It is the schematic which shows the plurality of flat tubes and fins which concerns on Embodiment 1. FIG. 実施の形態１に係る冷媒流量と扁平管内水力直径とフラッディング定数との関係を示す図である。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. 実施の形態１の変形例１に係る熱交換器を示す概略図である。It is the schematic which shows the heat exchanger which concerns on the modification 1 of Embodiment 1. 実施の形態１の変形例１に係る熱交換器の有効性を示す概略図である。It is the schematic which shows the effectiveness of the heat exchanger which concerns on the modification 1 of Embodiment 1. FIG. 従来技術の熱交換器を示す概略図である。It is the schematic which shows the heat exchanger of the prior art. 従来技術の凝縮器として機能する種々の熱交換器を示す概略図である。It is a schematic diagram which shows various heat exchangers functioning as a condenser of the prior art. 実施の形態１に係る凝縮器として機能する種々の熱交換器を示す概略図である。It is a schematic diagram which shows various heat exchangers functioning as a condenser which concerns on Embodiment 1. FIG. 従来技術の蒸発器として機能する種々の熱交換器を示す概略図である。It is a schematic diagram which shows various heat exchangers functioning as a prior art evaporator. 実施の形態１に係る蒸発器として機能する種々の熱交換器を示す概略図である。It is a schematic diagram which shows various heat exchangers functioning as an evaporator which concerns on Embodiment 1. FIG. 実施の形態１に係る時間と熱交換器上の水分量との関係を示す図である。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. 実施の形態１に係る複数の熱交換体の傾斜した角度とフィンの終端保水量との関係を示す図である。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. 実施の形態１に係る熱交換器の効果を示す図である。It is a figure which shows the effect of the heat exchanger which concerns on Embodiment 1. FIG. 実施の形態２に係る室外機を示す斜視図である。It is a perspective view which shows the outdoor unit which concerns on Embodiment 2. FIG. 実施の形態３に係る室外機を示す斜視図であり、図１６（ａ）が室外機を左方向から見た斜視図であり、図１６（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 16B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態４に係る室外機を示す斜視図であり、図１７（ａ）が室外機を左方向から見た斜視図であり、図１７（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 17B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態５に係る室外機を示す斜視図であり、図１８（ａ）が室外機を左方向から見た斜視図であり、図１８（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 18B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態６に係る室外機を示す斜視図であり、図１９（ａ）が室外機を左方向から見た斜視図であり、図１９（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 19B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態７に係る室外機を示す斜視図であり、図２０（ａ）が室外機を左方向から見た斜視図であり、図２０（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 20B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態８に係る室外機を示す斜視図であり、図２１（ａ）が室外機を左方向から見た斜視図であり、図２１（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 21 (b) is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態９に係る室外機を示す斜視図であり、図２２（ａ）が室外機を左方向から見た斜視図であり、図２２（ｂ）が室外機を右方向から見た斜視図である。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, and FIG. 22B is a perspective view of the outdoor unit viewed from the right. Is. 実施の形態１０に係る室内機を示す正面図である。It is a front view which shows the indoor unit which concerns on Embodiment 10.
　以下には、図面に基づいて実施の形態が説明されている。なお、各図において、同一の符号を付したものは、同一の又はこれに相当するものであり、これは明細書の全文において共通している。また、断面図の図面においては、視認性に鑑みて適宜ハッチングが省略されている。さらに、明細書全文に示す構成要素の形態は、あくまで例示であってこれらの記載に限定されるものではない。 The embodiments are described below based on the drawings. In each figure, those having the same reference numerals are the same or equivalent thereof, and they are common in the entire text of the specification. Further, in the cross-sectional view, hatching is appropriately omitted in view of visibility. Furthermore, the forms of the components shown in the full text of the specification are merely examples and are not limited to these descriptions.
実施の形態１．
＜空気調和装置１００の構成＞
　図１は、本発明の実施の形態１に係る空気調和装置１００を示す冷媒回路図である。空気調和装置１００は、熱交換器１を備える冷凍サイクル装置の一例である。図１に示された空気調和装置１００は、室外機１０１と室内機１０２とを備える。室外機１０１と室内機１０２とは、ガス冷媒配管１０３及び液冷媒配管１０４によって接続されている。 Embodiment 1.
<Structure of air conditioner 100>
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.
　室外機１０１は、圧縮機１０５、四方弁１０６、熱交換器１及び膨張弁１０８を有する。 The outdoor unit 101 includes a compressor 105, a four-way valve 106, a heat exchanger 1, and an expansion valve 108.
　圧縮機１０５は、吸入した冷媒を圧縮して吐出する。圧縮機１０５は、たとえばインバータ回路などにより、運転周波数を任意に変化させ、圧縮機１０５の単位時間あたりの冷媒を送り出す容量を変化させても良い。 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.
　四方弁１０６は、たとえば冷房運転時と暖房運転時とによって冷媒の流れを切り換える弁である。 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.
　熱交換器１は、冷媒と室外の空気との熱交換を行う。熱交換器１は、冷房運転時に凝縮器として機能し、冷媒を凝縮して液化させる。熱交換器１は、暖房運転時に蒸発器として機能し、冷媒を蒸発させて気化させる。熱交換器１は、室外熱交換器あるいは熱源側熱交換器と呼ばれる。このように、熱交換器１は、空気調和装置１００を構成する室外機１０１に搭載されている。なお、熱交換器１は、凝縮器又は蒸発器の少なくとも一方として機能しても良い。 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.
　膨張弁１０８は、流量制御弁であり、冷媒を減圧して膨張させる。膨張弁１０８は、たとえば電子式膨張弁などで構成された場合には、図示しない制御装置などの指示に基づいて開度調整を行える。 The expansion valve 108 is a flow control valve, and decompresses the refrigerant to expand it. When 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.
　室内機１０２は、室内熱交換器１０９を有する。室内熱交換器１０９は、たとえば空調対象の空気と冷媒との熱交換を行う。室内熱交換器１０９は、冷房運転時に蒸発器として機能し、冷媒を蒸発させて気化させる。室内熱交換器１０９は、暖房運転時に凝縮器として機能し、冷媒を凝縮して液化させる。 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.
　以上のように空気調和装置１００を構成することにより、室外機１０１の四方弁１０６によって冷媒の流れが切り換えられ、冷房運転又は暖房運転が実現できる。 By configuring the air conditioner 100 as described above, 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.
＜熱交換器１の構成＞
　図２は、実施の形態１に係る熱交換器１を示す概略図である。以下、図中のＸ方向は、水平方向を表す。Ｙ方向は、Ｘ方向に直交した鉛直方向を表す。白抜きの矢印は、熱交換器１を通過する空気の流れの方向を示す。 <Structure of heat exchanger 1>
FIG. 2 is a schematic view showing the heat exchanger 1 according to the first embodiment. Hereinafter, 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.
　図２に示されるように、熱交換器１は、複数の熱交換体１０と、複数の扁平管３と、ガスヘッダー４と、液ヘッダー２と、フィン６と、折り返しヘッダー５と、を備える。なお、熱交換器１は、熱交換体１０を１つだけ有しても良い。 As shown in FIG. 2, 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.
　複数の熱交換体１０は、上下方向に伸びた複数の扁平管３をそれぞれ有して並んでいる。図２では、２つの熱交換体１０を備える例が挙げられている。しかし、熱交換体１０の数は、３つ以上でも良い。複数の熱交換体１０のうちガスヘッダー４に接続された熱交換体１０は、室外機１０１の最外部側に配置されている。 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.
　複数の熱交換体１０のそれぞれは、通風させる並び方向に対して交差する表裏面を有する。図２では、各熱交換体１０が白抜きの矢印の方向に紙面手前側を表面とし、紙面奥側を裏面として有する。複数の熱交換体１０は、隣り合う熱交換体１０同士の対向する表裏面を平行に配置されている。 Each of the plurality of heat exchangers 10 has front and back surfaces that intersect with respect to the arrangement direction for ventilation. In FIG. 2, 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. In the plurality of heat exchangers 10, the front and back surfaces of adjacent heat exchangers 10 are arranged in parallel.
　複数の熱交換体１０のそれぞれの通風させる並び方向に直交する両側端部のそれぞれは、複数の熱交換体１０を白抜き矢印の並び方向から見て一致させて配置されている。複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を白抜き矢印の並び方向から見て一致させて配置されている。このため、複数の熱交換体１０は、図２では紙面手前側の熱交換体１０が最下方に位置し、紙面奥側の熱交換体１０が最上方に位置している。 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.
　図３は、実施の形態１に係る複数の扁平管３とフィン６とを示す概略図である。図２及び図３に示されるように、複数の扁平管３は、上下方向向に配管を延伸させ、Ｘ方向に間隔をあけて並ぶ。このように、伝熱管に扁平管３を用いているので、熱交換器１が扁平管熱交換器とも呼ばれる。 FIG. 3 is a schematic view showing a plurality of flat tubes 3 and fins 6 according to the first embodiment. As shown in FIGS. 2 and 3, the plurality of flat pipes 3 have pipes extended in the vertical direction and arranged at intervals in the X direction. As described above, since the flat tube 3 is used for the heat transfer tube, the heat exchanger 1 is also called a flat tube heat exchanger.
　図２に示されるように、ガスヘッダー４は、複数の熱交換体１０のうち図２の紙面手前側である並び方向の一方の端部の熱交換体１０の下端部に接続されてＸ方向に伸びている。ガスヘッダー４は、Ｘ方向に長手に伸び、Ｘ方向に冷媒を流通させる。ガスヘッダー４は、Ｘ方向に間隔をあけて並ぶ複数の扁平管３の一方の端部に接続されている。ガスヘッダー４は、熱交換器１が凝縮器として機能したときに、複数の扁平管３に対してホットガス冷媒を流入させる冷媒配管に接続されている。 As shown in FIG. 2, 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.
　図２に示されるように、液ヘッダー２は、複数の熱交換体１０のうち図２の紙面奥側である並び方向の他方の端部の熱交換体１０の下端部に接続されてＸ方向に伸びている。液ヘッダー２の種類は、特に限定されるものではない。なお、液ヘッダー２は、複数の熱交換体１０のうち図２の紙面奥側である並び方向の他方の端部の熱交換体１０に接続されていれば、高さ位置は適宜変更自在である。液ヘッダー２は、熱交換器１が凝縮器として機能したときに、複数の扁平管３に対して液冷媒を流出させる冷媒配管に接続されている。 As shown in FIG. 2, 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.
　図２及び図３に示されるように、フィン６は、複数の扁平管３のうち隣り合う扁平管３の間にＹ方向に間隔をあけて折り返されたコルゲートフィンである。フィン６は、複数の扁平管３のそれぞれの外管表面と接合されている。なお、フィン６は、プレートフィンなどでも良く、種類を限定されるものではない。フィン６は、プレートフィンなどで構成された場合には、Ｘ方向にガスヘッダー４又は液ヘッダー２と同等に延びている。 As shown in FIGS. 2 and 3, 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. When 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.
　図２に示されるように、折り返しヘッダー５は、２つの熱交換体１０の複数の扁平管３の上端部を挿入され、２つの熱交換体１０の上端部に接続されてＸ方向に伸びている。つまり、折り返しヘッダー５は、複数の熱交換体１０のうち隣り合う熱交換体１０同士における複数の扁平管３によって形成される冷媒流路を折り返す。折り返しヘッダー５では、一方の熱交換体１０から流出した冷媒が合流され、他方の熱交換体１０に冷媒を分配して流出させる。図２では、紙面手前側の熱交換体１０の複数の扁平管３を上昇する冷媒が合流し、紙面奥側の熱交換体１０に冷媒が折り返されて複数の扁平管３に下方に流通するように分配される。 As shown in FIG. 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. 2, 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.
＜凝縮器である熱交換器１の動作＞
　ホットガス状態の冷媒は、ガスヘッダー４に流入する。ガスヘッダー４に流入した冷媒は、流入する冷媒配管に近い扁平管３から順次、分配されて行く。これにより、冷媒は、ガスヘッダー４から複数の扁平管３に分配される。各扁平管３に分配されたガス状態の冷媒は、フィン６を介し、周囲の空気と熱交換し、気液二相状態又は液状態の冷媒になり、液ヘッダー２に流入する。液ヘッダー２には、複数の扁平管３から冷媒が流入して合流する。合流した冷媒は、流出させる冷媒配管を通り、熱交換器１から流出する。 <Operation of heat exchanger 1 which is a condenser>
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. As a result, 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.
＜複数の熱交換体１０の詳細＞
　図２に示されるように、複数の熱交換体１０は、ガスヘッダー４の伸びたＸ方向を起点として上向きＹ方向に対して角度θ傾けて配置されている。角度θは、０°＜θ＜９０°を満たしている。ここで、角度θは、７°＜θ＜９０°を満たすとより良い。角度θは、複数の熱交換体１０のうちガスヘッダー４に接続された熱交換体１０を白抜き矢印の並び方向にて最下位置に配置させている。なお、角度θは、複数の熱交換体１０のうちガスヘッダー４に接続された熱交換体１０を白抜き矢印の並び方向にて最上位置に配置させても良い。 <Details of the plurality of heat exchangers 10>
As shown in FIG. 2, the plurality of heat exchangers 10 are arranged at an angle θ with respect to the upward Y direction starting from the extended X direction of the gas header 4. The angle θ satisfies 0 ° <θ <90 °. Here, it is better that the angle θ satisfies 7 ° <θ <90 °. With respect to the angle θ, 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. As for the angle θ, 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.
　図４は、実施の形態１に係る冷媒流量と扁平管内水力直径とフラッディング定数との関係を示す図である。発明者らは、実験あるいは検証を行い、図４に示されるデータを得た。 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.
　図４のデータから次のようなパラメーター関係が得られた。ここで、Ｃは、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数［－］である。ρＬは、液体の密度［ｋｇ／ｍ３］である。ρＧは、気体の密度［ｋｇ／ｍ３］である。ｇは、重力加速度［ｍ／ｓ２］である。Ｄは、水力直径［ｍ］である。ｖＬは、液速度である。ｖＧは、気体速度である。このとき、以下の式（４）、式（５）及び式（６）が満たされる。そして、フラッディング定数であるＣでは、Ｃ≧１．５が満たされる。 The following parameter relationships were obtained from the data in FIG. Here, 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. ρ L is the density of the liquid [kg / m 3 ]. ρ 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. At this time, the following equations (4), (5) and (6) are satisfied. Then, in C, which is a flooding constant, C ≧ 1.5 is satisfied.
Figure JPOXMLDOC01-appb-M000007
Figure JPOXMLDOC01-appb-M000007
Figure JPOXMLDOC01-appb-M000008
Figure JPOXMLDOC01-appb-M000008
Figure JPOXMLDOC01-appb-M000009
Figure JPOXMLDOC01-appb-M000009
　以上のパラメーター関係によれば、図４に示されるように、水力直径Ｄがψ９のときには、冷媒流量がレベルＤの少量以上でＣ≧１．５が満たされ、フラッディング現象が生じ、液冷媒が上昇する。また、水力直径Ｄがψ１２のときには、冷媒流量がレベルＣより多量かつレベルＢより少量以上でＣ≧１．５が満たされ、フラッディング現象が生じ、液冷媒が上昇する。さらに、水力直径Ｄがψ１４のときには、冷媒流量がレベルＢより多量かつレベルＡより少量以上でＣ≧１．５が満たされ、フラッディング現象が生じ、液冷媒が上昇する。ここで、冷媒流量のレベルＡ～Ｄは、大きさの異なる部分負荷条件で使用される可能性のある領域である。つまり、定格条件での運転条件では、十分な冷媒流量が得られ、フラッディング現象により液冷媒が気流とともに上昇するため液冷媒の滞留が生じない。一方、これらの冷媒流量のレベルＡ～Ｄ領域では、冷媒流量が少なく扁平管３無いの冷媒速度が小さくなり、フラッディング現象による液冷媒の上昇が起こらず液冷媒の滞留及びそれに伴う能力の低下といった悪影響が生じ得る。このため、冷媒流量のレベルＡ～Ｄがそれぞれの量に定められている。 According to the above parameter relationship, as shown in FIG. 4, when the hydraulic diameter D is ψ9, C ≧ 1.5 is satisfied when the refrigerant flow rate is a small amount or more of the level D, a flooding phenomenon occurs, and the liquid refrigerant becomes To rise. Further, when the hydraulic diameter D is ψ12, when the refrigerant flow rate is larger than the level C and smaller than the level B or more, C ≧ 1.5 is satisfied, a flooding phenomenon occurs, and the liquid refrigerant rises. Further, when the hydraulic diameter D is ψ14, when the refrigerant flow rate is larger than the level B and smaller than the level A, C ≧ 1.5 is satisfied, a flooding phenomenon occurs, and the liquid refrigerant rises. Here, 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. On the other hand, in these 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.
＜変形例１＞
　図５は、実施の形態１の変形例１に係る熱交換器１を示す概略図である。図５に示されるように、熱交換器１は、複数の熱交換体１０のうち隣り合う熱交換体１０同士における複数の扁平管３をそれぞれ折り返すＵ字管８を備える。 <Modification example 1>
FIG. 5 is a schematic view showing the heat exchanger 1 according to the first modification of the first embodiment. As shown in FIG. 5, 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.
　複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を並び方向から見て順にずらされて配置されている。それにより、複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を並び方向から見て順にずらされて下端ｈ１から上端ｈ２までの同一高さに配置されている。 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.
　図６は、実施の形態１の変形例１に係る熱交換器１の有効性を示す概略図である。図６では、実施の形態１の熱交換器１が熱交換器１ａとして示され、変形例１の比較対象の熱交換器１が熱交換器１ｂとして示され、変形例１の有効性を示す対象の熱交換器１が熱交換器１ｃとして示される。図６に示されるように、熱交換器１ａの長さの扁平管３で変形例１の熱交換器１を構成すると、熱交換器１ｂのように熱交換器１ａに比して小型の熱交換器１が形成できる。また、熱交換器１を傾けて高さが減った分更に扁平管３の長さを上端ｈ３まで増すと、熱交換器１ｃのように熱交換器１が大型化でき、伝熱面積が増大でき、熱交換効率が向上できる。しかも、熱交換器１ｃの全体の大きさは、熱交換器１ａの全体の大きさとほぼ等しく、設置箇所での集約効率が高い。 FIG. 6 is a schematic view showing the effectiveness of the heat exchanger 1 according to the first modification of the first embodiment. In FIG. 6, the heat exchanger 1 of the first embodiment is shown as a heat exchanger 1a, and 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. As shown in FIG. 6, when 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. Further, if the length of the flat tube 3 is further increased to the upper end h3 by the amount that the heat exchanger 1 is tilted to reduce the height, 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. Moreover, 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.
＜作用及び効果＞
　図７は、従来技術の熱交換器２０１を示す概略図である。図７に示されるように、従来技術の熱交換器２０１における複数の熱交換体１０は、ガスヘッダー４の伸びたＸ方向を起点として上向きＹ方向にまっすぐ傾かずに配置されている。 <Action and effect>
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.
　図８は、従来技術の凝縮器として機能する種々の熱交換器２０１を示す概略図である。図８に示されるように、凝縮器として機能する種々の熱交換器２０１では、上下方向に伸びた複数の扁平管３内にて液冷媒がガスヘッダー４に接続された熱交換体１０から上昇し難い。このため、熱交換器２０１におけるガスヘッダー４に接続された熱交換体１０下部には液冷媒が溜まる。これにより、熱交換器２０１を流通する冷媒を通しての熱伝達率が低下し、熱交換器２０１の除霜能力が低下し、除霜時の除霜時間が長くなり、長い除霜時間を費やす分だけ暖房能力が低下する。 FIG. 8 is a schematic view showing various heat exchangers 201 functioning as a conventional condenser. As shown in FIG. 8, in various heat exchangers 201 functioning as condensers, 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. As a result, 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.
　図９は、実施の形態１に係る凝縮器として機能する種々の熱交換器１を示す概略図である。図９に示されるように、凝縮器として機能する種々の熱交換器１では、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、熱交換器１におけるガスヘッダー４に接続された熱交換体１０下部には液冷媒が溜まらない。これにより、熱交換器１を流通する冷媒を通しての熱伝達率が向上でき、熱交換器１の除霜能力が向上でき、除霜時の除霜時間が従来に比して短くなり、除霜時間の短縮化によって本来の暖房能力が支障なく発揮できる。 FIG. 9 is a schematic view showing various heat exchangers 1 functioning as the condenser according to the first embodiment. As shown in FIG. 9, in various heat exchangers 1 that function as condensers, 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. As a result, 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.
　図１０は、従来技術の蒸発器として機能する種々の熱交換器２０１を示す概略図である。図１０に示されるように、従来技術の蒸発器として機能する種々の熱交換器２０１では、低流量の暖房時に、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇し難く、液ヘッダー２から複数の扁平管３への冷媒の分配が安定しない。これにより、低流量の暖房時に偏着霜が生じ、着霜量が多い箇所にて除霜運転後に残霜が生じ、残霜が生じた箇所にて熱交換能力が発揮できずに暖房能力が低下する。 FIG. 10 is a schematic view showing various heat exchangers 201 functioning as a prior art evaporator. As shown in FIG. 10, in 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. As a result, 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.
　図１１は、実施の形態１に係る蒸発器として機能する種々の熱交換器１を示す概略図である。蒸発器として機能する種々の熱交換器１における低流量の暖房時では、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、液ヘッダー２から複数の扁平管３への冷媒の分配が安定する。これにより、低流量の暖房時に偏着霜が生じず、着霜量が多い箇所がなくほぼ均等になるので、除霜運転後に残霜が生じず、本来の暖房能力が支障なく発揮できる。 FIG. 11 is a schematic view showing various heat exchangers 1 functioning as the evaporator according to the first embodiment. During low-flow heating in various heat exchangers 1 that function as evaporators, 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.
　図１２は、実施の形態１に係る時間と熱交換器１上の水分量との関係を示す図である。図１２に示されるように、熱交換器１上の水分量は、所定時間までは減少するが、その後に定常状態に推移する。 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.
　図１３は、実施の形態１に係る複数の熱交換体１０の傾斜した角度θとフィン６の終端保水量との関係を示す図である。図１３に示されるように、たとえば、熱交換体１０の傾け角度は、７°＜θ＜９０°に設定されている。傾け角度θが３°又は５°では、フィン６の終端保水量の増大が見られ、傾けても必ずしも排水性向上の効果が得られない実験結果が得られている。また、傾け角度θが１０°では、フィン６の終端保水量の減少が見られ、排水性向上の効果が確実に得られる実験結果が得られている。このように、フィン表面の水滴の排水を向上させることが熱交換体１０の傾け角度θによって重力の成分のうちフィン表面と平行な成分が大きくなり、フィン表面から水が排水し易くなる。このため、確実な実験結果が得られた傾け角度θが１０°であることを考慮して、傾け角度θの重力の成分のうちフィン表面と平行な成分が大きくなる状態である傾け角度θが７°である状態が臨界値として設定されている。一方、熱交換体１０の傾け角度θが９０°を超えると、熱交換器１が実現的な設置状態ではなくなる。このため、熱交換器１として実現的な設置状態を満たす傾け角度θが９０°である状態が臨界値として設定されている。これにより、フィン６の表面が水平方向に対して７゜以上傾き、フィン６の表面の水分が滞留し難くなり、排水性が向上し、暖房時の残水の氷結が抑制され、暖房能力が向上する。 FIG. 13 is a diagram showing the relationship between the inclined angle θ of the plurality of heat exchangers 10 according to the first embodiment and the terminal water retention amount of the fins 6. As shown in FIG. 13, for example, the tilt angle of the heat exchanger 10 is set to 7 ° <θ <90 °. When the tilt angle θ 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. Further, when the inclination angle θ 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. In this way, improving the drainage of water droplets on the fin surface increases the component of gravity parallel to the fin surface depending on the tilt angle θ of the heat exchanger 10, and makes it easier for water to drain from the fin surface. Therefore, considering that the tilt angle θ for which reliable experimental results have been obtained is 10 °, the tilt angle θ, which is a state in which the component parallel to the fin surface is large among the gravitational components of the tilt angle θ, is set. The state of 7 ° is set as the critical value. On the other hand, when the tilt angle θ of the heat exchanger 10 exceeds 90 °, the heat exchanger 1 is not in a realistic installation state. Therefore, a state in which the tilt angle θ that satisfies the practical installation state of the heat exchanger 1 is 90 ° is set as the critical value. As a result, 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.
　図１４は、実施の形態１に係る熱交換器１の効果を示す図である。図１４に示されるように、角度θは、０°＜θ＜９０°を満たす結果、効果１として、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象が発生でき、液冷媒が上昇し易くなり、本来の暖房能力が支障なく発揮できる。角度θは、７°＜θ＜９０°を満たす結果、効果２として、フィン６の表面が水平方向に対して７゜以上傾き、フィン６の表面の水分が滞留し難くなり、排水性が向上し、暖房時の残水の氷結が抑制され、暖房能力が向上する。 FIG. 14 is a diagram showing the effect of the heat exchanger 1 according to the first embodiment. As shown in FIG. 14, as a result of satisfying 0 ° <θ <90 ° for the angle θ, 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. As a result of satisfying 7 ° <θ <90 ° for the angle θ, 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.
＜実施の形態１の効果＞
　実施の形態１によれば、熱交換器１は、上下方向に伸びた複数の扁平管３をそれぞれ有して並んだ複数の熱交換体１０を備える。熱交換器１は、複数の熱交換体１０のうち並び方向の一方の端部の熱交換体１０の下端部に接続されてＸ方向に伸びたガスヘッダー４を備える。熱交換器１は、複数の熱交換体１０のうち並び方向の他方の端部の熱交換体１０に接続されてＸ方向に伸びた液ヘッダー２を備える。複数の熱交換体１０は、ガスヘッダー４の伸びたＸ方向を起点として上向き鉛直方向である上向きＹ方向に対して角度θ傾けて配置されている。角度θは、０°＜θ＜９０°を満たしている。Ｃは、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数［－］である。ρＬは、液体の密度［ｋｇ／ｍ３］である。ρＧは、気体の密度［ｋｇ／ｍ３］である。ｇは、重力加速度［ｍ／ｓ２］である。Ｄは、水力直径［ｍ］である。ｖＬは、液速度である。ｖＧは、気体速度である。このとき、下記式（７）、式（８）及び式（９）が満たされるとともに、Ｃ≧１．５が満たされる。 <Effect of Embodiment 1>
According to the first embodiment, 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 θ 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 θ satisfies 0 ° <θ <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. ρ L is the density of the liquid [kg / m 3 ]. ρ 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. At this time, the following equations (7), (8) and (9) are satisfied, and C ≧ 1.5 is satisfied.
Figure JPOXMLDOC01-appb-M000010
Figure JPOXMLDOC01-appb-M000010
Figure JPOXMLDOC01-appb-M000011
Figure JPOXMLDOC01-appb-M000011
Figure JPOXMLDOC01-appb-M000012
Figure JPOXMLDOC01-appb-M000012
　この構成によれば、複数の熱交換体１０が角度θだけ傾けられている。また、上下方向に伸びた複数の扁平管３内にて液冷媒を上昇させるフラッディング現象に影響するパラメーターには、Ｙ方向に伸びた扁平管３に影響を与える重力加速度ｇではなく、角度θだけ傾けられた扁平管３に影響を与える重力加速度ｇ×ｃｏｓθが含まれる。そのため、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数Ｃが１．５以上に大きく設定し易くなる。したがって、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象が発生でき、液冷媒が上昇し易くなり、本来の暖房能力が支障なく発揮できる。 According to this configuration, the plurality of heat exchangers 10 are tilted by an angle θ. Further, 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 θ. The gravitational acceleration g × cos θ 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.
　すなわち、除霜時では、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、熱交換器１の下部には液冷媒が溜まらない。これにより、熱交換器１を流通する冷媒を通しての熱伝達率が向上でき、熱交換器１の除霜能力が向上でき、除霜時の除霜時間が従来に比して短くなり、除霜時間の短縮化によって本来の暖房能力が支障なく発揮できる。 That is, at the time of defrosting, 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. As a result, 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.
　また、低流量の暖房時では、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、液ヘッダー２から複数の扁平管３への冷媒の分配が安定する。これにより、低流量の暖房時に偏着霜が生じず、着霜量が多い箇所がなくほぼ均等になるので、除霜運転後に残霜が生じず、本来の暖房能力が支障なく発揮できる。 Further, at the time of low flow rate heating, 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. 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.
　実施の形態１によれば、熱交換体１０は、複数設けられている。角度θは、複数の熱交換体１０のうちガスヘッダー４に接続された熱交換体１０を図２の白抜き矢印の並び方向にて最下位置に配置させる角度である。 According to the first embodiment, a plurality of heat exchangers 10 are provided. The angle θ 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.
　この構成によれば、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象によって、液冷媒は、複数の熱交換体１０における上下方向に伸びた扁平管３内にて上昇と下降とを繰り返す。これにより、液冷媒は、最下位置の熱交換体１０の下部に位置するガスヘッダー４から複数の熱交換体１０のうち図２の白抜き矢印の並び方向にて最上位置に配置させた熱交換体１０に接続された液ヘッダー２に流通できる。 According to this configuration, 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. As a result, 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.
　実施の形態１によれば、熱交換器１では、角度θが７°＜θ＜９０°を満たしている。 According to the first embodiment, in the heat exchanger 1, the angle θ satisfies 7 ° <θ <90 °.
　この構成によれば、フィン６の表面が水平方向に対して７゜以上傾き、フィン６の表面の水分が滞留し難くなり、排水性が向上し、暖房時の残水の氷結が抑制され、暖房能力が向上する。 According to this configuration, 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.
　実施の形態１によれば、フィン６は、コルゲートフィンである。 According to the first embodiment, the fin 6 is a corrugated fin.
　この構成によれば、フィン６としては、排水性が向上して暖房時の残水の氷結が抑制されて暖房能力が向上できる。 According to this configuration, as 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.
　実施の形態１によれば、熱交換器１は、凝縮器又は蒸発器の少なくとも一方として機能する。 According to the first embodiment, the heat exchanger 1 functions as at least one of a condenser and an evaporator.
　この構成によれば、熱交換器１は、除霜時に凝縮器として機能すると、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、熱交換器１の下部には液冷媒が溜まらない。これにより、熱交換器１を流通する冷媒を通しての熱伝達率が向上でき、熱交換器１の除霜能力が向上でき、除霜時の除霜時間が従来に比して短くなり、除霜時間の短縮化によって本来の暖房能力が支障なく発揮できる。 According to this configuration, 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. As a result, 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.
　また、熱交換器１は、低流量の暖房時に蒸発器として機能すると、上下方向に伸びた複数の扁平管３内にて液冷媒が上昇でき、液ヘッダー２から複数の扁平管３への冷媒の分配が安定する。これにより、低流量の暖房時に偏着霜が生じず、着霜量が多い箇所がなくほぼ均等になるので、除霜運転後に残霜が生じず、本来の暖房能力が支障なく発揮できる。 Further, 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.
　実施の形態１によれば、複数の熱交換体１０のそれぞれは、図２の白抜き矢印の通風させる並び方向に対して交差する表裏面を有する。複数の熱交換体１０は、隣り合う熱交換体１０同士の対向する表裏面を平行に配置されている。 According to the first embodiment, 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. In the plurality of heat exchangers 10, the front and back surfaces of adjacent heat exchangers 10 are arranged in parallel.
　この構成によれば、隣り合う熱交換体１０同士のそれぞれの間の隙間が偏らずに均一になる。これにより、通風量が全体で偏らない。また、偏着霜が部分的に生じ難い。 According to this configuration, the gaps between the adjacent heat exchangers 10 are not biased and become uniform. As a result, the amount of ventilation is not biased as a whole. In addition, uneven frost is unlikely to occur partially.
　実施の形態１によれば、複数の熱交換体１０のそれぞれの通風させる図２の白抜き矢印の並び方向に直交する両側端部のそれぞれは、複数の熱交換体１０を図２の白抜き矢印の並び方向から見て一致させて配置されている。 According to the first embodiment, 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.
　この構成によれば、熱交換器１の通風方向に直交する両側端部のそれぞれは、凸凹を生じない。これにより、熱交換器１の構成が単純化でき、配置設計あるいは設置作業などが容易になる。 According to this configuration, each of the both end portions orthogonal to the ventilation direction of the heat exchanger 1 does not cause unevenness. As a result, the configuration of the heat exchanger 1 can be simplified, and the arrangement design or the installation work becomes easy.
　実施の形態１によれば、複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を図２の白抜き矢印の並び方向から見て一致させて配置された高さである。 According to the first embodiment, 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.
　この構成によれば、熱交換器１自体が製造容易である。 According to this configuration, the heat exchanger 1 itself is easy to manufacture.
　実施の形態１によれば、複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を図２の白抜き矢印の並び方向から見て順にずらされて配置された高さである。 According to the first embodiment, 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.
　この構成によれば、熱交換器１を傾けて高さが減った分更に熱交換器１が大型化でき、伝熱面積が増大でき、熱交換効率が向上できる。 According to this configuration, 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.
　実施の形態１によれば、複数の熱交換体１０のそれぞれの上下端部それぞれの高さは、複数の熱交換体１０を図２の白抜き矢印の並び方向から見て順にずらされて同一高さに配置された高さである。 According to the first embodiment, 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.
　この構成によれば、熱交換器１の上下端部それぞれの高さは、凸凹を生じない。これにより、熱交換器１の構成が単純化でき、配置設計あるいは設置作業などが容易になる。 According to this configuration, the heights of the upper and lower ends of the heat exchanger 1 do not cause unevenness. As a result, the configuration of the heat exchanger 1 can be simplified, and the arrangement design or the installation work becomes easy.
　実施の形態１によれば、熱交換器１は、複数の熱交換体１０のうち隣り合う熱交換体１０同士における複数の扁平管３によって形成される冷媒流路を折り返す折り返しヘッダー５を備える。 According to the first embodiment, 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.
　この構成によれば、折り返しヘッダー５は、上流側の熱交換体１０の複数の扁平管３からの冷媒を一旦集合させてその後に下流側の熱交換体１０の複数の扁平管３に分散させる。これにより、複数の熱交換体１０を流通する冷媒の状態が均一化され易い。また、熱交換器１の複数の冷媒流路の数が増大できるとともに、複数の冷媒流路の長さが短くなり、熱交換器１の圧力損失が低減でき、それに伴う性能が改善できる。 According to this configuration, 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. .. As a result, the state of the refrigerant flowing through the plurality of heat exchangers 10 can be easily made uniform. Further, 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.
　実施の形態１によれば、熱交換器１は、複数の熱交換体１０のうち隣り合う熱交換体１０同士における複数の扁平管３をそれぞれ折り返すＵ字管８を備える。 According to 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.
　この構成によれば、熱交換器１における冷媒を流通させる各冷媒流路の距離が稼げ、熱交換効率が向上できる。 According to this configuration, 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.
　実施の形態１によれば、熱交換器１は、空気調和装置１００を構成する室外機１０１に搭載されている。 According to the first embodiment, the heat exchanger 1 is mounted on the outdoor unit 101 constituting the air conditioner 100.
　この構成によれば、熱交換器１は、凝縮器又は蒸発器の少なくとも一方として室外に配置できる。 According to this configuration, the heat exchanger 1 can be arranged outdoors as at least one of a condenser and an evaporator.
　実施の形態１によれば、複数の熱交換体１０のうちガスヘッダー４に接続された熱交換体１０は、室外機１０１の最外部側に配置されている。 According to the first embodiment, 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.
　この構成によれば、熱交換器１が凝縮器として機能する際に、ガスヘッダー４から流入する高温高圧の冷媒が室外機１０１の最外部側の最も風上側にて効率良く熱交換できる。 According to this configuration, 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.
　実施の形態１によれば、冷凍サイクル装置としての空気調和装置１００は、熱交換器１を備える。 According to the first embodiment, the air conditioner 100 as a refrigeration cycle device includes a heat exchanger 1.
　この構成によれば、熱交換器１を備える冷凍サイクル装置としての空気調和装置１００では、上下方向に伸びた扁平管３内にて液冷媒を上昇させるフラッディング現象が発生でき、液冷媒が上昇し易くなり、本来の暖房能力が支障なく発揮できる。 According to this configuration, in the air conditioner 100 as a refrigeration cycle device including the heat exchanger 1, a flooding phenomenon that raises the liquid refrigerant in the flat pipe 3 extending in the vertical direction can occur, and the liquid refrigerant rises. It becomes easier and the original heating capacity can be exhibited without any trouble.
実施の形態２．
　図１５は、実施の形態２に係る室外機１０１を示す斜視図である。実施の形態２では、実施の形態１と同事項の説明が省略され、その特徴部分のみが説明されている。 Embodiment 2.
FIG. 15 is a perspective view showing the outdoor unit 101 according to the second embodiment. In the second embodiment, the description of the same items as in the first embodiment is omitted, and only the characteristic portion thereof is described.
　図１５に示されるように、室外機１０１は、傾いた複数の熱交換体１０を有する機種である。室外機１０１に搭載された複数の熱交換体１０は、ガスヘッダー４の伸びたＸ方向を起点として上向きＹ方向に対して角度θ傾けて配置されている。角度θは、θ＝１０°である。このため、効果２の実験結果が得られて排水性がより確実に向上できる。なお、効果２である排水性が発揮できれば、角度θは、７°＜θ＜９０°を満たせば良い。 As shown in FIG. 15, 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 θ with respect to the upward Y direction starting from the extended X direction of the gas header 4. The angle θ is θ = 10 °. Therefore, the experimental result of the effect 2 can be obtained, and the drainage property can be improved more reliably. If the drainage property, which is the effect 2, can be exhibited, the angle θ may satisfy 7 ° <θ <90 °.
実施の形態３．
　図１６は、実施の形態３に係る室外機１０１を示す斜視図であり、図１６（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図１６（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態３では、実施の形態１及び実施の形態２と同事項の説明が省略され、その特徴部分のみが説明されている。 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. In the third embodiment, the description of the same items as those in the first and second embodiments is omitted, and only the characteristic portions thereof are described.
　図１６に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち表裏の２側面に配置されている。具体的には、熱交換器１は、図１６での正面方向Ｆ側と背面方向Ｂ側との２側面に配置されている。右方向Ｒ及び左方向Ｌには、筐体側面７がそれぞれ配置されている。それぞれの熱交換器１は、上辺を起点として下辺を室外機１０１の筐体内側に傾斜させている。このため、室外機１０１における熱交換器１の下半体の領域には、凹空間領域が形成されている。 As shown in FIG. 16, 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.
＜実施の形態３の効果＞
　実施の形態３によれば、熱交換器１は、上辺を起点として下辺を室外機１０１の筐体内側に傾斜させている。 <Effect of Embodiment 3>
According to the third embodiment, 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.
　この構成によれば、既存の筐体サイズを保ちながら熱交換器１が傾けられる。 According to this configuration, the heat exchanger 1 can be tilted while maintaining the existing housing size.
　実施の形態３によれば、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち表裏の２側面に配置されている。 According to the third embodiment, 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.
　この構成によれば、筐体が表裏の２側面以外で他の筐体と連結されても、室外機１０１の熱交換効率が低下しない。 According to this configuration, 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.
実施の形態４．
　図１７は、実施の形態４に係る室外機１０１を示す斜視図であり、図１７（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図１７（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態４では、実施の形態１、実施の形態２及び実施の形態３と同事項の説明が省略され、その特徴部分のみが説明されている。 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. In the fourth embodiment, 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.
　図１７に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち表裏の２側面に配置されている。具体的には、熱交換器１は、図１７での右方向Ｒ側と左方向Ｌ側との２側面に配置されている。正面方向Ｆ及び背面方向Ｂには、筐体側面７がそれぞれ配置されている。それぞれの熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させている。このため、室外機１０１における熱交換器１の上半体の領域は、筐体よりも突出した凸領域が形成されている。 As shown in FIG. 17, 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.
＜実施の形態４の効果＞
　実施の形態４によれば、熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させている。 <Effect of Embodiment 4>
According to the fourth embodiment, 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.
　この構成によれば、既存の筐体に対して熱交換器１の上部を突き出させ、熱交換器１が大型化でき、伝熱面積が増大でき、熱交換効率が向上できる。 According to this configuration, 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.
実施の形態５．
　図１８は、実施の形態５に係る室外機１０１を示す斜視図であり、図１８（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図１８（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態５では、実施の形態１、実施の形態２、実施の形態３及び実施の形態４と同事項の説明が省略され、その特徴部分のみが説明されている。 Embodiment 5.
18A and 18B 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. In the fifth embodiment, 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.
　図１８に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち１側面を除く３側面に配置されている。具体的には、熱交換器１は、図１８での正面方向Ｆ側と右方向Ｒ側と左方向Ｌ側の３側面に配置されている。背面方向Ｂには、筐体側面７が配置されている。それぞれの熱交換器１は、上辺を起点として下辺を室外機１０１の筐体内側に傾斜させている。このため、室外機１０１における熱交換器１の下半体の領域には、凹空間領域が形成されている。 As shown in FIG. 18, 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.
＜実施の形態５の効果＞
　実施の形態５によれば、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち１側面を除く３側面に配置されている。 <Effect of Embodiment 5>
According to the fifth embodiment, 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.
　この構成によれば、筐体が３側面以外で他の筐体と連結されても、室外機１０１の熱交換効率が低下しない。 According to this configuration, 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.
実施の形態６．
　図１９は、実施の形態６に係る室外機１０１を示す斜視図であり、図１９（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図１９（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態６では、実施の形態１、実施の形態２、実施の形態３、実施の形態４及び実施の形態５と同事項の説明が省略され、その特徴部分のみが説明されている。 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. In the sixth embodiment, 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.
　図１９に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち１側面を除く３側面に配置されている。具体的には、熱交換器１は、図１９での正面方向Ｆ側と右方向Ｒ側と左方向Ｌ側の３側面に配置されている。背面方向Ｂには、筐体側面７が配置されている。それぞれの熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させている。このため、室外機１０１における熱交換器１の上半体の領域は、筐体よりも突出した凸領域が形成されている。 As shown in FIG. 19, 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.
実施の形態７．
　図２０は、実施の形態７に係る室外機１０１を示す斜視図であり、図２０（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図２０（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態７では、実施の形態１、実施の形態２、実施の形態３、実施の形態４、実施の形態５及び実施の形態６と同事項の説明が省略され、その特徴部分のみが説明されている。 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. In 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.
　図２０に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち３側面及び残り１側面の縦半分に配置されている。具体的には、熱交換器１は、図１９での正面方向Ｆ側と右方向Ｒ側と左方向Ｌ側の３側面の全体に配置されている。熱交換器１は、背面方向Ｂ側の縦半分に配置されている。背面方向Ｂの残りの縦半分には、筐体側面７が配置されている。それぞれの熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させている。このため、室外機１０１における熱交換器１の上半体の領域は、筐体よりも突出した凸領域が形成されている。 As shown in FIG. 20, 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.
＜実施の形態７の効果＞
　実施の形態７によれば、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち３側面及び残り１側面の縦半分に配置されている。 <Effect of Embodiment 7>
According to the seventh embodiment, 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.
　この構成によれば、筐体が３側面及び残り１側面の縦半分以外の１側面の縦半分で他の１つの筐体と連結されても、室外機１０１の熱交換効率が低下しない。また、連結された１対の室外機１０１ごとが集約状態で配置できる。また、それぞれの熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させても、筐体が３側面及び残り１側面の縦半分以外の１側面の縦半分で他の１つの筐体と連結できる。 According to this configuration, the heat exchange efficiency of the outdoor unit 101 does not decrease even if the housing is connected to the other housing at the vertical half of one side surface other than the vertical half of the three side surfaces and the remaining one side surface. Further, 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.
実施の形態８．
　図２１は、実施の形態８に係る室外機１０１を示す斜視図であり、図２１（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図２１（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態８では、実施の形態１、実施の形態２、実施の形態３、実施の形態４、実施の形態５、実施の形態６及び実施の形態７と同事項の説明が省略され、その特徴部分のみが説明されている。 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. In the eighth 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, the sixth embodiment and the seventh embodiment is omitted. Only the feature parts are explained.
　図２１に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち４側面全部に配置されている。具体的には、熱交換器１は、図２１での正面方向Ｆ側と背面方向Ｂと右方向Ｒ側と左方向Ｌ側の４側面の全体に配置されている。それぞれの熱交換器１は、上辺を起点として下辺を室外機１０１の筐体内側に傾斜させている。このため、室外機１０１における熱交換器１の下半体の領域には、凹空間領域が形成されている。 As shown in FIG. 21, 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.
＜実施の形態８の効果＞
　実施の形態８によれば、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち４側面全部に配置されている。 <Effect of Embodiment 8>
According to the eighth embodiment, 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.
　この構成によれば、１つの室外機１０１が単独で熱交換性能を最大限に発揮できる。 According to this configuration, one outdoor unit 101 can maximize the heat exchange performance by itself.
実施の形態９．
　図２２は、実施の形態９に係る室外機１０１を示す斜視図であり、図２２（ａ）が室外機１０１を左方向Ｌから見た斜視図であり、図２２（ｂ）が室外機１０１を右方向Ｒから見た斜視図である。実施の形態９では、実施の形態１、実施の形態２、実施の形態３、実施の形態４、実施の形態５、実施の形態６、実施の形態７及び実施の形態８と同事項の説明が省略され、その特徴部分のみが説明されている。 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, and FIG. 22B is an outdoor unit 101. Is a perspective view seen from the right direction R. In the ninth embodiment, 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.
　図２２に示されるように、室外機１０１は、４側面に構成された筐体を有する。熱交換器１は、筐体の４側面のうち４側面全部に配置されている。具体的には、熱交換器１は、図２２での正面方向Ｆ側と背面方向Ｂと右方向Ｒ側と左方向Ｌ側の４側面の全体に配置されている。それぞれの熱交換器１は、下辺を起点として上辺を室外機１０１の筐体外側に傾斜させている。このため、室外機１０１における熱交換器１の上半体の領域は、筐体よりも突出した凸領域が形成されている。 As shown in FIG. 22, 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.
実施の形態１０．
　図２３は、実施の形態１０に係る室内機１０２を示す正面図である。実施の形態１０では、実施の形態１、実施の形態２、実施の形態３、実施の形態４、実施の形態５、実施の形態６、実施の形態７、実施の形態８及び実施の形態９と同事項の説明が省略され、その特徴部分のみが説明されている。 Embodiment 10.
FIG. 23 is a front view showing the indoor unit 102 according to the tenth embodiment. In 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.
　図２３に示されるように、空気調和装置１００を構成する室内機１０２には、室内熱交換器１０９として熱交換器１１が搭載されている。ここで、熱交換器１１は、実施の形態１に示された図２の熱交換器１の構成と同様である。ただし、熱交換器１１が熱交換器１よりも小型であり、複数の熱交換体１０における複数の扁平管３の上下方向に伸びる長さが室外機１０１に搭載される場合に比して短い。 As shown in FIG. 23, the indoor unit 102 constituting the air conditioner 100 is equipped with the heat exchanger 11 as the indoor heat exchanger 109. Here, the heat exchanger 11 has the same configuration as the heat exchanger 1 of FIG. 2 shown in the first embodiment. However, 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. ..
＜実施の形態１０の効果＞
　実施の形態１０によれば、熱交換器１は、空気調和装置１００を構成する室内機１０２に搭載されている。 <Effect of Embodiment 10>
According to the tenth embodiment, the heat exchanger 1 is mounted on the indoor unit 102 constituting the air conditioner 100.
　この構成によれば、複数の熱交換体１０を流通する複数の冷媒流路が構成でき、室内機１０２に搭載された熱交換器１の複数の冷媒流路の数が増大できるとともに、複数の冷媒流路の長さが短くなり、熱交換器１の圧力損失が低減でき、それに伴う性能が改善できる。 According to this configuration, 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.
　なお、実施の形態１～１０は、組み合わせられても良いし、他の部分に適用されても良い。 It should be noted that the first to tenth embodiments may be combined or applied to other parts.
　１　熱交換器、１ａ　熱交換器、１ｂ　熱交換器、１ｃ　熱交換器、２　液ヘッダー、３　扁平管、４　ガスヘッダー、５　折り返しヘッダー、６　フィン、７　筐体側面、８　Ｕ字管、１０　熱交換体、１１　熱交換器、１００　空気調和装置、１０１　室外機、１０２　室内機、１０３　ガス冷媒配管、１０４　液冷媒配管、１０５　圧縮機、１０６　四方弁、１０８　膨張弁、１０９　室内熱交換器、２０１　熱交換器。 1 heat exchanger, 1a heat exchanger, 1b heat exchanger, 1c heat exchanger, 2 liquid header, 3 flat tube, 4 gas header, 5 folded header, 6 fins, 7 housing side surface, 8 U-shaped tube, 10 Heat exchanger, 11 heat exchanger, 100 air conditioner, 101 outdoor unit, 102 indoor unit, 103 gas refrigerant pipe, 104 liquid refrigerant pipe, 105 compressor, 106 four-way valve, 108 expansion valve, 109 indoor heat exchanger, 201 Heat exchanger.

Claims (22)

  1. 　上下方向に伸びた複数の扁平管を有する熱交換体と、
    　前記熱交換体の下端部に接続されて水平方向に伸びたガスヘッダーと、
    　前記熱交換体に接続されて水平方向に伸びた液ヘッダーと、
    を備え、
    　前記熱交換体は、前記ガスヘッダーの伸びた水平方向を起点として上向き鉛直方向に対して角度θ傾けて配置され、
    　前記角度θは、０°＜θ＜９０°を満たし、
    　Ｃが上下方向に伸びた扁平管内にて液冷媒を上昇させるフラッディング現象を発生させる基準となるフラッディング定数［－］であり、
    　ρＬが液体の密度［ｋｇ／ｍ３］であり、
    　ρＧが気体の密度［ｋｇ／ｍ３］であり、
    　ｇが重力加速度［ｍ／ｓ２］であり、
    　Ｄが水力直径［ｍ］であり、
    　ｖＬが液速度であり、
    　ｖＧが気体速度であるとき、
    Figure JPOXMLDOC01-appb-M000001
    Figure JPOXMLDOC01-appb-M000002
    Figure JPOXMLDOC01-appb-M000003
     　上記式（１０）、式（１１）及び式（１２）が満たされるとともに、
    　Ｃ≧１．５が満たされる熱交換器。     A heat exchanger with multiple 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,
    A liquid header connected to the heat exchanger and extending in the horizontal direction,
    With
    The heat exchanger is arranged at an angle θ with respect to the upward vertical direction starting from the extending horizontal direction of the gas header.
    The angle θ satisfies 0 ° <θ <90 °.
    C is a flooding constant [-] that serves as a reference for generating a flooding phenomenon that raises the liquid refrigerant in a flat tube extending in the vertical direction.
    ρ L is the density of the liquid [kg / m 3 ],
    ρ 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,
    When v G is the gas velocity
    Figure JPOXMLDOC01-appb-M000001
    Figure JPOXMLDOC01-appb-M000002
    Figure JPOXMLDOC01-appb-M000003
     The above equations (10), (11) and (12) are satisfied, and
    A heat exchanger in which C ≧ 1.5 is satisfied.
  2. 　前記熱交換体は、複数設けられ、
    　前記角度θは、前記複数の熱交換体のうち前記ガスヘッダーに接続された前記熱交換体を並び方向にて最下位置に配置させる角度である請求項１に記載の熱交換器。     A plurality of the heat exchangers are provided,
    The heat exchanger according to claim 1, wherein the angle θ is an angle at which the heat exchangers connected to the gas header among the plurality of heat exchangers are arranged at the lowest position in the alignment direction.
  3. 　フィンを備え、
    　前記角度θは、７°＜θ＜９０°を満たす請求項１又は請求項２に記載の熱交換器。     With fins
    The heat exchanger according to claim 1 or 2, wherein the angle θ satisfies 7 ° <θ <90 °.
  4. 　前記フィンは、コルゲートフィンである請求項３に記載の熱交換器。 The heat exchanger according to claim 3, wherein the fin is a corrugated fin.
  5. 　当該熱交換器は、凝縮器又は蒸発器の少なくとも一方として機能する請求項１～請求項４のいずれか１項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 4, wherein the heat exchanger functions as at least one of a condenser and an evaporator.
  6. 　前記複数の熱交換体のそれぞれは、通風させる並び方向に対して交差する表裏面を有し、
    　前記複数の熱交換体は、隣り合う前記熱交換体同士の対向する表裏面を平行に配置されている請求項２又は請求項２に従属する請求項３～請求項５のいずれか１項に記載の熱交換器。     Each of the plurality of heat exchangers has front and back surfaces that intersect with respect to the arrangement direction for ventilation.
    The plurality of heat exchangers are according to any one of claims 3 to 5, which are dependent on claim 2 or claim 2 in which the front and back surfaces of the adjacent heat exchangers are arranged in parallel. The heat exchanger described.
  7. 　前記複数の熱交換体のそれぞれの通風させる並び方向に直交する両側端部のそれぞれは、前記複数の熱交換体を並び方向から見て一致させて配置されている請求項２又は請求項２に従属する請求項３～請求項６のいずれか１項に記載の熱交換器。 According to claim 2 or 2, each of the end portions on both sides of the plurality of heat exchangers orthogonal to the direction in which the heat exchangers are to be ventilated are arranged so as to match the plurality of heat exchangers when viewed from the direction of arrangement. The heat exchanger according to any one of claims 3 to 6, which is dependent on the heat exchanger.
  8. 　前記複数の熱交換体のそれぞれの上下端部それぞれの高さは、前記複数の熱交換体を並び方向から見て一致させて配置された高さである請求項２又は請求項２に従属する請求項３～請求項７のいずれか１項に記載の熱交換器。 The height of each of the upper and lower ends of each of the plurality of heat exchangers is dependent on claim 2 or claim 2, which is the height at which the plurality of heat exchangers are arranged so as to be aligned when viewed from the arrangement direction. The heat exchanger according to any one of claims 3 to 7.
  9. 　前記複数の熱交換体のそれぞれの上下端部それぞれの高さは、前記複数の熱交換体を並び方向から見て順にずらされて配置された高さである請求項２又は請求項２に従属する請求項３～請求項７のいずれか１項に記載の熱交換器。 The height of each of the upper and lower ends of each of the plurality of heat exchangers is dependent on claim 2 or claim 2, which is the height at which the plurality of heat exchangers are arranged so as to be staggered in order when viewed from the arrangement direction. The heat exchanger according to any one of claims 3 to 7.
  10. 　前記複数の熱交換体のそれぞれの上下端部それぞれの高さは、前記複数の熱交換体を並び方向から見て順にずらされて同一高さに配置された高さである請求項９に記載の熱交換器。 The height of each of the upper and lower ends of each of the plurality of heat exchangers is the height at which the plurality of heat exchangers are arranged at the same height by being displaced in order when viewed from the arrangement direction. Heat exchanger.
  11. 　前記複数の熱交換体のうち隣り合う前記熱交換体同士における前記複数の扁平管によって形成される冷媒流路を折り返す折り返しヘッダーを備える請求項２又は請求項２に従属する請求項３～請求項１０のいずれか１項に記載の熱交換器。 Claims 3 to 3 subordinate to claim 2 or claim 2, further comprising a folded header that folds back a refrigerant flow path formed by the plurality of flat tubes between adjacent heat exchangers among the plurality of heat exchangers. The heat exchanger according to any one of 10.
  12. 　前記複数の熱交換体のうち隣り合う前記熱交換体同士における前記複数の扁平管をそれぞれ折り返すＵ字管を備える請求項２又は請求項２に従属する請求項３～請求項１０のいずれか１項に記載の熱交換器。 Any one of claims 3 to 10, which is dependent on claim 2 or claim 2, further comprising a U-shaped tube that folds back the plurality of flat tubes of the adjacent heat exchangers among the plurality of heat exchangers. The heat exchanger described in the section.
  13. 　当該熱交換器は、空気調和装置を構成する室外機に搭載されている請求項１～請求項１２のいずれか１項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 12, which is mounted on an outdoor unit constituting an air conditioner.
  14. 　前記複数の熱交換体のうち前記ガスヘッダーに接続された前記熱交換体は、前記室外機の最外部側に配置されている請求項２に従属する請求項１３に記載の熱交換器。 The heat exchanger according to claim 13, which is subordinate to claim 2, wherein the heat exchanger connected to the gas header among the plurality of heat exchangers is arranged on the outermost side of the outdoor unit.
  15. 　当該熱交換器は、上辺を起点として下辺を前記室外機の筐体内側に傾斜させている請求項１３又は請求項１４に記載の熱交換器。 The heat exchanger according to claim 13 or 14, wherein the heat exchanger has an upper side as a starting point and a lower side is inclined toward the inside of the housing of the outdoor unit.
  16. 　当該熱交換器は、下辺を起点として上辺を前記室外機の筐体外側に傾斜させている請求項１３又は請求項１４に記載の熱交換器。 The heat exchanger according to claim 13 or 14, wherein the heat exchanger has an upper side inclined to the outside of the housing of the outdoor unit with the lower side as a starting point.
  17. 　前記室外機は、４側面に構成された筐体を有し、
    　当該熱交換器は、前記筐体の４側面のうち表裏の２側面に配置されている請求項２に従属する請求項１３～請求項１６のいずれか１項に記載の熱交換器。     The outdoor unit has a housing configured on four sides.
    The heat exchanger according to any one of claims 13 to 16, which is subordinate to claim 2 and is arranged on two front and back side surfaces of the four side surfaces of the housing.
  18. 　前記室外機は、４側面に構成された筐体を有し、
    　当該熱交換器は、前記筐体の４側面のうち１側面を除く３側面に配置されている請求項２に従属する請求項１３～請求項１６のいずれか１項に記載の熱交換器。     The outdoor unit has a housing configured on four sides.
    The heat exchanger according to any one of claims 13 to 16, which is subordinate to claim 2 and is arranged on three side surfaces excluding one side surface of the four side surfaces of the housing.
  19. 　前記室外機は、４側面に構成された筐体を有し、
    　当該熱交換器は、前記筐体の４側面のうち３側面及び残り１側面の縦半分に配置されている請求項２に従属する請求項１３～請求項１６のいずれか１項に記載の熱交換器。     The outdoor unit has a housing configured on four sides.
    The heat according to any one of claims 13 to 16, which is dependent on claim 2, wherein the heat exchanger is arranged on three side surfaces of the four side surfaces of the housing and the vertical half of the remaining one side surface. Exchanger.
  20. 　前記室外機は、４側面に構成された筐体を有し、
    　当該熱交換器は、前記筐体の４側面のうち４側面全部に配置されている請求項２に従属する請求項１３～請求項１６のいずれか１項に記載の熱交換器。     The outdoor unit has a housing configured on four sides.
    The heat exchanger according to any one of claims 13 to 16, which is subordinate to claim 2 and is arranged on all four sides of the four sides of the housing.
  21. 　当該熱交換器は、空気調和装置を構成する室内機に搭載されている請求項１～請求項１２のいずれか１項に記載の熱交換器。 The heat exchanger according to any one of claims 1 to 12, which is mounted on an indoor unit constituting an air conditioner.
  22. 　請求項１～請求項２１のいずれか１項に記載の熱交換器を備える冷凍サイクル装置。 A refrigeration cycle apparatus including the heat exchanger according to any one of claims 1 to 21.
PCT/JP2019/041453 2019-10-23 2019-10-23 Heat exchanger and refrigeration cycle apparatus WO2021079422A1 (en)

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