WO2018173256A1 - 空気調和装置 - Google Patents
空気調和装置 Download PDFInfo
- Publication number
- WO2018173256A1 WO2018173256A1 PCT/JP2017/012014 JP2017012014W WO2018173256A1 WO 2018173256 A1 WO2018173256 A1 WO 2018173256A1 JP 2017012014 W JP2017012014 W JP 2017012014W WO 2018173256 A1 WO2018173256 A1 WO 2018173256A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- liquid
- pipe
- header
- heat exchanger
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Classifications
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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
- F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/14—Heat exchangers specially adapted for separate outdoor units
- F24F1/16—Arrangement or mounting thereof
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
- F24F1/38—Fan details of outdoor units, e.g. bell-mouth shaped inlets or fan mountings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
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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
- F28D1/0233—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 air flow channels
- F28D1/024—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 air flow channels with an air driving element
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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
- F28D1/0535—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 the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/0202—Header boxes having their inner space divided by partitions
- F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
-
- 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
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
-
- 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
- F28F2009/0285—Other particular headers or end plates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
Definitions
- the present invention relates to an air conditioner, and more particularly to a structure of a heat exchanger provided with a distribution header.
- liquid refrigerant condensed by a heat exchanger functioning as a condenser mounted on an indoor unit is decompressed by an expansion valve, and a gas-liquid two-phase state in which gas refrigerant and liquid refrigerant are mixed become.
- coolant of a gas-liquid two-phase state flows in into the heat exchanger which functions as an evaporator mounted in the outdoor unit.
- Patent Document 1 a technique for adjusting the insertion length of the branch pipe inserted into the header collecting pipe has been proposed (see, for example, Patent Document 1).
- the insertion length is equal among a plurality of branch pipes, and the refrigerant is evenly distributed to the heat exchanger by setting the flow velocity of the refrigerant in the distribution space between the header sets to an appropriate value. .
- the airflow passing through the actual heat exchanger is distributed in the vertical direction of the heat exchanger.
- the air volume is larger in the heat exchanger portion closer to the fan, and the air volume decreases as the distance from the fan increases.
- the amount of air passing through is larger at a position closer to the boss center of the fan, and closer to the upper end or lower end near the casing panel of the outdoor unit. It gets smaller.
- the refrigerant distribution is not optimal with respect to the air volume, so that the performance of the heat exchanger may be reduced and the energy efficiency of the air conditioner may be reduced. It was.
- the present invention has been made in order to solve the above-described problems, and provides an air conditioner capable of performing refrigerant distribution optimal for the amount of air passing through a heat exchanger while having a simple structure. With the goal.
- An air conditioner according to the present invention is arranged with a plurality of heat transfer tubes that are arranged apart from each other in the vertical direction and through which the refrigerant flows and a distribution space that extends in the vertical direction inside, and that are arranged apart from each other in the vertical direction.
- a heat exchanger having a header collecting pipe for allowing the refrigerant to flow into the plurality of heat transfer pipes from the branch pipes, and blades around the rotating boss, and a rotating surface of the blades with respect to the plurality of heat transfer tubes
- a refrigerant circuit that causes the refrigerant to flow into the circulation space so that the refrigerant in a gas-liquid two-phase state flows upward and evaporates the refrigerant with the heat exchanger.
- the flow mode of the refrigerant flowing in the header collecting pipe is an annular flow or a churn flow in which a gas phase refrigerant gathers at the center of the header collecting pipe and a liquid phase refrigerant gathers on the wall surface, and the center in the horizontal plane of the circulation space is 0%, said A plurality of the branch pipes whose height is within the range of rotation of the blades when the position of the wall surface of the tubder collecting pipe is 100% and the distance from the center in the horizontal plane is represented by 0 to 100% Of these, most of the branch pipes positioned below the height of the boss are inserted into the header collecting pipe so that the tip is 0 to 50% at a distance from the center, and are higher than the height of the boss. Most of the branch pipes located in the section are connected to the header collecting pipe so that the tip is larger than 50% in the distance from the center.
- another air conditioner according to the present invention is arranged spaced apart in the vertical direction, has a plurality of heat transfer tubes through which the refrigerant flows, and a flow space extending in the vertical direction inside, and is arranged spaced apart in the vertical direction.
- a heat exchanger having a header collecting pipe for allowing the refrigerant to flow from the plurality of branch pipes into the plurality of heat transfer pipes, a fan positioned above the plurality of heat transfer pipes, and a gas-liquid in the circulation space
- a refrigerant circuit that causes the refrigerant to flow in so that the refrigerant in a two-phase state flows upward, and evaporates the refrigerant in the heat exchanger, and the flow pattern of the refrigerant flowing in the header collecting pipe is the header assembly
- An annular flow or churn flow in which gas phase refrigerant gathers in the center of the tube and liquid phase refrigerant gathers on the wall surface, and the header collecting pipe is composed of a plurality of header collecting pipes arranged at different heights in the vertical direction.
- the position closest to the fan is In one header collecting pipe, most of the branch pipes to be connected are inserted at a distance of 0 to 50% from the center, and are lower than the header collecting pipe located closest to the fan. In the header collecting pipe, the most of the branch pipes to be connected are connected such that the tip is larger than 50% in the distance from the center.
- another air conditioner according to the present invention is arranged spaced apart in the vertical direction, has a plurality of heat transfer tubes through which the refrigerant flows, and a flow space extending in the vertical direction inside, and is arranged spaced apart in the vertical direction.
- a heat exchanger having a header collecting pipe for allowing the refrigerant to flow from the plurality of branch pipes into the plurality of heat transfer pipes, a fan positioned above the plurality of heat transfer pipes, and a gas-liquid in the circulation space
- a refrigerant circuit that causes the refrigerant to flow in so that the refrigerant in a two-phase state flows upward, and evaporates the refrigerant in the heat exchanger, and the flow pattern of the refrigerant flowing in the header collecting pipe is the header assembly
- An annular flow or churn flow in which the gas phase refrigerant gathers in the center of the pipe and the liquid phase refrigerant gathers on the wall surface, the center in the horizontal plane of the circulation space is 0%, and the position of the wall surface of the header collecting pipe is 100%.
- the header is configured so that most of the branch pipes connected to the header collecting pipe have a tip at 0 to 50% in the distance from the center.
- the branch pipe that is inserted into the collecting pipe and is connected to the header collecting pipe and located at the uppermost part of the branch pipe is connected to the header collecting pipe so that the tip thereof is greater than 50% in the distance from the center. It is connected.
- the insertion length of the plurality of branch pipes into the header collecting pipe is varied in the vertical direction of the heat exchanger according to the positional relationship between the heat exchanger and the fan or the axial flow fan. Yes.
- the flow mode of the refrigerant flowing into the liquid header collecting pipe is an annular flow or a churn flow
- the branch pipe is In the header region connected so as to be covered with the liquid layer, the liquid refrigerant flows in the lower part. Therefore, by combining such regions vertically, refrigerant distribution suitable for the wind speed distribution of the heat exchanger can be realized, and the performance of the heat exchanger can be improved.
- FIG. 45 is a partial cross-sectional view showing a BB cross section of FIG. 44. It is the schematic which shows an example of the heat exchanger which concerns on Embodiment 10 of this invention. It is the schematic which showed the liquid header which concerns on Embodiment 10 of this invention, and the relationship between a liquid refrigerant
- FIG. 1 is a schematic diagram illustrating an example of a heat exchanger according to Embodiment 1 of the present invention.
- FIG. 2 is a diagram showing a heat transfer tube according to Embodiment 1 of the present invention.
- FIG. 3 is a diagram showing an example of the heat transfer tube according to Embodiment 1 of the present invention.
- FIG. 4 is a diagram showing another example of the heat transfer tube according to Embodiment 1 of the present invention.
- the heat exchanger 1 includes a liquid header 10, a gas header 40, a heat exchange unit 20, a plurality of branch pipes 12 that connect the liquid header 10 or the gas header 40 to the heat exchange unit 20, and the like. Consists of. Further, one axial fan 30 is disposed on the side surface of the heat exchanger 1. The heat exchanger 1 constitutes a part of the refrigeration cycle of the air conditioner.
- the liquid header 10 is configured by connecting a plurality of branch pipes 12 to a liquid header main pipe 11.
- a header collecting pipe one or a plurality of liquid header main pipes 11 constituting the liquid header 10 may be collectively referred to as a header collecting pipe.
- the liquid header main pipe 11 is formed with a circulation space extending in the vertical direction (arrow Z direction) and has a circular pipe shape.
- the lower part of the liquid header main pipe 11 is connected to an inflow pipe 52 whose upstream side is connected to the piping of the refrigerant circuit.
- the liquid phase refrigerant Rb and the gas phase refrigerant Ra are distributed in the circulation space, and a liquid layer formed by collecting the liquid phase refrigerant Rb along the wall surface of the liquid header main pipe 11 is formed.
- the run-up distance L [m] is defined as a distance from the position of the inflow portion of the liquid header 10 into which the refrigerant flows and the position of the central axis of the branch pipe 12 closest to the position of the inflow portion.
- the gas header 40 is configured by connecting a plurality of branch pipes 12 to a circular gas header main pipe 41 having a circulation space formed therein.
- an outflow pipe 51 through which the refrigerant flows out is connected to the lower part of the gas header 40.
- FIG. 2 is a perspective view showing a part of the AA cross section of the heat exchange section 20 shown in FIG.
- the heat exchanging unit 20 has a plurality of fins 21 arranged in parallel in the direction of the arrow X at intervals, and penetrates the fins 21 in the juxtaposition direction of the fins 21 and protrudes on both sides.
- a plurality of heat transfer tubes 22 and the like arranged in such a manner.
- the heat transfer tubes 22 are arranged apart from each other in the vertical direction (arrow Z direction). One end of the heat transfer tube 22 is connected to the liquid header 10 and the other end is connected to the gas header 40 via the branch tube 12, and the refrigerant flows inside.
- a flat tube having a flat cross section is shown as the heat transfer tube 22 of the heat exchange unit 20, but the type and shape are not limited.
- the heat transfer tube 22 may be, for example, a flat porous tube 22a having a flat cross section as shown in FIG. 3 and having a plurality of holes formed therein, or a circular cross section as shown in FIG. It may be configured by a circular tube 22b having a shape. Further, the heat transfer tube 22 may be configured with a grooved surface that expands the heat transfer area by cutting the groove, or may be configured with a smooth surface to suppress an increase in pressure loss.
- the axial fan 30 includes a boss 31 and blades 32 arranged around the boss 31, and supplies air to the heat exchanger 1.
- the boss 31 is rotated by a motor or the like, and air is taken in from one side surface in the arrow Y direction and blown out from the other side surface.
- the axial fan 30 is arranged such that the rotating surface of the blade 32 faces the plurality of heat transfer tubes 22 of the heat exchanger 1 in the horizontal direction.
- the height of the center of the boss 31 in the vertical direction (arrow Z direction) is represented by the boss center line Ob.
- the plurality of branch pipes 12 are arranged so as to be spaced apart in the vertical direction (arrow Z direction), connect the liquid header 10 or the gas header 40 and the plurality of heat transfer pipes 22, and allow refrigerant to flow therethrough.
- branch pipes 12a positioned below the boss center line Ob are connected to the liquid header 10 so that the tip positions penetrate the liquid layer, and are positioned above the boss center line Ob.
- the branch pipe 12b is connected so that the tip position is covered with the liquid phase refrigerant Rb. That is, the branch pipe 12a below the boss center line Ob has a longer insertion length into the liquid header main pipe 11 than the upper branch pipe 12b.
- FIG. 5 is an explanatory diagram showing an example of the wind speed distribution of the heat exchanger and the liquid refrigerant distribution of the liquid header according to Embodiment 1 of the present invention.
- FIG. 5A is a schematic diagram of the heat exchanger 1
- FIG. 5B shows the wind speed distribution of the airflow passing through the heat exchanger 1
- FIG. 5C is the liquid refrigerant flow distribution of the liquid header 10.
- Indicates. 5 (a) and 5 (b) the vertical axis represents the height of the heat exchanger 1 shown in FIG. 5 (a).
- the wind speed flowing through the height position of the boss 31 of the axial fan 30 is high. Maximum.
- the liquid refrigerant flow rate distribution of the liquid header 10 in the region from the lower end of the heat exchanger 1 to the boss center line Ob, the liquid refrigerant increases as it approaches the boss 31, and the heat exchanger starts from the boss center line Ob. In the region up to the upper end of 1, the liquid refrigerant becomes less distributed as the distance from the boss 31 increases.
- the liquid refrigerant flow distribution of the liquid header 10 as described above is obtained by the difference in insertion amount between the branch pipe 12a and the branch pipe 12b.
- the plurality of branch pipes 12a penetrate the liquid layer of the refrigerant flowing through the liquid header 10, so that the distribution of the liquid refrigerant below, that is, the lower part of the heat exchanger 1 is suppressed.
- the plurality of branch pipes 12b remain in the liquid layer of the refrigerant flowing through the liquid header 10, so that the liquid refrigerant at the lower position, that is, at the height of the boss center line Ob.
- the distribution of will increase.
- the heat exchanger 1 can perform refrigerant distribution suitable for the wind speed distribution, and can improve the performance of the heat exchanger 1.
- the plurality of branch pipes 12 a and 12 b whose insertion lengths are adjusted in this way are positioned on the upstream side of the liquid header 10. This is because when the area of the liquid header 10 is divided vertically with respect to the boss center line Ob, the upstream side structure has a greater influence on the liquid distribution characteristics than the downstream side in each area.
- the connection between the liquid header 10 and the branch pipe 12a positioned below the boss center line Ob will be described.
- the branch pipe 12 a located below the boss center line Ob is connected so that the tip position is located at the inner diameter center of the liquid header main pipe 11.
- the distal end portion of the branch pipe 12a only needs to penetrate the liquid layer of the refrigerant flowing in the liquid header 10, and may be located in a range having a spread near the center.
- a range having a spread near the center will be described.
- FIG. 6 is a diagram showing positions in the liquid header of a plurality of branch pipe tip portions connected to a lower part than the boss center line according to Embodiment 1 of the present invention.
- FIG. 7 is a diagram illustrating an example of positions in the liquid header of a plurality of branch pipe tip portions connected to a lower part than the boss center line according to Embodiment 1 of the present invention.
- FIG. 8 is a diagram showing another example of positions in the liquid header of a plurality of branch pipe tip portions connected to a lower part than the boss center line according to Embodiment 1 of the present invention.
- the vicinity of the center here means that the center position in the horizontal plane of the circulation space of the liquid header main pipe 11 is defined as 0% as shown in FIGS. 6, 7, and 8, and the circulation space of the liquid header main pipe 11 is defined.
- the wall surface position on the horizontal plane is defined as ⁇ 100%, it means that the tip of the branch pipe 12 is connected so as to be within an area within ⁇ 50%.
- a shown in FIGS. 6, 7, and 8 indicates the effective flow path cross-sectional area [m 2 ] in the horizontal cross-sectional view at the position where the branch pipe 12 is inserted.
- FIG. 9 is a diagram showing an example of the relationship between the tip positions of a plurality of branch pipes connected to the lower part of the boss center line according to Embodiment 1 of the present invention and the heat exchanger performance.
- FIG. 9 shows an example of the experimental results of the inventors.
- the horizontal axis represents the tip position of the branch pipe 12a, and the vertical axis represents the heat exchanger performance.
- the distal end portion of the branch pipe 12 is placed within a position within ⁇ 50%, thereby obtaining an effect of improving the distribution performance. be able to.
- the tip of the branch pipe 12a positioned below the boss center line Ob is placed within ⁇ 50%, so that the liquid refrigerant is moved upward, that is, in the boss area in the region from the lower end of the liquid header 10 to the boss center line Ob. A large amount can be distributed to the height near the center line Ob.
- the tip of the branch pipe 12a is arranged at the center of the inner diameter of the liquid header main pipe 11, that is, at a position of 0%, the liquid in the region of the boss center line Ob from the lower end of the liquid header 10 in a wider refrigerant flow rate range. It is even better that a large amount of refrigerant can flow through the top.
- the boss center line Ob In the upper end region of the liquid header 10, a large amount of liquid refrigerant can be allowed to flow downward.
- the thickness ⁇ [m] of the liquid layer is such that when the dryness of the refrigerant flowing into the liquid header 10 is 0.05 ⁇ x ⁇ 0.30, the refrigerant flow rate G [ kg / (m 2 s)], the dryness x of the refrigerant, the inner diameter D [m] of the liquid header 10, the refrigerant liquid density ⁇ L [kg / m 3 ], and the apparent gas of the refrigerant flowing into the circulation space of the liquid header 10
- U LS [m / s] which is the maximum value of the speed fluctuation range
- the front ends of the plurality of branch pipes 12a connected to the liquid header 10 below the boss center line Ob protrude at least from the thickness ⁇ of the liquid layer obtained by the above formula, and the gas phase refrigerant Ra is in the circulation space. It only has to be reached.
- the reference liquid apparent speed U LS [m / s] is defined by G (1-x) / ⁇ L.
- the determination of the flow mode is performed from the flow mode diagram of the vertical upward flow, and the refrigerant reference gas apparent velocity U GS [m / s] at the maximum value of the fluctuation range of the refrigerant flow rate flowing into the circulation space of the liquid header main pipe 11.
- the reference gas apparent velocity U GS [m / s] of the refrigerant flowing into the liquid header main pipe 11 is U GS ⁇ ⁇ ⁇ L ⁇ (g ⁇ D) 0.5 /(40.6 ⁇ D) ⁇ 0.22 ⁇ (G ⁇ D) 0.5 should be satisfied.
- FIG. 10 is a diagram showing a relationship between the reference gas apparent speed U GS [m / s] of the refrigerant according to Embodiment 1 of the present invention and the effect of improving the distribution performance.
- U GS [m / s] of the refrigerant in the range specified above, the refrigerant flowing in the liquid header 10 becomes an annular flow or a churn flow, and the effect of improving the distribution performance is obtained. I can expect.
- L is the run-up distance [m]
- g is the gravitational acceleration [m / s 2 ]
- D is the inner diameter [m] of the liquid header 10
- x is the dryness of the refrigerant
- ⁇ G is the refrigerant gas density [kg / m 3 ]
- ⁇ L is the refrigerant liquid density [kg / m 3 ]
- ⁇ is the refrigerant surface tension [ N / m].
- the refrigerant void ratio ⁇ is measured by, for example, measurement using electric resistance or observation by visualization.
- run-up distance L 2 [m] of the inflow portion of the liquid header 10 is defined by a distance from the position of the inflow portion of the liquid header 10 to the position of the central axis of the branch pipe 12 closest to the position of the inflow portion. To do.
- the distribution performance improvement effect is as follows: U SG ⁇ ⁇ ⁇ L 2 ⁇ (g ⁇ D) 0.5 /(40.6 ⁇ D) ⁇ 0.22 ⁇ (g ⁇ D) The effect is increased rapidly by satisfying 0.5 . Then, in particular, the effect becomes remarkable by satisfying U SG ⁇ 3.1 / ( ⁇ G 0.5) ⁇ [ ⁇ ⁇ g ⁇ ( ⁇ L - ⁇ G)] 0.25.
- the maximum value of the fluctuation range of the refrigerant flow rate flowing into the distribution space of the liquid header 10 is the distribution of the liquid header 10 when the liquid header 10 is in the heating rated operation.
- the gas-liquid two-phase refrigerant flows as an upward flow through the space.
- the refrigerant flowing through the liquid header main pipe 11 has a large amount of liquid phase refrigerant Rb distributed near the wall surface. It becomes a flow pattern.
- the improvement effect of the distribution performance by the protrusion of the branch pipe 12 and the improvement effect of the performance of the heat exchanger may be particularly large.
- the central axis extending in the horizontal direction (arrow X direction) of the branch pipe 12a and the vertical direction (arrows) of the liquid header main pipe 11 are shown.
- the case where the central axis extending in the (Z direction) intersects is mentioned.
- the central axis extending in the horizontal direction of the branch pipe 12 a may be shifted from the central axis extending in the vertical direction of the liquid header main pipe 11.
- FIG. 11 is a diagram showing another example of the positions in the liquid header 10 of a plurality of branch pipe tip portions connected to the lower part of the boss center line according to Embodiment 1 of the present invention.
- FIG. 12 is a diagram showing another example of the positions in the liquid header 10 of the plurality of branch pipe tip portions connected to the lower part of the boss center line according to Embodiment 1 of the present invention.
- the center position of the distribution space of the liquid header main pipe 11 in the horizontal plane is defined as 0%.
- the wall surface position in the horizontal plane of the circulation space of the liquid header main pipe 11 is defined as ⁇ 100%.
- the insertion direction of the plurality of branch pipes 12 on the horizontal plane is the X direction, and the width direction is the Y direction.
- the liquid phase refrigerant Rb has a flow mode characteristic in which it is distributed in the vicinity of the wall surface of the liquid header main pipe 11. Useful distribution performance can be improved.
- the central axis of the branch pipe 12a located below the boss center line Ob is accommodated in a region within ⁇ 50% in the Y direction, and the tip of the branch pipe 12a is When it is stored in an area within ⁇ 50% in the X direction, the protruding length can be easily managed by connecting so that a part of the branch pipe 12a contacts the inner wall of the liquid header main pipe 11. Good to be able.
- each branch pipe 12a positioned below the boss center line Ob has the same insertion amount.
- the insertion amount may not be the same.
- the boiling point is a mixture of two or more of olefinic refrigerants such as R1234yf or R1234ze (E), HFC refrigerants such as R32, hydrocarbon refrigerants such as propane or isobutane, CO 2 , DME (dimethyl ether), and the like.
- olefinic refrigerants such as R1234yf or R1234ze (E)
- HFC refrigerants such as R32
- hydrocarbon refrigerants such as propane or isobutane
- CO 2 cyclobutane
- DME dimethyl ether
- the present invention depends on the flow mode of the gas-liquid two-phase refrigerant flowing through the liquid header 10. For this reason, it is preferable that the refrigerant flow in the gas-liquid two-phase state is sufficiently developed.
- the run-up distance L required for the development of the gas-liquid two-phase refrigerant satisfies L ⁇ 5D when the inner diameter of the liquid header main pipe 11 is D [m]. If secured, the effect of improving distribution performance is greater. Further, it is better that the approach distance L is secured so as to satisfy L ⁇ 10D.
- FIG. 13 is a schematic diagram showing a state in which the run-up distance Li of the liquid header and the gas-liquid two-phase refrigerant are developed according to Embodiment 1 of the present invention.
- the gas-liquid two-phase refrigerant flows from the refrigerant inlet at the bottom of the liquid header 10 as a vertical upward flow.
- the liquid layer is thick at the inflow portion, but gradually becomes thinner as droplets begin to be generated as the flow develops.
- the thickness of the liquid layer is constant.
- FIG. 14 is a schematic diagram showing another example of the liquid header according to the first embodiment of the present invention.
- the pitch length between the adjacent branch pipes 12 among the plurality of branch pipes 12 is defined as Lp and the stagnation region length at the top of the liquid header 10 is defined as Lt, Lt ⁇ 2 ⁇ Lp.
- the refrigerant in the gas-liquid two-phase state is less affected by collision at the top of the liquid header 10, and the effect of improving the distribution performance is increased by stabilizing the flow pattern.
- FIG. 15 is a schematic view showing another example of the liquid header according to Embodiment 1 of the present invention.
- the end branch pipe 18b is connected to the upper end of the liquid header 10 from the upper side. According to this configuration, a decrease in dynamic pressure due to the collision of the refrigerant at the upper part of the liquid header 10 is suppressed. This stabilizes the flow pattern and increases the effect of improving the distribution performance.
- branch pipe 12 described with respect to the position of the tip portion does not include, for example, an end branch pipe 18b connected from the upper end or the lower end of the liquid header main pipe 11.
- FIG. 16 is a schematic diagram showing another example of the liquid header according to the first embodiment of the present invention.
- the case where the bifurcated pipe 13 is used as the branch pipe 12 is shown.
- the bifurcated pipe 13 has two outlets with respect to the inlet from the liquid header main pipe 11.
- the bifurcated tube 13 By using the bifurcated tube 13 as the branch tube 12, it is possible to suppress fluctuations in dynamic pressure caused by causing the branch tube 12 a located below the boss center line Ob to protrude from the liquid header main tube 11. Therefore, the liquid header 10 can suppress the change in the flow mode, and can increase the efficiency of the heat exchanger 1.
- FIG. 16 shows an example in which the plurality of branch pipes 12 are all composed of bifurcated pipes 13. However, only a part of the plurality of branch pipes 12 may be constituted by the bifurcated pipe 13.
- FIG. 17 is a schematic diagram showing another example of the liquid header according to Embodiment 1 of the present invention.
- a bifurcated tube 13 is used for a part of the branch pipes, and a branch pipe 12 having one inlet and one outlet is used for the other branch pipes.
- the bifurcated tube 13 may be provided at a position near the lower portion of the liquid header 10 where the flow rate of refrigerant flowing through the liquid header 10 is large. In this case, a decrease in dynamic pressure due to the branch pipe protruding may be effectively suppressed.
- the branch pipe 12 is described as a part of the liquid header 10.
- the circular heat transfer tube 22 of the heat exchanger 1 may be extended to be configured by a part of the heat transfer tube.
- a heat transfer promotion shape such as a groove may be processed on the inner surface.
- the inflow pipe 52 is connected to the lower end of the liquid header main pipe 11, but if the space of the liquid header main pipe 11 is formed by the lower end and the branch pipe 12 closest to the lower end, It may be connected.
- FIG. 18 shows an example of the connection position between the liquid header and the inflow pipe according to Embodiment 1 of the present invention.
- the inflow pipe 52 when the inflow pipe 52 is connected to the side surface, the inflow pipe 52 may be eccentric with respect to the center line of the liquid header main pipe 11. In this case, the gas-liquid two-phase refrigerant flowing through the liquid header 10 easily transitions to the annular flow, and refrigerant distribution is improved.
- the air conditioner has a plurality of heat transfer tubes 22 that are arranged apart from each other in the vertical direction and through which the refrigerant flows, and a distribution space that extends in the vertical direction (arrow Z direction).
- the heat exchanger 1 having a header collecting pipe (liquid header main pipe 11) for allowing the refrigerant to flow into the plurality of heat transfer pipes 22 from the plurality of branch pipes 12 spaced apart in the vertical direction, and the rotating boss 31
- the axial flow fan 30 having the rotating surface of the blade 32 facing the plurality of heat transfer tubes 22 in the horizontal direction so that the gas-liquid two-phase refrigerant flows upward in the circulation space.
- a refrigerant circuit that flows in the refrigerant and evaporates the refrigerant in the heat exchanger 1, and the flow mode of the refrigerant flowing in the header collecting pipe is such that the gas-phase refrigerant Ra gathers in the center of the header collecting pipe and the liquid-phase refrigerant on the wall surface
- An annular flow or channel where Rb collects When the center of the distribution space in the horizontal plane is 0%, the position of the wall surface of the header collecting pipe is 100%, and the distance from the center in the horizontal plane is 0 to 100%, the height of the blade 32 is Among the plurality of branch pipes 12 within the range of the rotating height, most of the branch pipes 12a located below the height of the boss 31 are set so that the tip is 0 to 50% in the distance from the center. Most of the branch pipes 12b inserted into the pipe and positioned above the height of the boss 31 are connected to the header collecting pipe so that the tip is larger than 50% in the distance from the center.
- the air conditioner is connected so that the branch pipes 12 connected to the liquid header main pipe 11 are covered with the liquid layer at a position higher than the boss 31, and the branches at a position lower than the boss 31.
- a tube is inserted through the liquid layer. Therefore, when a large amount of liquid phase refrigerant Rb is distributed on the wall surface in the liquid header 10, a large amount of liquid refrigerant flows in the lower part in the region above the boss 31, and a large amount of liquid refrigerant flows in the upper part in the region below the boss 31. . Therefore, the side flow heat exchanger 1 can obtain a liquid refrigerant flow rate distribution suitable for a wind speed distribution having a peak at a height near the boss center line Ob. As a result, the air conditioner can improve the performance of the heat exchanger 1 and improve the energy efficiency.
- the tip is 0 to 50% of the distance from the center, and the tip of the branch pipe located on the most upstream side is a liquid phase refrigerant on the wall surface.
- the tip is 50% at the distance from the center.
- the tip of the branch pipe that is larger and located most upstream is in the liquid layer.
- the plurality of branch pipes 12a connected to the lower portion than the height of the boss 31 need only penetrate at least the liquid layer having the thickness ⁇ [m] obtained by the above formula based on the experimental result.
- the range of the adjustable insertion length can be widened.
- the dryness x of the refrigerant flowing into the header collecting pipe is in the range of 0.05 ⁇ x ⁇ 0.30.
- FIG. FIG. 19 is a schematic diagram showing an example of a heat exchanger according to Embodiment 2 of the present invention.
- one axial flow fan 30 is arranged on the side surface of the heat exchanger 1, and the liquid header 10 has the liquid header main pipe 11 vertically above the boss center line Ob of the boss 31 of the axial flow fan 30.
- the first liquid header main pipe 11a is formed at the lower part, and the second liquid header main pipe 11b is formed at the upper part.
- a plurality of branch pipes 12a positioned below the boss center line Ob are connected to the first liquid header main pipe 11a and inserted to the vicinity of the inner diameter center of the first liquid header main pipe 11a so as to penetrate the liquid layer. It is.
- the plurality of branch pipes 12b positioned above the boss center line Ob are connected to the second liquid header main pipe 11b so as to be covered with the liquid layer.
- a first inflow pipe 52a is connected upstream of the first liquid header main pipe 11a
- a second inflow pipe 52b is connected upstream of the second liquid header main pipe 11b.
- the first inflow pipe 52a and the second inflow pipe 52b are each connected to the lower end of the first liquid header main pipe 11a or the second liquid header main pipe 11b, but the connection position is not particularly limited thereto.
- FIG. 20 is a schematic diagram showing another example of the heat exchanger according to Embodiment 2 of the present invention.
- each inflow pipe may be connected to the side surface of each liquid header main pipe as long as it is a space between the lower end of each liquid header main pipe and the branch pipe closest to the lower end.
- the first liquid header main pipe 11a and the second liquid header main pipe 11b can be coaxially arranged vertically by connecting the second inflow pipe 52b to the side surface. For this reason, the liquid header 10 can easily manage the insertion of the branch pipe 12 and is excellent in manufacturability.
- FIG. 21 is a schematic view showing another example of the heat exchanger according to Embodiment 2 of the present invention.
- the end branch pipe 18a is connected to the upper end of the first liquid header main pipe 11a from the upper side.
- the refrigerant can flow into the second liquid header main pipe 11b from the lower end to stabilize the flow mode, and the decrease in dynamic pressure due to the collision of the refrigerant at the upper part of the first liquid header main pipe 11a is suppressed. it can.
- branch pipe 12 described with respect to the position of the tip portion does not include, for example, an end branch pipe 18a that is connected from the upper end or the lower end of each liquid header main pipe.
- the plurality of branch pipes 12a connected to the lower part of the boss center line Ob are inserted to the vicinity of the inner diameter center of the first liquid header main pipe 11a, but as in the case of the first embodiment.
- the thickness ⁇ [m] of the liquid layer may be penetrated.
- the formula of the liquid layer thickness ⁇ [m] described in the first embodiment the position range of the tip portions of the plurality of branch pipes 12a
- the effect of improving the distribution performance using the flow mode characteristics of the annular flow or the churn flow can be obtained.
- the plurality of branch pipes 12b to be connected may have a length of insertion of the branch pipe 12b that is less than the thickness ⁇ [m] of the liquid layer.
- FIG. 22 is a diagram showing positions in the second liquid header of a plurality of branch pipe tip portions connected to the second liquid header according to Embodiment 2 of the present invention.
- FIG. 23 is a diagram illustrating an example of positions in the second liquid header of a plurality of branch pipe tip portions connected to the second liquid header according to Embodiment 2 of the present invention.
- FIG. 24 is a diagram illustrating another example of positions in the second liquid header of a plurality of branch pipe tip portions connected to the second liquid header according to Embodiment 2 of the present invention.
- the central position in the horizontal plane of the distribution space of the branch pipe 12b connected to the second liquid header main pipe 11b is defined as 0%, and the wall surface position in the horizontal plane of the distribution space of the second liquid header main pipe 11b is defined as ⁇ 100%.
- the branch pipe 12b is connected along the wall surface of the second liquid header main pipe 11b.
- the distal end portion of the branch pipe 12b is inserted at a position of ⁇ 51%, and in FIG. 24, it is inserted at a position of 70%.
- the plurality of branch pipes 12b positioned on the upper portion of the liquid header 10 are housed in the region where the tip end is within ⁇ 100% to 51% or within 51% to 100% in the arrow X direction as the insertion direction. It is good that they are connected.
- a shown in FIGS. 22 to 24 indicates the effective flow path cross-sectional area [m 2 ] in the horizontal cross-sectional view at the position where the branch pipe 12 is inserted.
- FIG. 25 is a diagram showing the relationship between the wind speed distribution and the liquid refrigerant flow rate distribution according to Embodiment 2 of the present invention.
- the air volume has a peak near the center of the boss 31, and the upper end of the heat exchanger 1 or The air volume becomes smaller as it approaches the lower end.
- the liquid header 10 is vertically divided into two with respect to the boss center line Ob of the axial fan 30, and a plurality of branch pipes 12a connected to the lower first liquid header main pipe 11a are connected so as to penetrate the liquid layer.
- the plurality of branch pipes 12b connected to the upper second liquid header main pipe 11b are connected so as to be covered with the liquid layer.
- the liquid refrigerant flows in the upper part, that is, near the height of the boss center line Ob
- the second liquid header main pipe 11b the liquid refrigerant flows in the lower part, that is, near the height of the boss center line Ob. A lot flows. Therefore, refrigerant distribution suitable for the side flow wind speed distribution can be performed in the heat exchanger 1, and the performance of the heat exchanger 1 is improved.
- the air conditioner is connected to the second liquid header main pipe 11b at a position higher than the boss 31 such that the ends of the branch pipes 12b are covered with the liquid layer.
- the plurality of branch pipes 12a are inserted so that the tips penetrate the liquid layer.
- the side-flow heat exchanger 1 can obtain a liquid refrigerant flow distribution suitable for the wind speed distribution having a peak at a height near the boss center line Ob, The performance of the exchanger 1 is improved.
- the header collecting pipe (liquid header main pipe 11) is divided into a plurality of vertical spaces in which the circulation space connected to the plurality of branch pipes 12 within the range of the height of rotation of the blades 32 is divided. Has been.
- the heat exchanger 1 is easy to adjust so that it may become a refrigerant
- FIG. 26 is a schematic diagram illustrating an example of a heat exchanger according to Embodiment 3 of the present invention.
- the main pipe of the liquid header 10 is divided into two in the vertical direction as in the second embodiment.
- a first inflow pipe 52a is connected to the lower first liquid header main pipe 11a
- a second inflow pipe 52b is connected to the upper second liquid header main pipe 11b.
- the heat exchanger 1 is further provided with the 1st flow volume adjustment mechanism 53 arrange
- the first flow rate adjusting mechanism 53 can adjust the flow rate of the refrigerant flowing into the first liquid header main pipe 11a and the second liquid header main pipe 11b, for example, by adjusting the opening degree.
- the flow resistance becomes variable depending on the opening degree of the first flow rate adjusting mechanism 53, and the performance of the heat exchanger 1 can be improved in a wide operation range.
- a pressure difference can be generated between the upstream and downstream sides of the first flow rate adjusting mechanism 53.
- the heat exchanger 1 can adjust the dryness x of the refrigerant flowing into the first liquid header main pipe 11a to 0.05 ⁇ x ⁇ 0.30 in a wide operation range. Performance can be improved.
- the first flow rate adjusting mechanism 53 is provided on the first inflow pipe 52a and the opening degree can be adjusted.
- the first flow rate adjusting mechanism 53 only needs to adjust the flow resistance of the first inflow pipe 52a and the second inflow pipe 52b.
- the first flow rate adjustment mechanism 53 may be adjusted by a capillary tube, a pipe diameter, a pipe length, or the like. good.
- FIG. 27 is a schematic diagram showing another example of the heat exchanger according to Embodiment 3 of the present invention.
- an upper temperature sensor 42 is provided on the uppermost branch pipe 12 among the plurality of branch pipes 12 connected to the gas header 40.
- the upper temperature sensor 42 detects the temperature of the uppermost branch pipe 12 connected to the gas header 40, and when the temperature of the branch pipe 12 becomes higher than the saturation temperature, the opening degree of the first flow rate adjusting mechanism 53 is set. Control is made in the closing direction to cause a large amount of liquid refrigerant to flow in the second liquid header main pipe 11b, adjust the refrigerant distribution, and improve the performance of the heat exchanger 1.
- the saturation temperature may be defined by the saturation temperature estimated from the pressure at the refrigerant outlet of the gas header 40 or the measured temperature at the refrigerant outlet of the gas header 40.
- FIG. 28 is a schematic diagram showing another example of the heat exchanger according to Embodiment 3 of the present invention.
- an outflow temperature sensor 43 is provided in an outflow pipe 51 connected to the gas header 40.
- the outflow part temperature sensor 43 detects the temperature of the refrigerant flowing out of the gas header 40.
- 27 and 28 show the case where the upper temperature sensor 42 is provided in the uppermost branch pipe among the plurality of branch pipes 12 connected to the gas header 40, but the present invention is not limited to this. Absent.
- the position of the upper temperature sensor 42 is connected to the region of 75% to 100% when the distance in the height direction (arrow Z direction) of the gas header 40 is defined as 0% to 100% with the lower end as 0%.
- the branch pipe 12 it may be disposed anywhere.
- the opening degree of the first flow rate adjustment mechanism 53 is controlled in the closing direction so that the liquid refrigerant flows more in the second liquid header main pipe 11b, the refrigerant distribution is adjusted, and the performance of the heat exchanger 1 is improved.
- the side-flow heat exchanger 1 is a liquid refrigerant suitable for a wind speed distribution having a peak at a height near the boss center line Ob. A flow distribution can be obtained, and the performance of the heat exchanger 1 is improved.
- FIG. 29 is a schematic diagram illustrating an example of a heat exchanger according to Embodiment 4 of the present invention.
- the main pipe of the liquid header 10 is divided into upper and lower parts in the same manner as in the second embodiment.
- a first inflow pipe 52a is connected to the lower first liquid header main pipe 11a
- a second inflow pipe 52b is connected to the upper second liquid header main pipe 11b.
- the size of the main pipe of the liquid header 10 is different between the upper and lower sides.
- the branch pipe 12 is inserted so as to penetrate the liquid layer. Therefore, the flow path blockage area by the branch pipe 12 is larger than that of the second liquid header main pipe 11b. Therefore, the liquid header 10, the inner diameter of the first liquid header main 11a D 1 [m], the inner diameter of the second fluid header main 11b when defined as D 2 [m], so as to satisfy D 1> D 2 It is configured. In other words, the inner diameter D 1 of the first liquid header main 11a located below the liquid header 10 is made larger than the inner diameter D 2 of the second liquid header main 11b located above, an increase in flow resistance due to the branch pipe 12 Is suppressed.
- the side-flow heat exchanger 1 is a liquid refrigerant suitable for a wind speed distribution having a peak at a height near the boss center line Ob. A flow distribution can be obtained, and the performance of the heat exchanger 1 is improved.
- the header collecting pipe includes a plurality of header collecting pipes (first liquid header main pipe 11a, second liquid arranged at different heights in the vertical direction (arrow Z direction).
- the header collecting pipe lower header collecting pipe to which the branch pipe 12a located below the height of the boss 31 is connected among the plurality of branch pipes 12 formed of the header main pipe 11b) and within the range of the height of rotation of the blade 32.
- the first liquid header main pipe 11a) and the upper header collecting pipe (second liquid header main pipe 11b) to which the branch pipe 12b located above the height of the boss is connected include the distribution space of the lower header collecting pipe.
- the inner diameter D 1 is larger than the inner diameter D 2 of the flow space of the upper header collecting pipe.
- the inner diameter D 1 of the first liquid header main 11a is configured larger than the inner diameter D 2 of the second liquid header main 11b, suppress an increase in flow resistance due to the branch pipe 12a of the first fluid header main 11a it can.
- the difference in flow resistance due to the difference in insertion amount of the branch pipe 12 at the top and bottom of the liquid header 10 is suppressed to be small, and the refrigerant can be made to flow into the upper and lower portions of the liquid header 10 in a state that is nearly equal.
- FIG. 29 the case where the first liquid header main pipe 11a and the second liquid header main pipe 11b are arranged so that the centers of the inner diameters are located on the same straight line is shown as an example.
- the positional relationship with the two-liquid header main pipe 11b is not particularly limited to this.
- FIG. 30 is a schematic diagram showing another example of the heat exchanger according to Embodiment 4 of the present invention.
- the first liquid header main pipe 11 a and the second liquid header main pipe 11 b may be arranged so that the ends in the width direction (arrow X direction) are aligned.
- the insertion amounts of the branch pipe 12a and the branch pipe 12b should be different even if the branch pipe 12 has the same length. Can do.
- the heat exchanger 1 can reduce the types of components, and the insertion amount can be easily managed.
- FIG. FIG. 31 is a schematic diagram showing an example of a heat exchanger according to Embodiment 5 of the present invention.
- the side flow heat exchanger 1 has a plurality of flow paths formed in the liquid header 10.
- the same or corresponding configurations will be denoted by the same reference numerals and description thereof will be omitted.
- the liquid header 10 is divided into the flow path of the liquid header main pipe 11, and has a first liquid header flow path 13a and a second liquid header flow path 13b.
- the first liquid header flow path 13 a and the second liquid header flow path 13 b are divided vertically with respect to the boss center line Ob of the axial flow fan 30 disposed on the side surface of the heat exchanger 1.
- Each flow path constitutes a circulation space through which the refrigerant flows, and a partition wall 14 that partitions each flow path between the first liquid header flow path 13a located at the lower part and the second liquid header flow path 13b located at the upper part. Is provided.
- the 1st inflow port 15a which penetrates the 1st liquid header flow path 13a is formed in the lower end of the liquid header main pipe 11, and a refrigerant
- a second inflow port 15b penetrating the second liquid header flow path 13b is formed on the lower side surface of the second liquid header flow path 13b, and the refrigerant flows in from the second inflow pipe 52b. .
- the plurality of branch pipes 12a positioned below the boss center line Ob of the axial fan 30 is inserted into the liquid header 10 so that the tip portion penetrates the liquid layer, and is connected to the first liquid header flow path 13a. Yes.
- the plurality of branch pipes 12b positioned above the boss center line Ob are inserted into the liquid header 10 so that the tip ends are covered with the liquid layer, and are connected to the second liquid header flow path 13b.
- liquid header 10 when the inner diameter of the first liquid header channel 13a is defined as D 1 [m] and the inner diameter of the second liquid header channel 13b is defined as D 2 [m], D 1 > D 2 is satisfied.
- a flow path is preferably formed as described above. According to such a configuration, the difference in the flow resistance between the flow paths due to the difference in the amount of insertion of the branch pipes 12 can be kept small, and the refrigerant distribution to each flow path can be made to be in an almost equal state. it can.
- the above-described side-flow heat exchanger 1 is easy to position when the branch pipe 12 is inserted, and has good manufacturability by forming a plurality of flow paths with a single header pipe.
- the pressure resistance of the liquid header 10 is improved by the partition wall 14 that partitions each flow path.
- the cross-sectional shape of the liquid header 10 on the horizontal plane is not circular, for example, an elliptical shape, a rectangular shape, a D shape, or a semicircular shape
- the pressure resistance may be improved by partitioning each flow path.
- the dryness x of the refrigerant flowing into the liquid header 10 is in the range of 0.05 ⁇ x ⁇ 0.30, the liquid phase refrigerant Rb is increased on the wall surface in the first liquid header channel 13a.
- the distribution improvement effect by the distributed flow mode can be obtained.
- the side-flow heat exchanger 1 is a liquid refrigerant suitable for a wind speed distribution having a peak near the boss center line Ob. A flow distribution can be obtained, and the performance of the heat exchanger 1 is improved.
- the distribution space connected to the plurality of branch pipes 12 within the range of the rotating height of the blades is divided into a plurality in the vertical direction. ing.
- the insertion length of a branch pipe should just be managed for every distribution space, and it is excellent in manufacturability.
- the heat exchanger 1 is easy to adjust so that it may become a refrigerant
- FIG. 32 is a schematic diagram illustrating an example of a heat exchanger according to Embodiment 6 of the present invention.
- the side-flow heat exchanger 101 includes two axial fans 30a and 30b on the upper and lower sides.
- the liquid header 110 is divided into two upper and lower parts with respect to the boss center lines Ob1 and Ob2 of the bosses 31a and 31b, and is composed of four main pipes.
- the same or corresponding configurations will be denoted by the same reference numerals and description thereof will be omitted.
- the two axial fans 30a and 30b are provided such that the rotating surfaces of the blades 32a and 32b face the plurality of heat transfer tubes 22 in the horizontal direction.
- the liquid header 110 is positioned above the first liquid header main pipe 111a positioned below the boss center line Ob1 at the height of the rotational surface of the axial fan 30a disposed below the two axial fans.
- the third liquid header main pipe 111c is located at the lower part of the boss center line Ob2 at the height of the rotational surface of the axial flow fan 30b that is divided into the second liquid header main pipe 111b and disposed above. It is divided into a fourth liquid header main pipe 111d.
- a distributor 54 is provided upstream of the liquid header 110 in order to evenly distribute the refrigerant to the first liquid header main pipe 111a, the second liquid header main pipe 111b, the third liquid header main pipe 111c, and the fourth liquid header main pipe 111d. It has been.
- the distributor 54 and each liquid header main pipe are connected by a first inflow pipe 52a, a second inflow pipe 52b, a third inflow pipe 52c, or a fourth inflow pipe 52d through which the refrigerant flows.
- the outflow pipe 51 is connected to the upper part of the gas header 40 so that the liquid refrigerant easily flows to the upper part of the liquid header 110.
- the connection position of the outflow pipe 51 is not particularly limited to this, and the outflow pipe 51 may be connected to the lower portion of the gas header 40 as in the case of the first embodiment.
- a plurality of branch pipes connected to the first liquid header main pipe 111a arranged below. 112a is inserted in the vicinity of the center of the inner diameter so that the tip portion penetrates the liquid layer.
- the plurality of branch pipes 112b connected to the second liquid header main pipe 111b disposed on the upper side with respect to the boss center line Ob1 are connected so that the tip ends are covered with the liquid phase refrigerant Rb.
- the plurality of branch pipes 112d connected to the fourth liquid header main pipe 111d disposed on the upper side with respect to the boss center line Ob2 are connected so that the tip ends thereof are covered with the liquid phase refrigerant Rb.
- the liquid phase refrigerant Rb is increased in the vicinity of the tube wall of each liquid header main pipe. It becomes a distributed flow pattern.
- the heat exchanger 101 can obtain refrigerant distribution suitable for the airflow distribution of the side flow when the two axial fans 30a and 30b are arranged up and down.
- FIG. 33 is an explanatory diagram showing an example of the air volume distribution of the heat exchanger of the sixth embodiment and the liquid refrigerant distribution of the liquid header.
- the vertical axis represents the height of the heat exchanger 101 in the vertical direction (arrow Z direction)
- the horizontal axis represents the wind speed distribution or the liquid header of the heat exchanger 101, respectively.
- 110 represents the liquid refrigerant flow rate distribution.
- the wind speed distribution has a peak at the height of the bosses 31a and 31b of each axial fan.
- the heat exchanger 101 divides the liquid header 110 vertically with respect to the boss center lines Ob1 and Ob2, respectively, and varies the amount of insertion of the branch pipe 12, as shown in FIG. Refrigerant distribution suitable for the airflow distribution of the side flow when the two axial fans 30a and 30b are arranged vertically can be achieved.
- the inner diameter of the first liquid header main pipe 111a is D 1 [m]
- the inner diameter of the second liquid header main pipe 111b is D 2 [m]
- the inner diameter of the third liquid header main pipe 111c is D 3 [m]
- the fourth liquid is defined as D 4 [m] if D 1 > D 2 and D 3 > D 4 , the difference in flow resistance in each liquid header main pipe due to the difference in the amount of insertion of the branch pipe 12 Is still good to be reduced.
- FIG. 34 shows another example of the heat exchanger according to the sixth embodiment of the present invention.
- the liquid header 110 is divided into four liquid header main pipes and arranged vertically.
- the flow path is the first liquid header flow path inside one liquid header 110.
- the structure may be divided into four parts: 113a, second liquid header flow path 113b, third liquid header flow path 113c, and fourth liquid header flow path 113d.
- the liquid header 110 is composed of one header pipe, the amount of insertion of the branch pipe 12 can be easily managed, and the productivity is excellent.
- the partition wall 14 is formed between the flow paths in the liquid header 110, the pressure strength is improved.
- the side-flow heat exchanger 101 is suitable for a wind speed distribution having a peak at a height near the boss center lines Ob1 and Ob2.
- a liquid refrigerant flow rate distribution can be obtained, and the performance of the heat exchanger 101 is improved.
- the axial fan 30 includes a plurality of axial fans 30a and 30b arranged at different heights in the vertical direction (arrow Z direction), and the blades 32a and 32b of each axial fan.
- the branch pipe 112b is inserted into the header collecting pipe (the first liquid header main pipe 111a and the third liquid header main pipe 111c) so as to be 0 to 50% and is positioned above the height of the bosses 31a and 31b of the axial fans.
- 112d is connected so that the tip is larger than 50% in the distance from the center.
- the liquid header 110 is configured by varying the insertion length of the branch pipe 12 with the height of the bosses 31a and 31b as the boundary for each of the axial fans 30a and 30b. Also in the side-flow heat exchanger 101 in which 30b is arranged in the vertical direction, refrigerant distribution suitable for the wind speed distribution passing through the heat exchanger 101 can be performed, and the performance of the heat exchanger 101 is improved.
- Embodiment 7 FIG.
- the liquid header 10 has a flow path in which the horizontal cross section of the liquid header main pipe 11 is noncircular.
- FIG. 35 is a schematic cross-sectional view showing an example of a liquid header according to Embodiment 7 of the present invention.
- FIG. 36 is a schematic cross-sectional view showing another example of the liquid header according to Embodiment 7 of the present invention.
- FIG. 37 is an explanatory diagram showing an example of the center position of the liquid header according to the seventh embodiment of the present invention.
- 35 and 36 show a case where the horizontal section of the liquid header main pipe 11 is rectangular and the flow path in the liquid header 10 is a rectangular flow path. Even in such a rectangular flow path, a plurality of branch pipes 12 connected to the liquid header main pipe 11 disposed below the boss center line Ob are connected so as to penetrate the liquid layer, thereby causing side flow.
- the refrigerant distribution suitable for the wind speed distribution of the heat exchanger 1 can be realized, and the distribution can be improved.
- the liquid header 10 having a rectangular horizontal cross section has a width direction extending to both sides into which the branch pipe 12 is inserted (as compared with the liquid header 10 having a circular cross section in the horizontal cross section) (The dimension in the direction of the arrow X) can be reduced, and space saving is excellent.
- the joint surface between the liquid header main pipe 11 and the branch pipe 12 is an orthogonal plane. Since the joining of these metals is generally performed by brazing, the liquid header 10 having a rectangular horizontal cross section has a good brazing property of the joining surface during the joining, and the joining quality is improved.
- the center position on the horizontal plane of the circulation space is defined as the intersection of diagonal lines of the rectangular flow path as shown in FIG.
- the diameter of an equivalent circle corresponding to the channel cross-sectional area A of the rectangular channel is used.
- the working fluid of the heat exchanger 1 uses a low-pressure fluorocarbon refrigerant such as R134a, an HFO refrigerant such as R1234yf and R1234ze (E), a hydrocarbon refrigerant such as DME (dimethyl ether), or propane as a pure refrigerant.
- a low-pressure fluorocarbon refrigerant such as R134a, an HFO refrigerant such as R1234yf and R1234ze (E)
- a hydrocarbon refrigerant such as DME (dimethyl ether)
- propane propane
- FIG. 38 is a schematic cross-sectional view showing another example of the liquid header according to Embodiment 7 of the present invention.
- FIG. 39 is an explanatory diagram showing an example of the center position of the liquid header according to the seventh embodiment of the present invention.
- the center position on the horizontal plane of the circulation space is defined as the intersection of the long axis and the short axis center line as shown in FIG. To do.
- the branch pipe 12 protrudes to the vicinity of the center position of the circulation space, there is a concern about the pressure loss of the refrigerant due to the branch pipe 12 protruding into the liquid header 10, but in the liquid header 10 having an elliptical flow path, the liquid header 10 The increase in the pressure loss of the refrigerant flowing through can be suppressed, and the flow mode can be stabilized.
- the liquid header 10 has a structure in which the branch pipe 12 is inserted toward the major axis of the elliptical flow path, that is, in the minor axis direction, so that the horizontal section of the liquid header 10 is circular.
- the curvature of the brazing surface with the branch pipe 12 can be reduced, and the brazing property is improved.
- the diameter of an equivalent circle corresponding to the channel cross-sectional area A of the elliptical channel is used.
- FIG. 40 is a schematic cross-sectional view showing another example of the liquid header according to Embodiment 7 of the present invention.
- FIG. 41 is a schematic cross-sectional view showing another example of the liquid header according to Embodiment 7 of the present invention.
- the flow path in the liquid header 10 is a semicircular flow path. Even in such a semicircular flow path, a plurality of branch pipes 12 connected to the liquid header main pipe 11 disposed below the boss center line Ob are connected so as to penetrate the liquid layer, thereby allowing the side Refrigerant distribution suitable for the wind speed distribution of the flow heat exchanger 1 can be realized, and distribution can be improved.
- the center position on the horizontal plane of the circulation space is defined as an intersection of straight lines connecting the three closest approach positions and the farthest position with respect to the center.
- the diameter of an equivalent circle corresponding to the channel cross-sectional area A of the semicircular channel is used.
- the channel cross-sectional area A can be increased while suppressing an increase in the volume in the width direction (arrow X direction), which is excellent in space saving and low pressure loss. Moreover, such a liquid header 10 can make the joint surface with the branch pipe 12 into a flat plane, and is excellent in brazing.
- FIG. 41 shows a case where the horizontal cross section of the liquid header main pipe 11 has a triangular tube shape, and the flow path in the liquid header 10 is a triangular flow path. Even in such a triangular flow path, a plurality of branch pipes 12 connected to the liquid header main pipe 11 disposed below the boss center line Ob are connected so as to penetrate the liquid layer. Refrigerant distribution suitable for the wind speed distribution of the heat exchanger 1 can be realized, and distribution can be improved.
- the center position in the horizontal plane of the circulation space is a straight line connecting the midpoints of the three closest sides and the farthest corner position. Defined as the intersection of Further, when determining the flow mode, the diameter of an equivalent circle corresponding to the cross-sectional area of the triangular channel is used.
- the channel cross-sectional area A can be increased while suppressing an increase in the volume in the width direction (arrow Y direction), which is excellent in space saving and low pressure loss.
- such a liquid header 10 can make the joint surface with the branch pipe 12 into a flat plane, and is excellent in brazing.
- the flow mode of the refrigerant flowing into the liquid header 10 may be configured to be an annular flow or a churn flow. .
- the improvement effect of distribution performance is acquired in the liquid header 10 of various horizontal cross-sectional shapes.
- the dryness x of the refrigerant flowing into the liquid header 10 is 0.05 ⁇ x ⁇ 0.30, a greater effect of improving the distribution performance can be obtained.
- the heat exchanger 1 has a liquid refrigerant flow rate distribution suitable for the wind speed distribution having a peak near the boss center line Ob. Can be obtained, and the performance of the heat exchanger 1 is improved.
- Embodiment 8 of the present invention will be described below.
- the plurality of branch pipes 12 have a flat tube shape.
- the description overlapping with the first to seventh embodiments is omitted, and the same reference numerals are given to the same or corresponding parts as those of the first to seventh embodiments.
- FIG. 42 is a schematic perspective view showing an example of connection of branch pipes of the liquid header according to the eighth embodiment of the present invention.
- FIG. 43 is a schematic perspective view showing another example of connection of branch pipes of the liquid header 10 according to Embodiment 8 of the present invention.
- the plurality of branch pipes 12 have a flat tube shape.
- the position of the central axis in the Y direction defined above of the branch pipe 12 in this case is located in an area within ⁇ 50% considering the equivalent diameter of the circular pipe with the effective flow area of the flat flow path. It shall be.
- the flat tube-shaped branch pipe 12 may be a part of the heat exchanger 1. That is, a part of the flat heat transfer tube constituting the heat exchanger 1 may be extended to be formed into a flat tube shape.
- a heat transfer promotion shape such as a groove may be processed on the inner surface.
- the plurality of branch pipes 12 connected to the liquid header 10 may have a flat and flat shape having a partition 16 inside the branch pipe 12, and in this case, the strength of the branch pipe 12 is improved. To do.
- the heat exchanger 1 has a liquid refrigerant flow rate distribution suitable for the wind speed distribution having a peak near the boss center line Ob. Can be obtained, and the performance of the heat exchanger 1 is improved.
- the plurality of branch pipes 12 are configured by the end portions of the plurality of heat transfer tubes 22. Thereby, the heat exchanger tube 22 of the heat exchange part 20 can be substituted for the branch tube 12, and the number of parts of the heat exchanger 1 can be reduced.
- FIG. FIG. 44 is a schematic diagram showing an example of a heat exchanger according to Embodiment 9 of the present invention.
- the heat exchanger 1 includes a joint pipe 23 that converts the pipe shapes of the heat transfer pipe 22 and the branch pipe 12.
- the same components as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
- the tube shape can be converted to the branch tube 12 in which the closed area of the liquid header 10 is smaller than the heat transfer tube 22 of the heat exchange unit 20. it can. Therefore, in the liquid header 10, as compared with the case where the heat transfer tube 22 is directly inserted as the branch tube 12, the pressure loss due to the branch tube 12 protruding into the flow path is reduced.
- the joint tube 23 may have one end connected to the heat transfer tube 22 and the other end connected to the branch tube 12, or the branch tube 12 is integrally formed and one end connected to the heat transfer tube 22. It may be a thing.
- the joint pipe 23 is not limited to use in the liquid header 10 but may be used for connection between the gas header 40 and the heat exchange unit 20. In this case, compared with the case where the heat transfer tube 22 is connected to the gas header main pipe 41, the pressure loss due to the insertion of the branch pipe 12 is reduced in the gas header 40.
- FIG. 45 is a partial cross-sectional view showing a BB cross section of FIG.
- the connection state of the heat transfer tube 22, the branch tube 12, and the liquid header main tube 11 when the joint tube 23 is used is shown in a cross-sectional view.
- the width of the branch pipe 12 is defined as Lb [m] and the width of the heat transfer pipe 22 is defined as Lm [m] in the arrow Y direction
- the pressure loss in the liquid header 10 can be reduced when Lb ⁇ Lm.
- the side-flow heat exchanger 1 is a liquid refrigerant suitable for a wind speed distribution having a peak near the boss center line Ob. A flow distribution can be obtained, and the performance of the heat exchanger 1 is improved.
- the plurality of branch pipes 12 are joint pipes 23 attached to the end portions of the plurality of heat transfer pipes 22.
- FIG. FIG. 46 is a schematic diagram showing an example of a heat exchanger according to Embodiment 10 of the present invention.
- FIG. 47 is a schematic diagram showing the relationship between the liquid header according to Embodiment 10 of the present invention, the liquid refrigerant flow rate, and the air volume distribution.
- the heat exchanger 201 includes a liquid header 210, a gas header 40, a heat exchange unit 20, and a plurality of branch pipes 12 and 212 that connect the liquid header 210 and the gas header 40 to the heat exchange unit 20.
- the heat exchanger 201 is a top-flow heat exchanger 201 in which the fan 35 is disposed on the upper surface.
- symbol is attached
- the liquid header 210 is configured by connecting a plurality of branch pipes 212 to a liquid header main pipe 211.
- the liquid header 210 is disposed upstream of the heat exchange unit 20, and the heat exchange unit 20 and the liquid header 210 are connected by a plurality of branch pipes 212.
- An inflow pipe 52 is connected to the lower end of the liquid header 210, and a gas-liquid two-phase refrigerant flows from the refrigerant circuit into the liquid header 210.
- the fan 35 includes a boss 36 and blades 37 arranged around the boss 36, and supplies air to the heat exchanger 201 by rotation.
- the fan 35 passes air from the side surface of the heat exchanger 201 and sends it upward in the vertical direction (arrow Z direction).
- the wind speed becomes maximum at a position close to the fan 35, that is, at the top of the heat exchanger 201. Therefore, all the branch pipes 212 of the liquid header 210 may be inserted near the inner diameter center of the liquid header main pipe 211.
- the vertical axis represents the height of the heat exchanger 201
- FIG. 47A shows the configuration of the liquid header 210
- FIG. 47B shows the liquid refrigerant flow rate distribution of the liquid header 210
- FIG. The air volume distribution of the heat exchanger 201 is shown.
- the airflow distribution of the top flow heat exchanger 201 is suitable. Refrigerant distribution is obtained and the performance of the heat exchanger is improved.
- the heat exchanger 201 is connected to the height 75% to 100% of the plurality of branch pipes 212.
- the upper branch pipe 212b is inserted into the liquid header main pipe 211 so that the tip is covered with the liquid layer. Even in this case, the characteristics of the liquid refrigerant distribution are almost the same as the above-described configuration in which all the branch pipes 212 are inserted to the vicinity of the center of the inner diameter. Therefore, the pressure loss may be reduced if the tip position of the branch pipe 212b connected to the height of 75% to 100% is not inserted into the liquid header 210.
- the dryness x of the refrigerant is 0.05 ⁇ x ⁇ 0.30.
- it is inserted to penetrate the liquid layer.
- at least the lower branch pipe 212a among the plurality of branch pipes 212 connected to the liquid header 210 is inserted so as to penetrate the liquid layer, so that the top flow heat as shown in FIG. Liquid refrigerant distribution suitable for the exchanger 201 can be realized, the performance of the heat exchanger 201 is improved, and the energy efficiency is improved.
- the amount of insertion of the branch pipe 212 is different with a 75% height position as a boundary, but the present invention is not limited to this.
- most of the plurality of branch pipes 212 connected to the liquid header 210 are inserted so that the tip portion penetrates the liquid layer, and at least the uppermost branch pipe is covered with the liquid layer. It may be configured to be connected.
- the majority of the plurality of branch pipes 212 means that more than half of all the branch pipes 212, and within this range, the height position serving as the above-mentioned boundary is the air volume distribution and liquid of the heat exchange unit 20. It may be determined according to the stagnation region length Lt at the top of the header 210 or the flow pattern of the refrigerant.
- connection position of the inflow pipe 52 is not limited to the lower end of the liquid header 10, and is inserted anywhere as long as it is a space constituted by the lower end of the liquid header 10 and the center line of the branch pipe 12 closest to the lower end. It may be.
- the heat transfer pipe 22 of the heat exchange unit 20 may be extended and connected to the liquid header main pipe 211.
- the shape of the branch pipe 12 is not limited to a circular pipe, and may be a flat pipe, for example.
- the plurality of connected branch pipes 212a only need to penetrate the liquid layer of the refrigerant flowing in the liquid header main pipe 211, and the tip portion is the center. You may be located in the range with the breadth of neighborhood.
- FIG. 48 is an external view showing an example of an outdoor unit equipped with a top-flow heat exchanger according to Embodiment 10 of the present invention.
- the broken line arrow in a figure represents the flow of air.
- An outdoor unit 100 equipped with a top-flow heat exchanger 201 as shown in FIG. 48 constitutes a refrigeration cycle circuit by circulating a refrigerant with an indoor unit (not shown).
- the outdoor unit 100 is used, for example, in a building multi-unit outdoor unit or the like, and is installed on the roof of a building.
- the outdoor unit 100 includes a casing 102 formed in a box shape.
- a suction port 103 is formed on the side surface of the casing 102 by an opening, and an air outlet 104 is formed on the upper surface by the opening.
- the outdoor unit 100 includes the heat exchanger 201 in the casing 102 along the suction port 103.
- the outdoor unit 100 includes a fan guard 105 that can ventilate so as to cover the air outlet 104.
- the outdoor unit 100 includes a top flow type fan 35 that is disposed inside the fan guard 105 and sucks the outside air from the suction port 103 and discharges the outside air from the air outlet 104.
- FIG. 49 is a diagram showing a relationship between a parameter (M R ⁇ x) / (31.6 ⁇ A) related to the thickness of the liquid phase and the performance of the heat exchanger according to the tenth embodiment of the present invention. .
- the liquid phase thickness is an important parameter for refrigerant distribution along the airflow distribution of the top flow type fan 35.
- the maximum refrigerant flow rate [kg / h] flowing through the liquid header 210 is M R
- the refrigerant dryness is x
- the liquid header is
- the effective channel cross-sectional area [m 2 ] of the main pipe 211 is defined as A
- the parameter (M R ⁇ x) / (31.6 ⁇ A) related to the liquid film thickness (liquid phase thickness) of the refrigerant is 0.010 ⁇ 10 6 ⁇ (M R ⁇ x) / (31 .6) It is even better if it is in the range of ⁇ 0.120 ⁇ 10 6 . In this case, the distribution performance can be improved over a wide range of operating conditions.
- the maximum refrigerant flow rate M R can be the flow rate of refrigerant during the heating rated operation, to measure the compressor input and the indoor function forces, or by the number of operating units such as the speed and the indoor unit of the compressor.
- FIG. 50 is a diagram showing a relationship between a parameter (M R ⁇ x) /31.6 related to the liquid film thickness of the refrigerant according to Embodiment 10 of the present invention and the performance of the heat exchanger.
- M R ⁇ x parameter
- the inner diameter D [m] of the liquid header 210 is in the range of 0.010 ⁇ D ⁇ 0.018 and 0. .427 ⁇ (M R ⁇ x) /31.6 ⁇ 5.700 is preferably satisfied.
- coolant flows into the liquid header 210 with the optimal liquid film thickness, and distribution performance can be improved.
- FIG. 51 is a diagram showing the relationship between the parameter x / (31.6 ⁇ A) representing the flow mode independent of the flow rate of the refrigerant and the performance of the heat exchanger according to the tenth embodiment of the present invention.
- the parameter x / (31.6 ⁇ A) satisfies the condition of 1.4 ⁇ 10 ⁇ x / (31.6 ⁇ A) ⁇ 8.7 ⁇ 10.
- the optimum refrigerant distribution performance for the airflow distribution of the top flow type fan 35 can be obtained regardless of the refrigerant flow rate.
- FIG. 52 is a diagram showing a relationship between an apparent gas velocity U SG [m / s] and an effect of improving distribution performance according to Embodiment 10 of the present invention.
- the gas apparent speed U SG satisfies the range of 1 ⁇ U SG ⁇ 10
- the performance deterioration due to the deterioration of distribution can be reduced to 1 ⁇ 2 or less.
- the apparent gas velocity U SG [m / s] is the refrigerant flow rate G [kg / (m 2 s)] flowing into the liquid header 210, the dryness x of the refrigerant, and the refrigerant gas density ⁇ G [kg / m 3].
- the air conditioner has a plurality of heat transfer tubes 22 that are spaced apart from each other in the vertical direction (arrow Z direction) and that has a flow space that extends in the vertical direction.
- a heat exchanger 201 having a header collecting pipe (liquid header main pipe 211) for allowing the refrigerant to flow into the plurality of heat transfer pipes 22 from the plurality of branch pipes 212 spaced apart in the vertical direction, and the plurality of heat transfer pipes 22, a fan 35 positioned above 22, and a refrigerant circuit that causes the refrigerant to flow into the flow space so that the refrigerant in a gas-liquid two-phase state flows upward, and evaporates the refrigerant in the heat exchanger 201
- the refrigerant flowing through the pipe is an annular flow or churn flow in which the gas-phase refrigerant Ra gathers at the center of the header collecting pipe and the liquid-phase refrigerant Rb gathers on the wall surface, and the center in the horizontal plane of the
- the branch pipes 212 connected to the header collecting pipe (for example, the branch pipe 212a) Is inserted into the header collecting pipe so that the distance from the center is 0 to 50%, and the branch pipe (for example, 212b) located at the uppermost part of the branch pipe connected to the header collecting pipe has a tip from the center. It is connected to the header collecting pipe so that it becomes larger than 50% at the distance of.
- the top flow heat exchanger 201 in which the fan 35 is disposed above the heat exchanger 201 can obtain a liquid refrigerant flow rate distribution suitable for the wind speed distribution having a peak at a position closest to the fan 35.
- the performance of the heat exchanger 1 is improved and energy efficiency is improved.
- FIG. 53 is a schematic diagram showing an example of a heat exchanger according to Embodiment 11 of the present invention.
- the liquid header 310 is divided into at least two.
- the same components as those in the tenth embodiment are denoted by the same reference numerals, description thereof is omitted, and only different components are described.
- the liquid header 310 is divided into upper and lower main pipes, and includes a lower first liquid header main pipe 311a and an upper second liquid header main pipe 311b. That is, the second liquid header main pipe 311 b is disposed at a position closest to the fan 35 in the liquid header 310.
- the plurality of branch pipes 312b connected to the upper second liquid header main pipe 311b are inserted so as to penetrate the liquid layer.
- the plurality of branch pipes 312a connected to the lower first liquid header main pipe 311a may be inserted so that the tip part penetrates the liquid layer, or connected so that the tip part is covered with the liquid layer. May be.
- the inner diameter D 11 [m] of the first liquid header main pipe 311a is equal to the inner diameter D of the second liquid header main pipe 311b. It may be configured to be smaller than 12 [m].
- all of the plurality of branch pipes 312b connected to the upper second liquid header main pipe 311b pass through the liquid layer of the refrigerant flowing through the liquid header 310, and are connected to the lower first liquid header main pipe 311a.
- all of the plurality of branch pipes 312 a are connected so as to remain in the liquid layer of the refrigerant flowing through the liquid header 310.
- more than half of the plurality of branch pipes 312b penetrate the liquid layer of the refrigerant flowing through the liquid header 310, and more than half of the plurality of branch pipes 312a remain in the liquid layer of the refrigerant flowing through the liquid header 310. If it is connected, the heat exchanger 301 can obtain the effect of distribution improvement.
- FIG. 54 is a diagram showing an example of the liquid refrigerant flow rate distribution of the liquid header and the air volume distribution of the heat exchanger according to Embodiment 11 of the present invention.
- the vertical axis represents the position of the branch pipe 312 in the vertical direction (arrow Z direction)
- FIG. 54A shows the liquid refrigerant flow rate with respect to the branch pipe 312 position
- FIG. 54B shows the position with respect to the branch pipe 312 position.
- the air volume is shown.
- a broken line C1 in the figure represents the liquid refrigerant flow rate suitable for the top flow air volume distribution.
- the tip of the plurality of branch pipes 312b connected to the second liquid header main pipe 311b is connected so as to penetrate the liquid layer, so that the liquid refrigerant is placed above the liquid header 310 at a position close to the fan. Can be distributed more.
- FIG. 55 is a diagram showing another example of the liquid refrigerant flow rate distribution of the liquid header according to Embodiment 11 of the present invention.
- FIG. 55 shows the distribution of the liquid refrigerant when the tips of the plurality of branch pipes 312a connected to the first liquid header main pipe 311a are covered with the liquid layer.
- tip position of the branch pipe 312 is small.
- the distribution of the liquid refrigerant at the upper part of the liquid header 310 can be improved, which is indicated by a broken line C1. It is possible to approximate a liquid refrigerant distribution suitable for such a top flow air volume distribution.
- the inner diameter D 11 of the first liquid header main 311a and the inner diameter D 12 of the second liquid header main 311b it is more preferable to is D 12> D 11.
- the liquid header 310 may not be divided into a plurality of main pipes.
- the flow path in the liquid header may be divided into a plurality of parts by the partition wall 14 or the like.
- the air conditioner has a plurality of heat transfer tubes 22 that are spaced apart from each other in the vertical direction (arrow Z direction) and that has a flow space that extends in the vertical direction.
- header collecting pipes first liquid header main pipe 311a and second liquid header main pipe 311b that allow the refrigerant to flow into the plurality of heat transfer pipes 22 from the plurality of branch pipes 312 that are spaced apart in the vertical direction.
- the refrigerant is introduced into the exchanger 301, the fan 35 positioned above the plurality of heat transfer tubes 22, and the refrigerant so that the gas-liquid two-phase refrigerant flows upward, and the refrigerant is evaporated by the heat exchanger 301.
- a refrigerant circuit, and a flow mode of the refrigerant flowing in the header collecting pipe is an annular flow or a churn flow in which the gas phase refrigerant Ra gathers in the center of the header collecting pipe and the liquid phase refrigerant Rb gathers on the wall surface.
- the collecting pipe is composed of a plurality of header collecting pipes (first liquid header main pipe 311a, second liquid header main pipe 311b) arranged at different heights in the vertical direction, and is centered on the horizontal plane of the distribution space.
- the header collecting pipe closest to the fan 35 (second liquid header main pipe 311b)
- most of the branch pipes 312b to be connected are inserted such that the tip is 0 to 50% in the distance from the center, and the header collecting pipe located at a position lower than the header collecting pipe located closest to the fan 35.
- most of the branch pipes 312a to be connected are connected such that the tip is larger than 50% in the distance from the center.
- the air conditioner is inserted so that most of the branch pipe 312b penetrates the liquid layer. It is. Therefore, when the liquid phase refrigerant Rb is distributed on the wall surface in the liquid header 310, the second liquid header main pipe 311b closest to the fan 35 can distribute the liquid refrigerant in the upper part. Therefore, the top-flow heat exchanger 301 in which the fan 35 is disposed above the heat exchanger 301 can obtain a liquid refrigerant flow rate distribution suitable for the wind speed distribution having a peak at a position closest to the fan 35. As a result, in the air conditioner, the performance of the heat exchanger 301 is improved and energy efficiency is improved.
- header collection pipe located closest to the fan 35 the inner diameter D 12 of the (second liquid header main 311b) circulation space of the header collection pipe located at a position lower than the header collection pipe located closest to the fan 35 larger than the inner diameter D 11 (first liquid header main 311a) distribution space.
- the heat exchanger 301 can distribute a large amount of liquid refrigerant in the upper part of the liquid header 310 and perform refrigerant distribution suitable for the wind speed distribution of the top-flow heat exchanger 301.
- FIG. 56 is a circuit diagram showing an example of a refrigerant circuit of the air-conditioning apparatus according to Embodiment 12 of the present invention.
- the air conditioner 200 according to the twelfth embodiment may be mounted with any of the heat exchangers according to the first to eleventh embodiments.
- a heat exchanger 201 (hereinafter referred to as an outdoor heat exchanger) using the liquid header 210 described in the tenth embodiment is replaced with a compressor 61, a first expansion device 62, and an indoor heat exchanger 26.
- An air conditioner 200 that is connected to each other by a refrigerant pipe to form a refrigeration cycle circuit and is capable of heating operation will be described.
- An air conditioner 200 shown in FIG. 56 connects an outdoor unit 100 including a liquid header 210 and an outdoor heat exchanger (heat exchanger 201) to an indoor unit 25 including an indoor heat exchanger 26 and the like.
- the compressor 61 compresses the refrigerant
- the first expansion device 62 depressurizes the refrigerant.
- the air conditioning apparatus 200 includes a control device 70 that controls the operation.
- the control device 70 is composed of a CPU, ROM, RAM, and a microcomputer provided with an I / O port.
- the control device 70 is connected to various sensors via a wireless or wired control signal line, and is configured to receive detection information.
- the control device 70 adjusts, for example, the dryness of the refrigerant flowing into the liquid header main pipe 211 according to the operating conditions. Specifically, the control device 70 controls the first throttling device 62 according to the operation mode, the number of connected indoor units 25, the frequency of the compressor 61, the outside air temperature, the indoor temperature, and the like. The dryness x of the refrigerant flowing in is adjusted.
- the refrigerant becomes a high-temperature and high-pressure gas state in the compressor 61, flows through the compressor discharge pipe 93, and flows into the indoor unit 25.
- the gas refrigerant is cooled by exchanging heat with room air in the indoor heat exchanger 26 in the indoor unit 25.
- the liquid refrigerant that has become high pressure and low temperature in the indoor heat exchanger 26 flows through the indoor unit outlet pipe 17 and then flows into the first expansion device 62.
- the refrigerant is depressurized to become a low-temperature low-pressure gas-liquid two-phase refrigerant or liquid refrigerant.
- the refrigerant flows through the inflow pipe 52 and flows into the liquid header 210.
- the refrigerant is distributed to the plurality of heat transfer tubes 22, absorbs heat in the heat exchange unit 20, and returns to the compressor 61 through the gas header 40 and the outflow tube 51.
- the refrigerant returned to the compressor 61 is compressed again to become a high-temperature and high-pressure refrigerant and circulates in the refrigerant circuit.
- control device 70 can adjust the degree of pressure reduction by changing the opening degree of the first expansion device 62 according to the operating conditions, and can adjust the dryness of the refrigerant in the liquid header 210.
- the heating rated operation (100% heating operation)
- refrigerant distribution suitable for the arrangement of the fan 35 and the heat exchanger 201 such as top flow or side flow can be realized in the liquid header 210, and the performance of the heat exchanger 201 can be improved.
- the energy efficiency of the harmony device 200 is improved.
- FIG. 57 is a circuit diagram showing an example of sensor arrangement of the air-conditioning apparatus according to Embodiment 12 of the present invention.
- the air conditioning apparatus 200 includes a first temperature sensor 66, a second temperature sensor 67, a third temperature sensor 68, and the like.
- the 1st temperature sensor 66 is installed in the heat exchanger tube of the indoor heat exchanger 26, for example, and measures the saturation temperature of the indoor heat exchanger 26.
- the second temperature sensor 67 is installed in the indoor unit outlet pipe 17 and measures the temperature of the refrigerant flowing into the first expansion device 62.
- the third temperature sensor 68 is installed in the inflow pipe 52 and measures the saturation temperature downstream of the first throttling device 62. Detection information of these temperature sensors is transmitted to the control device 70.
- the air conditioner 200 estimates the refrigerant dryness x based on the detection information of the plurality of temperature sensors.
- the air conditioner 200 can estimate the temperature and pressure of the refrigerant flowing into the first throttle device 62 by the first temperature sensor 66 and the second temperature sensor 67, and thereby flow into the first throttle device 62. It is possible to estimate the enthalpy of the refrigerant. Further, the air conditioner 200 assumes that the refrigerant change before and after passing through the first throttle device 62 is an isenthalpy process, and measures the saturation temperature downstream of the first throttle device 62 with the third temperature sensor 68. Then, the pressure of the refrigerant is estimated. Thereby, since the refrigerant
- the air conditioner 200 includes a plurality of temperature sensors, so that the refrigerant dryness x is 0.05 ⁇ x ⁇ 0.30 even under various operating conditions.
- the opening degree can be adjusted, and the appropriate range of refrigerant distribution in the liquid header 210 can be expanded.
- temperature sensors may be substituted with pressure sensors or information such as compressor frequency, operating mode or number of indoor units.
- the cooling operation and the heating operation may be switched.
- the refrigerant flow is reversed from that during the heating operation, and high-temperature and high-pressure refrigerant gas flows through the outdoor heat exchanger (heat exchanger 201), and is cooled by heat exchange with the outside air.
- the heat exchanger 201 of the air conditioner 200 is a liquid refrigerant suitable for the wind speed distribution having a peak at a position closest to the fan 35. A flow distribution can be obtained. As a result, the performance of the heat exchanger 1 is improved, and energy efficiency is improved in the air conditioner 200.
- the air conditioner 200 includes the air conditioner described above and the control device 70 that adjusts the dryness x of the refrigerant flowing into the header collecting pipe (liquid header main pipe 211) according to the operating conditions.
- the first expansion device 62 is provided upstream of the header collecting pipe in the refrigerant flow during the heating operation, and the control device 70 controls the first expansion device 62.
- the air conditioner 200 can adjust the dryness x of the refrigerant in the liquid header 210 by controlling the first throttle device 62.
- refrigerant distribution suitable for the arrangement of the fan 35 and the heat exchanger 201 can be realized in the liquid header 210, the performance of the heat exchanger 201 can be improved, and the energy efficiency of the air conditioner 200 can be improved. improves.
- control device 70 adjusts the dryness x of the refrigerant flowing into the liquid header collecting pipe (liquid header main pipe 211) so as to be within the range of 0.05 ⁇ x ⁇ 0.30 during the heating operation.
- the air conditioning apparatus 200 can extend the appropriate range of refrigerant distribution in the liquid header 210.
- FIG. FIG. 58 is a circuit diagram showing an example of a refrigerant circuit of the air-conditioning apparatus according to Embodiment 13 of the present invention.
- an air conditioner 200a is obtained by further providing a gas-liquid separation container 84 to the air conditioner 200 of the twelfth embodiment.
- the same components as those in the twelfth embodiment are denoted by the same reference numerals, description thereof is omitted, and only components different from those in the twelfth embodiment are described.
- the gas-liquid separation container 84 is provided between the liquid header 210 and the first throttling device 62, and the first throttling device 62 and the gas-liquid separation container 84 are connected by a connection pipe 47.
- An inflow pipe 52 connected to the liquid header 210 is connected to the lower part of the gas-liquid separation container 84.
- a bypass pipe 82 connected to the outflow pipe 51 is connected to the upper part of the gas-liquid separation container 84, and a bypass adjustment valve 83 is provided on the bypass pipe 82.
- the bypass pipe 82 bypasses the gas refrigerant separated in the gas-liquid separation container 84 to the compressor 61, and the opening of the bypass adjustment valve 83 can be changed by the control device 70.
- FIG. 59 is a schematic diagram showing an example of the configuration of a gas-liquid separation container according to Embodiment 13 of the present invention.
- the connection pipe 47 on the upstream side of the gas-liquid separation container 84 is connected to the side surface of the gas-liquid separation container 84, and the bypass pipe 82 is the center of the connection pipe 47 in the gas-liquid separation container 84. Connected to the top of the line.
- the gas-liquid two-phase refrigerant that has flowed into the connection pipe 47 flows into the gas-liquid separation container 84 and is separated into gas and liquid by gravity, the gas refrigerant flows into the bypass pipe 82, and the liquid refrigerant flows into the inflow pipe 52. It flows.
- the control device 70 controls the bypass adjusting valve 83 to close when the dryness x of the refrigerant flowing through the inflow pipe 52 is x ⁇ 0.05, and when x> 0.30, By controlling the adjustment valve 83 in the opening direction, the dryness x of the refrigerant flowing into the liquid header 210 is controlled to 0.05 ⁇ x ⁇ 0.30.
- the air conditioning apparatus 200a can appropriately distribute the refrigerant to the liquid header 210, improve the efficiency of the heat exchanger 201, and improve the energy efficiency. Further, the air conditioner 200a includes the gas-liquid separation container 84, so that the operating condition range in which distribution can be improved is further expanded.
- FIG. 60 is a schematic diagram showing another example of the configuration of the gas-liquid separation container according to Embodiment 13 of the present invention.
- a gas-liquid separation container 84 is configured using a T-shaped pipe 85.
- arrows indicate the flow of the refrigerant, and a configuration is shown in which the gas-liquid two-phase refrigerant flows into the pipe 85, the gas refrigerant flows from above, and the liquid refrigerant flows out from below.
- the air conditioning apparatus 200a can adjust the dryness x at low cost.
- FIG. 61 is a schematic diagram showing another example of the configuration of the gas-liquid separation container according to Embodiment 13 of the present invention.
- a gas-liquid separation container 84 is configured using a Y-shaped tube 86.
- the inflow pipe 52 has an inclination and is connected to the Y-shaped pipe 86, and as shown in FIG. 61, the gas-liquid two-phase refrigerant flows into the Y-shaped pipe 86 and the gas and liquid are separated.
- the liquid refrigerant having a higher density is more likely to flow to the lower pipe due to inertial force, and the gas-liquid separation efficiency is higher. Therefore, the operating condition range in which distribution can be improved can be expanded.
- gas-liquid separation container has been described above, only an example of a collision-type gas-liquid separation container is shown here.
- other collision type gas-liquid separation containers, gas-liquid separation containers using surface tension, or gas-liquid separation containers using centrifugal force may be employed.
- the air conditioning apparatus 200a can reduce the gas refrigerant which flows into the heat exchanger 201 by bypassing the gas refrigerant using the gas-liquid separation container 84 as described above, and the pressure loss in the heat exchanger 201 can be reduced. Can be reduced. As a result, the air conditioner 200a can improve the performance of the heat exchanger 201 by reducing the pressure loss in addition to improving the refrigerant distribution.
- the control device 70 may control the bypass adjustment valve 83 so that the dryness x of the refrigerant flowing into the liquid header 210 is 0.05 ⁇ x ⁇ 0.30 under the heating rated condition.
- bypass adjustment valve 83 has been described as being capable of adjusting the opening, any configuration may be used as long as the refrigerant flow rate of the bypass pipe 82 can be adjusted (bypass flow rate adjustment mechanism).
- the heat exchanger 201 of the air conditioner 200a is a liquid refrigerant suitable for the wind speed distribution having a peak at a position closest to the fan 35. A flow distribution can be obtained. As a result, the performance of the heat exchanger 201 is improved, and the energy efficiency of the air conditioner 200a is improved.
- the refrigerant circuit includes a gas-liquid separation container 84 (gas-liquid separation container 84, pipe 85 or Y-shaped pipe 86) provided between the first throttle device 62 and the header collecting pipe (liquid header main pipe 211).
- the bypass pipe 82 that connects the gas-liquid separation container 84 and the downstream of the heat exchanger 201 in the refrigerant flow during heating operation, and a bypass flow rate adjustment mechanism that is provided on the bypass pipe 82 and adjusts the flow rate of the refrigerant (for example, And a bypass regulating valve 83).
- the air conditioning apparatus 200a separates the gas-liquid two-phase refrigerant in the gas-liquid separation container 84, and controls the bypass adjustment valve 83 to adjust the dryness x of the refrigerant flowing into the liquid header 210. be able to. Therefore, the air conditioner 200a can appropriately distribute the refrigerant to the liquid header 210, improve the efficiency of the heat exchanger 201, and improve energy efficiency.
- FIG. FIG. 62 is a circuit diagram showing an example of a refrigerant circuit of the air-conditioning apparatus according to Embodiment 14 of the present invention.
- the air conditioner 200b is configured to be able to switch between a heating operation and a cooling operation.
- the solid arrow in the figure represents the refrigerant flow during the heating operation.
- the description of the same components as those in the thirteenth embodiment is omitted, and the same or corresponding portions as those in the thirteenth embodiment are denoted by the same reference numerals.
- the air conditioner 200b further includes a flow path switching device 94, an accumulator 91, and a second throttling device 90.
- the flow path switching device 94 is composed of, for example, a four-way valve or the like, and switches the refrigerant flow between the cooling operation and the heating operation.
- the accumulator 91 is provided on the suction side of the compressor 61, and an accumulator inflow pipe 92 is provided on the upstream side of the accumulator 91.
- the second expansion device 90 is provided between the gas-liquid separation container 84 and the liquid header 10, that is, on the inflow pipe 52. The opening degree of the second expansion device 90 is adjusted by the control device 70.
- the distribution may be improved.
- the gas density of the refrigerant is increased, the flow velocity of the refrigerant flowing into the gas-liquid separation container 84 is reduced, and the small-sized gas-liquid separation is performed. Even in the container 84, high gas-liquid separation efficiency can be obtained.
- the opening degree is controlled to be small so that the flow resistance of the second expansion device 90 is large.
- FIG. 62 has been described with respect to the heating operation, the flow direction of the refrigerant is reversed by the flow path switching device 94 during cooling.
- excess refrigerant can be stored in the gas-liquid separation container 84 by depressurizing the refrigerant in two stages of the second expansion device 90 and the first expansion device 62, and also function as an auxiliary device for the accumulator 91. be able to.
- the processing amount of the surplus refrigerant is determined by adjusting the opening degree of the first expansion device 62 and the second expansion device 90, and can be changed by the pressure of the gas-liquid separation container 84.
- the refrigerant amount can be easily adjusted even during the cooling operation, and the performance of the air conditioner 200b can be improved.
- the gas-liquid separation container 84 can be used as an auxiliary device for the accumulator 91 during the cooling operation, the capacity of the accumulator 91 can be reduced.
- the heat exchanger 201 is shown as an example of the form relating to the fan 35 having the top flow arrangement, but any heat exchanger may be used as long as it is the heat exchanger described in the first to thirteenth embodiments. good.
- the heat exchanger 201 of the air conditioner 200b is a liquid refrigerant suitable for the wind speed distribution having a peak at a position closest to the fan 35. A flow distribution can be obtained. As a result, the performance of the heat exchanger 201 is improved and the energy efficiency of the air conditioner 200b is improved.
- the refrigerant circuit of the air conditioner 200b further includes a flow path switching device 94 that switches the flow of the refrigerant, and a second provided between the heat exchanger 201 and the first expansion device 62.
- the control device 70 controls the flow path switching device 94, the first throttle device 62, and the second throttle device 90.
- the air conditioning apparatus 200b improves the gas-liquid separation efficiency in the gas-liquid separation container 84 and controls the dryness x of the refrigerant flowing into the liquid header 10 by the control of the second expansion device 90 during the heating operation.
- the adjustable operating range is expanded. Further, since the air conditioner 200b includes the second throttle device 90 and the first throttle device 62, the refrigerant amount can be easily adjusted even during the cooling operation, and the performance of the air conditioner 200 can be improved. .
- the embodiment of the present invention is not limited to the above embodiment, and various changes can be made.
- the case where the number of indoor units 25 is one has been described.
- the present invention is not limited to this, and a plurality of indoor units 25 may be connected.
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Abstract
Description
図1~図4に基づき、熱交換器1について説明する。図1は、本発明の実施の形態1に係る熱交換器の一例を示す概略図である。図2は、本発明の実施の形態1に係る伝熱管を示す図である。図3は、本発明の実施の形態1に係る伝熱管の一例を示す図である。図4は、本発明の実施の形態1に係る伝熱管の他の一例を示す図である。
図19は、本発明の実施の形態2に係る熱交換器の一例を示す概略図である。実施の形態2において、1つの軸流ファン30は熱交換器1の側面に配置され、液ヘッダー10は、液ヘッダー主管11が軸流ファン30のボス31のボス中心線Obに対して上下に2分割され、下部が第1液ヘッダー主管11a、上部が第2液ヘッダー主管11bを構成している。液ヘッダー10において、ボス中心線Obよりも下部に位置する複数の枝管12aは、第1液ヘッダー主管11aに接続され、液層を貫くように第1液ヘッダー主管11aの内径中心付近まで差し込まれている。一方、ボス中心線Obよりも上部に位置する複数の枝管12bは、第2液ヘッダー主管11bに、液層に覆われるように接続されている。そして、第1液ヘッダー主管11aの上流には第1流入管52aが接続され、第2液ヘッダー主管11bの上流には第2流入管52bが接続される。図19では、第1流入管52aおよび第2流入管52bはそれぞれ、第1液ヘッダー主管11aまたは第2液ヘッダー主管11bの下端に接続されているが、接続位置は特にこれに限定されない。
図26は、本発明の実施の形態3に係る熱交換器の一例を示す概略図である。実施の形態3において、サイドフローの熱交換器1は、実施の形態2の場合と同様に液ヘッダー10の主管が上下に2つに分割されている。そして下部の第1液ヘッダー主管11aには第1流入管52aが接続され、上部の第2液ヘッダー主管11bには第2流入管52bが接続されている。また実施の形態3において、熱交換器1は、さらに、第1流入管52a上に配置された第1流量調整機構53を備える。以下、実施の形態3において、実施の形態2と異なる構成についてのみ説明し、同一または対応する構成については同一符号を付し、説明を省略する。
図29は、本発明の実施の形態4に係る熱交換器の一例を示す概略図である。実施の形態4において、サイドフローの熱交換器1は、実施の形態2の場合と同様に、液ヘッダー10の主管が上下2つに分割されている。そして、下部の第1液ヘッダー主管11aには第1流入管52aが接続され、上部の第2液ヘッダー主管11bには第2流入管52bが接続されている。実施の形態4では、液ヘッダー10の主管のサイズが上下で異なる。以下、実施の形態4において、実施の形態2と異なる構成についてのみ説明し、同一または対応する構成には同一符号を付し、説明を省略する。
図31は、本発明の実施の形態5に係る熱交換器の一例を示す概略図である。実施の形態5において、サイドフローの熱交換器1は、液ヘッダー10に流路が複数形成されている。以下、実施の形態2と異なる構成についてのみ説明し、同一または対応する構成については同一符号を付し、説明を省略する。
図32は、本発明の実施の形態6に係る熱交換器の一例を示す概略図である。実施の形態6において、サイドフローの熱交換器101は、側面に上下に2つの軸流ファン30a、30bを備えている。また実施の形態6において、液ヘッダー110は、各ボス31a、31bのボス中心線Ob1、Ob2に対してそれぞれ上下2つに分割され、4つの主管から構成されている。以下、実施の形態2と異なる構成についてのみ説明し、同一または対応する構成については同一符号を付し、説明を省略する。
以下、本発明の実施の形態7について説明する。ここで、実施の形態1~6と重複するものについては説明を省略し、実施の形態1~6と同じ部分または相当する部分には同じ符号を付す。実施の形態7において、液ヘッダー10は、液ヘッダー主管11の水平断面が非円形状である流路を有している。
以下、本発明の実施の形態8について説明する。実施の形態8では、複数の枝管12は、扁平管形状である。ここで、実施の形態1~7と重複するものについては説明を省略し、実施の形態1~7と同じ部分または相当する部分には同じ符号を付す。
図44は、本発明の実施の形態9に係る熱交換器の一例を示す概略図である。実施の形態9において、熱交換器1は、伝熱管22と枝管12の管形状を変換するジョイント管23を備えている。以下、実施の形態1と同様の構成については同一の符号を付し、説明を省略する。
図46は、本発明の実施の形態10に係る熱交換器の一例を示す概略図である。図47は、本発明の実施の形態10に係る液ヘッダーと、液冷媒流量および風量分布の関係を示した概略図である。熱交換器201は、液ヘッダー210と、ガスヘッダー40と、熱交換部20と、熱交換部20に液ヘッダー210およびガスヘッダー40を接続する複数の枝管12、212等で構成される。実施の形態10において、熱交換器201は、上面にファン35が配置されたトップフローの熱交換器201である。以下、実施の形態10において、実施の形態1の場合と同様の構成については同一符号を付し、説明を省略する。
図53は、本発明の実施の形態11に係る熱交換器の一例を示した概略図である。実施の形態11において、トップフローの熱交換器301は、液ヘッダー310が少なくとも2つに分割されている。以下、実施の形態11において、実施の形態10と同じ構成については同一符号を付して説明を省略し、異なる構成についてのみ説明する。
以下、本発明の実施の形態12について説明する。図56は、本発明の実施の形態12に係る空気調和装置の冷媒回路の一例を示す回路図である。ここで、実施の形態10と重複するものについては説明を省略し、実施の形態10と同じ部分または相当する部分については同じ符号を付す。なお、実施の形態12の空気調和装置200は、実施の形態1~11の熱交換器のいずれを搭載するものであってもよい。
図58は、本発明の実施の形態13に係る空気調和装置の冷媒回路の一例を示す回路図である。実施の形態13において、空気調和装置200aは、実施の形態12の空気調和装置200に、さらに気液分離容器84を備えたものである。以下、実施の形態13において、実施の形態12と同一の構成については同一符号を付して説明を省略し、実施の形態12と異なる構成についてのみ説明する。
図62は、本発明の実施の形態14に係る空気調和装置の冷媒回路の一例を示す回路図である。実施の形態14において、空気調和装置200bは、暖房運転と冷房運転とを切り替え可能に構成されている。図中の実線矢印は、暖房運転時の冷媒流れを表している。ここで、実施の形態13と重複する構成については説明を省略し、実施の形態13と同じ部分または相当する部分については同じ符号を付す。
Claims (14)
- 上下方向に離間して配列され、冷媒が流れる複数の伝熱管と、内部に上下方向にのびる流通空間を有し、上下方向に離間して配列された複数の枝管から複数の前記伝熱管に前記冷媒を流入させるヘッダー集合管と、を有する熱交換器と、
回転するボスの周りに羽根を有し、前記羽根の回転面が複数の前記伝熱管に対して水平方向に対向する軸流ファンと、
前記流通空間に気液二相状態の冷媒が上向きに流れるように前記冷媒を流入させ、前記熱交換器で前記冷媒を蒸発させる冷媒回路と、を備え、
前記ヘッダー集合管に流れる前記冷媒の流動様式は、前記ヘッダー集合管の中央にガス相冷媒が集まり、壁面に液相冷媒が集まる環状流またはチャーン流であり、
前記流通空間の水平面における中心を0%、前記ヘッダー集合管の壁面の位置を100%として、前記水平面における前記中心からの距離を0~100%であらわす場合に、高さが前記羽根の回転する高さの範囲内にある複数の前記枝管のうち、前記ボスの高さ以下に位置する前記枝管の大半は、先端が前記中心からの距離において0~50%にあるように前記ヘッダー集合管に挿入され、前記ボスの高さよりも上に位置する前記枝管の大半は、先端が前記中心からの距離において50%より大となるように前記ヘッダー集合管に接続されている
空気調和装置。 - 前記ボスの高さ以下に位置する前記枝管のうち、先端が前記中心からの距離において0~50%にあり、かつ、最も上流側に位置する前記枝管の先端は、前記壁面に前記液相冷媒が集まってできた厚さδ[m]の液層を貫いて前記ガス相冷媒に至り、
前記ボスの高さよりも上に位置する枝管のうち、先端が前記中心からの距離において50%より大となり、かつ、最も上流側に位置する枝管の先端は、前記液層内にある
請求項1記載の空気調和装置。
ここで、液層の厚さδ[m]は、冷媒流速G[kg/(m2s)]、冷媒の乾き度x、前記ヘッダー集合管の内径D[m]、冷媒液密度ρL[kg/m3]、前記ヘッダー集合管の流通空間に流入する冷媒のガス見かけ速度の変動範囲の最大値である基準液見かけ速度ULS[m/s]としたとき、δ=G×(1-x)×D/(4ρL×ULS)で定義される。また、基準液見かけ速度ULS[m/s]は、G(1-x)/ρLで定義される。 - 前記ヘッダー集合管に流入する冷媒の乾き度が0.05≦x≦0.30の範囲にある
請求項1又は2記載の空気調和装置。 - 前記ヘッダー集合管は、前記羽根の回転する高さの範囲内にある複数の前記枝管と接続される前記流通空間が、上下方向に複数に分割されている
請求項1~3のいずれか一項記載の空気調和装置。 - 前記ヘッダー集合管は、上下方向に異なる高さに配置された複数のヘッダー集合管で構成され、前記羽根の回転する高さの範囲内にある複数の前記枝管のうち、前記ボスの高さより下に位置する前記枝管が接続される下部のヘッダー集合管と、前記ボスの高さよりも上に位置する前記枝管が接続される上部のヘッダー集合管とでは、下部の前記ヘッダー集合管の前記流通空間の内径が上部の前記ヘッダー集合管の前記流通空間の内径よりも大きい
請求項4記載の空気調和装置。 - 前記軸流ファンは、上下方向に異なる高さに配置された複数の軸流ファンで構成され、各軸流ファンの前記羽根の回転する高さの範囲内にある複数の前記枝管のうち、各軸流ファンの前記ボスの高さ以下に位置する前記枝管の大半は、先端が前記中心からの距離において0~50%にあるように前記ヘッダー集合管に挿入され、各軸流ファンの前記ボスの高さよりも上に位置する前記枝管の大半は、先端が前記中心からの距離において50%より大となるように接続されている
請求項1~3のいずれか一項記載の空気調和装置。 - 上下方向に離間して配列され、冷媒が流れる複数の伝熱管と、内部に上下方向にのびる流通空間を有し、上下方向に離間して配列された複数の枝管から複数の前記伝熱管に前記冷媒を流入させるヘッダー集合管と、を有する熱交換器と、
複数の前記伝熱管よりも上方に位置するファンと、
前記流通空間に気液二相状態の冷媒が上向きに流れるように前記冷媒を流入させ、前記熱交換器で前記冷媒を蒸発させる冷媒回路と、を備え、
前記ヘッダー集合管に流れる前記冷媒の流動様式は、前記ヘッダー集合管の中央にガス相冷媒が集まり、壁面に液相冷媒が集まる環状流またはチャーン流であり、
前記ヘッダー集合管は、上下方向に異なる高さに配置された複数のヘッダー集合管で構成されたものであり、
前記流通空間の水平面における中心を0%、前記ヘッダー集合管の壁面の位置を100%として、前記水平面における前記中心からの距離を0~100%であらわす場合に、前記ファンに最も近い位置にあるヘッダー集合管では、接続される前記枝管の大半は、先端が前記中心からの距離において0~50%にあるように挿入され、前記ファンに最も近い位置にあるヘッダー集合管よりも低い位置にあるヘッダー集合管では、接続される前記枝管の大半は、先端が前記中心からの距離において50%より大となるように接続されている
空気調和装置。 - 前記ファンに最も近い位置にあるヘッダー集合管の前記流通空間の内径は、前記ファンに最も近い位置にあるヘッダー集合管よりも低い位置にあるヘッダー集合管の前記流通空間の内径よりも大きい
請求項7記載の空気調和装置。 - 上下方向に離間して配列され、冷媒が流れる複数の伝熱管と、内部に上下方向にのびる流通空間を有し、上下方向に離間して配列された複数の枝管から複数の前記伝熱管に前記冷媒を流入させるヘッダー集合管と、を有する熱交換器と、
複数の前記伝熱管よりも上方に位置するファンと、
前記流通空間に気液二相状態の冷媒が上向きに流れるように前記冷媒を流入させ、前記熱交換器で前記冷媒を蒸発させる冷媒回路と、を備え、
前記ヘッダー集合管に流れる前記冷媒の流動様式は、前記ヘッダー集合管の中央にガス相冷媒が集まり、壁面に液相冷媒が集まる環状流またはチャーン流であり、
前記流通空間の水平面における中心を0%、前記ヘッダー集合管の壁面の位置を100%として、前記水平面における前記中心からの距離を0~100%であらわす場合に、前記ヘッダー集合管に接続される前記枝管の大半は、先端が前記中心からの距離において0~50%にあるように前記ヘッダー集合管に挿入され、前記ヘッダー集合管に接続される前記枝管の少なくとも最上部に位置する前記枝管は、先端が前記中心からの距離において50%より大となるように前記ヘッダー集合管に接続されている
空気調和装置。 - 複数の前記枝管は、複数の前記伝熱管の端部、または複数の前記伝熱管の端部に取り付けられたジョイント管である
請求項1~9のいずれか一項記載の空気調和装置。 - 運転条件に応じて前記ヘッダー集合管に流入する前記冷媒の乾き度を調整する制御装置と、を備え
前記冷媒回路は、暖房運転時の冷媒流れにおける前記ヘッダー集合管の上流に第1の絞り装置が設けられ、
前記制御装置は、前記第1の絞り装置を制御する
請求項1~10のいずれか一項記載の空気調和装置。 - 前記冷媒回路は、
前記第1の絞り装置と前記ヘッダー集合管との間に設けられた気液分離容器と、
前記気液分離容器と、暖房運転時の冷媒流れにおける前記熱交換器の下流とを接続するバイパス配管と、
前記バイパス配管上に設けられ、前記冷媒の流量を調整するバイパス流量調整機構と、を有する
請求項11記載の空気調和装置。 - 前記冷媒回路はさらに、
前記冷媒の流れを切り替える流路切替装置と、
前記熱交換器と前記第1の絞り装置との間に設けられた第2の絞り装置と、を有し、
前記制御装置は、前記流路切替装置と前記第1の絞り装置と前記第2の絞り装置とを制御する
請求項12記載の空気調和装置。 - 前記制御装置は、暖房運転時に、前記液ヘッダー集合管に流入する前記冷媒の乾き度xが0.05≦x≦0.30の範囲に収まるように調整する
請求項11~13のいずれか一項記載の空気調和装置。
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Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2020162096A1 (ja) * | 2019-02-06 | 2020-08-13 | 株式会社デンソー | 熱交換器 |
CN113544454A (zh) * | 2019-03-06 | 2021-10-22 | 三星电子株式会社 | 分配器、热交换器单元和空调 |
US20210356144A1 (en) * | 2020-05-14 | 2021-11-18 | Samsung Electronics Co., Ltd. | Distributor and air conditioner including the same |
JPWO2022079763A1 (ja) * | 2020-10-12 | 2022-04-21 | ||
US11698234B2 (en) * | 2019-03-06 | 2023-07-11 | Samsung Electronics Co.. Ltd. | Distributor, heat exchanger unit and air conditioner |
WO2024166276A1 (ja) * | 2023-02-09 | 2024-08-15 | 三菱電機株式会社 | 空気調和装置 |
JP7562284B2 (ja) | 2020-05-14 | 2024-10-07 | 三星電子株式会社 | 分配器及び熱交換器ユニット |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3176532B1 (en) * | 2014-07-29 | 2022-07-20 | Kyocera Corporation | Heat exchanger |
WO2018047332A1 (ja) * | 2016-09-12 | 2018-03-15 | 三菱電機株式会社 | ヘッダー、熱交換器および空気調和装置 |
WO2018047330A1 (ja) * | 2016-09-12 | 2018-03-15 | 三菱電機株式会社 | 空気調和装置 |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5626254B2 (ja) | 1976-12-20 | 1981-06-17 | ||
JPH03177761A (ja) * | 1989-12-06 | 1991-08-01 | Matsushita Electric Ind Co Ltd | 熱交換器 |
JPH05223490A (ja) * | 1992-02-13 | 1993-08-31 | Matsushita Electric Ind Co Ltd | 熱交換器 |
JPH05264126A (ja) * | 1992-03-23 | 1993-10-12 | Matsushita Refrig Co Ltd | 冷媒分流器 |
JP2012021682A (ja) * | 2010-07-13 | 2012-02-02 | Mitsubishi Electric Corp | 熱交換器及びこの熱交換器を搭載したヒートポンプシステム |
WO2015178097A1 (ja) * | 2014-05-19 | 2015-11-26 | 三菱電機株式会社 | 空気調和装置 |
WO2016017430A1 (ja) * | 2014-07-30 | 2016-02-04 | 三菱電機株式会社 | 室外機および冷凍サイクル装置 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001304775A (ja) * | 2000-04-26 | 2001-10-31 | Mitsubishi Heavy Ind Ltd | 車両用空気調和装置 |
US20060101849A1 (en) * | 2004-11-12 | 2006-05-18 | Carrier Corporation | Parallel flow evaporator with variable channel insertion depth |
CN2775569Y (zh) * | 2005-02-04 | 2006-04-26 | 法雷奥汽车空调湖北有限公司 | 一种优化制冷剂流向的平行流冷凝器 |
JP2007003080A (ja) * | 2005-06-23 | 2007-01-11 | Calsonic Kansei Corp | 蒸発器 |
JP5626254B2 (ja) * | 2012-04-05 | 2014-11-19 | ダイキン工業株式会社 | 熱交換器 |
JP5901748B2 (ja) * | 2012-04-26 | 2016-04-13 | 三菱電機株式会社 | 冷媒分配器、この冷媒分配器を備えた熱交換器、冷凍サイクル装置及び空気調和機 |
KR101615445B1 (ko) * | 2014-08-14 | 2016-04-25 | 엘지전자 주식회사 | 공기 조화기 |
-
2017
- 2017-03-24 JP JP2019506889A patent/JP6704507B2/ja active Active
- 2017-03-24 WO PCT/JP2017/012014 patent/WO2018173256A1/ja active Application Filing
- 2017-03-24 US US16/484,732 patent/US11543185B2/en active Active
- 2017-03-24 EP EP17901970.8A patent/EP3605000B1/en active Active
- 2017-03-24 CN CN201780086542.7A patent/CN110418935B/zh active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5626254B2 (ja) | 1976-12-20 | 1981-06-17 | ||
JPH03177761A (ja) * | 1989-12-06 | 1991-08-01 | Matsushita Electric Ind Co Ltd | 熱交換器 |
JPH05223490A (ja) * | 1992-02-13 | 1993-08-31 | Matsushita Electric Ind Co Ltd | 熱交換器 |
JPH05264126A (ja) * | 1992-03-23 | 1993-10-12 | Matsushita Refrig Co Ltd | 冷媒分流器 |
JP2012021682A (ja) * | 2010-07-13 | 2012-02-02 | Mitsubishi Electric Corp | 熱交換器及びこの熱交換器を搭載したヒートポンプシステム |
WO2015178097A1 (ja) * | 2014-05-19 | 2015-11-26 | 三菱電機株式会社 | 空気調和装置 |
WO2016017430A1 (ja) * | 2014-07-30 | 2016-02-04 | 三菱電機株式会社 | 室外機および冷凍サイクル装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3605000A4 |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2020162096A1 (ja) * | 2019-02-06 | 2020-08-13 | 株式会社デンソー | 熱交換器 |
JP2020125896A (ja) * | 2019-02-06 | 2020-08-20 | 株式会社デンソー | 熱交換器 |
JP7255215B2 (ja) | 2019-02-06 | 2023-04-11 | 株式会社デンソー | 熱交換器 |
CN113544454A (zh) * | 2019-03-06 | 2021-10-22 | 三星电子株式会社 | 分配器、热交换器单元和空调 |
CN113544454B (zh) * | 2019-03-06 | 2023-06-13 | 三星电子株式会社 | 分配器、热交换器单元和空调 |
US11698234B2 (en) * | 2019-03-06 | 2023-07-11 | Samsung Electronics Co.. Ltd. | Distributor, heat exchanger unit and air conditioner |
US20210356144A1 (en) * | 2020-05-14 | 2021-11-18 | Samsung Electronics Co., Ltd. | Distributor and air conditioner including the same |
JP7562284B2 (ja) | 2020-05-14 | 2024-10-07 | 三星電子株式会社 | 分配器及び熱交換器ユニット |
JPWO2022079763A1 (ja) * | 2020-10-12 | 2022-04-21 | ||
WO2022079763A1 (ja) * | 2020-10-12 | 2022-04-21 | 三菱電機株式会社 | 冷凍サイクル装置、空気調和機、及び熱交換器 |
WO2024166276A1 (ja) * | 2023-02-09 | 2024-08-15 | 三菱電機株式会社 | 空気調和装置 |
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