WO2017037772A1 - Heat exchanger and method for manufacturing same - Google Patents

Heat exchanger and method for manufacturing same Download PDF

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Publication number
WO2017037772A1
WO2017037772A1 PCT/JP2015/074366 JP2015074366W WO2017037772A1 WO 2017037772 A1 WO2017037772 A1 WO 2017037772A1 JP 2015074366 W JP2015074366 W JP 2015074366W WO 2017037772 A1 WO2017037772 A1 WO 2017037772A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
header
refrigerant
heat exchanger
transfer tube
Prior art date
Application number
PCT/JP2015/074366
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French (fr)
Japanese (ja)
Inventor
良太 赤岩
寿守務 吉村
松本　崇
山田　彰二
皓亮 宮脇
石橋　晃
智嗣 上山
綾 河島
Original Assignee
三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2017537042A priority Critical patent/JP6537615B2/en
Priority to PCT/JP2015/074366 priority patent/WO2017037772A1/en
Publication of WO2017037772A1 publication Critical patent/WO2017037772A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates

Definitions

  • the present invention relates to a heat exchanger, a refrigeration cycle apparatus, and a heat exchanger manufacturing method, for example, a heat exchanger used in an air conditioner capable of defrosting operation and heating operation, and a heat exchanger manufacturing method.
  • a heat exchanger for a car air conditioner a pair of headers that are horizontally opposed to each other, a plurality of flat heat transfer tubes that are connected in parallel to the pair of headers at a constant interval, and between flat heat transfer tubes
  • a corrugated fin that intervenes closely in a gap and supplies a refrigerant as a heat exchange medium to a plurality of flat heat transfer tubes.
  • the above-described heat exchanger functions as an evaporator.
  • the surface temperature of the fins and heat transfer tubes in the evaporator decreases to below the freezing point, and moisture in the air may form frost on the fins and heat transfer tube surfaces.
  • JP 2012-72955 A Japanese Patent No. 3738404
  • Patent Document 2 since the refrigerant does not flow in the refrigerant flow path in the heat transfer tube located on the windward side of the heat transfer tube, when performing the defrosting operation, Patent Document 1 As in the heat exchanger described in 1., the fin surface temperature on the windward side of the heat transfer tube is unlikely to rise, and the defrosting time becomes long.
  • Patent Documents 1 and 2 have a problem that the defrosting efficiency is poor and as a result, the heating efficiency is lowered. Moreover, when performing cooling operation, there also existed a subject that the effective windward side temperature difference area
  • the present invention has been made against the background of the problems described above, and provides a heat exchanger and a heat exchanger manufacturing method that can improve the defrosting efficiency than before and suppress frosting than before. It is intended to provide.
  • the heat exchanger according to the present invention is a heat exchanger for exchanging heat between the refrigerant flowing inside and the air flowing around, and each of the plurality of heat transfer tubes extending linearly and each of both ends of the plurality of heat transfer tubes
  • Each of the plurality of heat transfer tubes has openings at both ends and has a plurality of refrigerant flow paths through which the refrigerant flows,
  • the opening provided in a part of the part including the part located on the most upstream side of the air flow is at the one end.
  • the opening of the remaining part to be provided and the inside of the header have different orientations.
  • the manufacturing method of the heat exchanger includes a first step of inserting the plurality of heat transfer tubes into one arcuate member of two arcuate members having an arcuate cross section constituting the hollow tubular header, After the first step, a part of the plurality of heat transfer tubes including the heat transfer tube located on the most upstream side of the air flow is left with an opening provided at one end located on the one header side.
  • the second step of bending so as to be located on the other end side of the opening provided on the one header side of the portion of the portion, and the bent portion of the plurality of heat transfer tubes after the second step
  • a third step of producing the header by combining the one arcuate member and the other arcuate member so as to be located inside the header.
  • the gas refrigerant flowing into the heat exchanger functioning as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared to the conventional heat transfer tube.
  • the gas refrigerant that has flowed into the heat exchanger that functions as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared with the conventional heat transfer tube.
  • the heat exchange in can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. It is a perspective view which shows the outline
  • FIG. 7 It is a figure which shows the 2nd example of the shape of the heat exchanger tube 12 and the header 10 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 6 of this invention. It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. It is a figure which shows the header 110 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus.
  • FIG. 1 It is a figure which shows the header 111 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the mode of the frost on the fin 113 of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. It is a figure which shows the relationship between the refrigerant
  • FIG. It is a figure which shows the relationship between the refrigerant
  • FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus 100 includes a compressor 1, a four-way valve 2, an indoor heat exchanger 3, an expansion valve 4, and an outdoor heat exchanger 5.
  • the compressor 1 is a variable capacity compressor that compresses sucked refrigerant and discharges it as a high-temperature and high-pressure refrigerant.
  • the four-way valve 2 is for switching the refrigerant flow path provided on the discharge side of the compressor 1.
  • the refrigerant flow in a state where the four-way valve 2 is switched so as to perform the heating operation is indicated by a solid line.
  • coolant flow in the state in which the four-way valve 2 was switched so that a defrost operation may be performed is shown with the dotted line.
  • the indoor heat exchanger 3 is a heat exchanger that functions as an evaporator during cooling operation and functions as a condenser during heating operation.
  • the expansion valve 4 is for decompressing and expanding the refrigerant flowing out of the outdoor heat exchanger 5 during the cooling operation and decompressing and expanding the refrigerant flowing out of the indoor heat exchanger 3 during the heating operation.
  • the outdoor heat exchanger 5 is a heat exchanger that functions as a condenser during cooling operation and functions as an evaporator during heating operation.
  • the refrigerant flow when the heating operation is performed in the refrigeration cycle apparatus 100 will be described.
  • the four-way valve 2 is switched to the heating side, the indoor heat exchanger 3 functions as a condenser, and the outdoor heat exchanger 5 functions as an evaporator.
  • the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the indoor heat exchanger 3.
  • the refrigerant that has flowed into the indoor heat exchanger 3 is cooled and liquefied by heat exchange with the indoor air introduced into the indoor heat exchanger 3.
  • the liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the outdoor heat exchanger 5.
  • the refrigerant flowing into the outdoor heat exchanger 5 returns to the compressor 1 in a state where it is heated and gasified by exchanging heat with outdoor air introduced into the outdoor heat exchanger 5.
  • the heating operation is executed and the cumulative amount of frost in the outdoor heat exchanger 5 increases, the defrosting operation is started.
  • the refrigerant flow when the defrosting operation is performed in the refrigeration cycle apparatus 100 will be described.
  • the four-way valve 2 is switched to the cooling side, the indoor heat exchanger 3 functions as an evaporator, and the outdoor heat exchanger 5 functions as a condenser.
  • the refrigerant flow during the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.
  • the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the outdoor heat exchanger 5.
  • the refrigerant that has flowed into the outdoor heat exchanger 5 is cooled and liquefied by exchanging heat with the indoor air introduced into the outdoor heat exchanger 5.
  • the liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the indoor heat exchanger 3.
  • the refrigerant flowing into the indoor heat exchanger 3 returns to the compressor 1 in a state of being heated and gasified by exchanging heat with outdoor air introduced into the indoor heat exchanger 3.
  • FIG. 2 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 3 is a perspective view showing an outline of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • the arrows in FIGS. 2 and 3 indicate the flow of air. The air passes through the gaps between the fins by driving the blowing means (not shown).
  • the outdoor heat exchanger 5 includes headers 10 and 11, heat transfer tubes 12, and fins 13.
  • the header 10 is provided below the outdoor heat exchanger 5, and the header 11 is provided below the outdoor heat exchanger 5.
  • the headers 10 and 11 are configured in, for example, a hollow cylindrical shape.
  • the heat transfer tube 12 has a plurality of flow paths through which the refrigerant flows and has a flat shape extending linearly and is inserted into the headers 10 and 11.
  • the fin 13 is a corrugated fin, for example, and is closely intervened in the gap between the adjacent heat transfer tubes 12.
  • the header 10 is connected to the refrigerant pipe 101.
  • the refrigerant pipe 101 is connected to the expansion valve 4.
  • the header 11 is connected to the refrigerant pipe 102.
  • the refrigerant pipe 102 is connected to the four-way valve 2.
  • the heat transfer tube 12 is not limited to the example configured to have a plurality of refrigerant flow paths, and each of the plurality of heat transfer tubes may be configured to have a single refrigerant flow path.
  • the fin 13 is not limited to the above-mentioned example, A plate type fin may be used and the finless type which does not use a fin may be employ
  • the gas-liquid two-phase refrigerant flows into the header 10 through the refrigerant pipe 101, and the refrigerant that has flowed into the header 10 is distributed to the heat transfer pipe 12.
  • the gas-liquid two-phase refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes a gas refrigerant and flows out to the header 11.
  • the gas refrigerant that has flowed out to the header 11 is guided to the refrigerant pipe 102.
  • the gas refrigerant flows into the header 11 through the refrigerant pipe 102, and the refrigerant that has flowed into the header 11 is distributed to the plurality of heat transfer tubes 12. Then, the gas refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes liquid refrigerant and flows out to the header 10. The liquid refrigerant that has flowed out to the header 10 is guided to the refrigerant pipe 101.
  • the refrigerant flow during the cooling operation or the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.
  • openings 15A to 15F are provided at the end of the heat transfer tube 12 in order from the windward side.
  • FIG. 3 illustrates an example in which an opening is provided on one end side of the heat transfer tube 12, the opening is similarly provided on the other end side of the heat transfer tube 12.
  • a plurality of refrigerant flow paths 15 are provided inside the heat transfer tube 12.
  • the refrigerant channels 15a, 15b, 15c, 15d, 15e, and 15f are sequentially called from the windward side.
  • the refrigerant channels 15a, 15b, and 15c may be referred to as refrigerant channels 15a to 15c.
  • the refrigerant channels 15d, 15e, and 15f may be referred to as refrigerant channels 15d to 15f.
  • the portion on the windward side of the heat transfer tube 12 is referred to as the windward heat transfer tube 12a.
  • a portion on the windward side of the fin 13 is referred to as a windward fin 13a.
  • a louver 14 is provided on the surface of the fin 13. The louver 14 has a shape cut and raised so as to promote heat transfer.
  • the refrigerant is distributed from the header 10 to the plurality of refrigerant flow paths 15 of the heat transfer pipe 12.
  • the header 10 and the refrigerant flow path 15 there are flows in which the flow rate ratio of the refrigerant flowing in each refrigerant flow path 15 and the ratio of the gas refrigerant and the liquid refrigerant are different.
  • FIG. 4 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 5 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 6 is a diagram showing a state of frost on the fins 13 of the heat transfer tubes 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • a flow such as a laminar flow, a wavy flow, a bubble flow, and a plug flow in which the gas refrigerant is likely to collect on the upper portion of the header 10. It is assumed that it will occur.
  • liquid refrigerant is accumulated in the lower part of the header 10
  • gas refrigerant is accumulated in the upper part of the header 10.
  • the opening provided at the lower end is located above the liquid level of the liquid refrigerant and is opposite to the traveling direction of the gas refrigerant inside the header 10. It is bent to face the direction.
  • the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is configured such that the opening provided at the lower end is positioned below the liquid level of the liquid refrigerant.
  • the gas refrigerant flowing inside the header 10 is likely to flow into the refrigerant flow paths 15a to 15c due to inertial force.
  • the liquid refrigerant flowing under the header 10 is sucked into the refrigerant flow paths 15d to 15f. That is, the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller gas refrigerant ratio than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c.
  • the two-phase refrigerant that has passed through the refrigerant flow paths 15a to 15f exchanges heat with air, changes to a gas single-phase refrigerant, and is supplied to the header 11.
  • a gas refrigerant is stored inside the header 11.
  • portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are configured to extend linearly.
  • a portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so as to face the direction opposite to the traveling direction of the gas refrigerant inside the header 11.
  • the in-tube pressure loss of the refrigerant channels 15a to 15c and the refrigerant channels 15d to 15f are equal, or the in-tube pressure loss of the refrigerant channels 15d to 15f is made larger than that of the refrigerant channels 15a to 15c.
  • the flow rate of the gas refrigerant flowing to ⁇ 15c can be increased. This is because, when comparing two-phase refrigerants of the same flow rate, the pressure loss in the pipe increases as the proportion of the gas refrigerant increases, and the part of the heat transfer pipe 12 having the refrigerant flow paths 15a to 15c is bent. This is to prevent the flow rate of the refrigerant flow paths 15a to 15c in the heat transfer tube 12 from being reduced due to an increase in pressure loss.
  • the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c is more gas than the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f.
  • the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller ratio of the gas refrigerant than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c. For this reason, the heat exchange amount in which the refrigerant flowing through the refrigerant flow path provided on the windward side of the heat transfer tube 12 exchanges heat with air can be suppressed, and as shown in FIG. It becomes uniform from the upper side toward the leeward side.
  • the heat transfer tube 12 By configuring the heat transfer tube 12 as shown in FIG. 5, when the gas single-phase refrigerant inside the header 11 is supplied to the refrigerant channel 15 during the cooling operation or the defrosting operation, the refrigerant channel 15 a Since the refrigerant flowing through the refrigerant channels 15-15c is larger than the refrigerant flowing through the refrigerant channels 15d-15f, the amount of heat exchange in the refrigerant channels 15a-15c can be increased.
  • FIG. 7 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the temperature of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 8 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the heat exchange amount of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 9 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the refrigerant flow rate of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 7.
  • the horizontal axis in FIG. 8 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis in FIG. 8 defines the heat exchange amount of the heat transfer tube 12.
  • the horizontal axis of FIG. 9 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 9 defines the refrigerant flow rate of the heat transfer tube 12.
  • the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 7, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 8, the heat exchange amount of the outdoor heat exchanger 5 is increased from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
  • the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
  • the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 increases from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path.
  • the two-phase refrigerant having a high ratio of gas refrigerant flows through the refrigerant channel on the leeward side, and the two-phase refrigerant having a high ratio of liquid refrigerant is the refrigerant on the leeward side.
  • the flow path heat exchange on the leeward side that can obtain more latent heat of the refrigerant is promoted.
  • the air flowing on the fins 13 flows from the upstream side to the downstream side, the amount of water vapor that the air has decreases.
  • FIG. 10 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 11 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • FIG. 12 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
  • the header 10 includes, for example, an arc member 10a and an arc member 10b.
  • the arc-shaped member 10a and the arc-shaped member 10b are configured by, for example, members having a cross-sectional arc shape.
  • the heat transfer tube 12 is inserted into the arc-shaped member 10a as shown in FIG. 10, for example, in a state where there is a cut in the longitudinal direction of the heat transfer tube 12 between the refrigerant flow channel 15c and the refrigerant flow channel 15d. Is done.
  • one of the end portions of the heat transfer tubes 12 corresponding to the refrigerant flow paths 15a to 15c is bent in the longitudinal direction of the header by a bending machine, for example, as shown in FIG. It becomes a state.
  • the arcuate member 10a and the arcuate member 10b are fitted to each other to fit the header 10. Is formed. Specifically, for example, the fitting of the arc-shaped member 10a and the arc-shaped member 10b is performed by, for example, a belt conveyor type integrated brazing process or the like. As a result, the state shown in FIG. 12 is obtained.
  • the above-described assembly process is not limited to the case of the circular pipe header as shown in FIG. 12, but also in the case of a header constituted by a plurality of members, the obstacle in the process of bending the heat transfer tube 12 by the bending machine. As long as it is not, it can be applied.
  • the heat transfer tube 12 inserted into the header 10 is thermally expanded in the course of the belt conveyor type integrated brazing process so that the heat transfer tube 12 is thermally expanded. Has the effect of solving the problem of missing from the header 10.
  • FIG. 13 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 13, portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are bent, and portions of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are not bent and extend in a straight line. Yes. As described above, the direction of the opening provided in the end portion on the header 10 side of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the same as that of the heat transfer tube having the refrigerant flow paths 15d to 15f in the heat transfer tube 12. This is different from the direction of the opening provided at the end on the header 10 side.
  • FIG. 29 is a diagram showing a header 110 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus.
  • FIG. 30 is a diagram showing a header 111 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus.
  • FIG. 31 is a diagram showing a state of frost on the fin 113 of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
  • the conventional heat transfer tube 112 corresponds to all the refrigerant flow paths 115, and the lower end portion located inside the header 110 extends in a straight line without being bent. In addition, as shown in FIG. 30, the conventional heat transfer tube 112 extends in a straight line without being bent at the upper end portion located inside the header 111.
  • FIG. 32 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the temperature of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
  • FIG. 33 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the heat exchange amount of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
  • FIG. 34 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the refrigerant flow rate of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
  • the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 32.
  • the horizontal axis of FIG. 33 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 33 defines the heat exchange amount of the heat transfer tube 12.
  • the horizontal axis of FIG. 34 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 34 defines the refrigerant flow rate of the heat transfer tube 12.
  • the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 32, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 33, the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
  • the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path.
  • the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel.
  • the heat transfer tube 112 When the heat transfer tube 112 is configured as shown in FIGS. 29 and 30, two-phase refrigerants having the same ratio of gas refrigerant to liquid refrigerant and the same amount are distributed from the header 110 as shown in FIG. Will be.
  • the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
  • the temperature difference between the air and the refrigerant is the largest in the portion located on the windward side of the heat transfer tube 112, and the windward side to the leeward side. The temperature difference between the air and the refrigerant becomes lower.
  • the frost accumulated on the windward side of the conventional heat transfer tube 112 eventually leads to a decrease in the air volume passing through the heat exchanger because it obstructs the air path, and the frost on the fin surface becomes a thermal resistance and the heat exchange efficiency with the air is increased. The problem of deteriorating occurs.
  • the outdoor heat exchanger 5 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air flowing around, and includes a plurality of heat transfer tubes 12 extending linearly.
  • Each end of each of the plurality of heat transfer tubes 12 is inserted, and each of the plurality of heat transfer tubes 12 has an opening at each end so that the refrigerant flows.
  • the opening to be formed has a different orientation in the inside of the header 10 and the opening of the remaining part located on the header 10 side.
  • the openings of some of the flow paths are the openings of other flow paths and the refrigerant flow in the header 10. Try to have a different orientation to the direction. For this reason, a difference arises in the ease of a refrigerant
  • the difference in the height position in the header 10 is also used between the openings of some of the flow paths and the openings of the other flow paths.
  • the distribution of the refrigerant gas and liquid inside the header may be various.
  • the difference in the direction of the opening may be used to generate gas, liquid, and inflow distribution between the flow paths.
  • a bent portion is formed so that the openings of some of the flow paths are different from the openings of the other flow paths, and the flow of the refrigerant is made different by making the resistance of the flow paths different. It may be. Such a difference in bending may be used for a difference in refrigerant inflow.
  • FIG. 1 By using such a structure, during the defrosting operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows inside the heat transfer tube 12 located on the windward side of the heat transfer tube 12 as compared with the conventional case. Heat exchange in the heat transfer tube 12 is promoted, and during the heating operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows through the heat transfer tube 12 located on the windward side of the heat transfer tube 12 than before. Heat exchange in the heat transfer tube 12 can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.
  • FIG. in the second embodiment the heat transfer tube 12 is configured differently from the first embodiment.
  • items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 14 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.
  • FIG. 15 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.
  • FIG. 16 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.
  • the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so that the lower end thereof faces in the direction opposite to the refrigerant flow direction in the header 10. Further, as shown in FIG. 14, the portion having the refrigerant flow paths 15 d to 15 f in the heat transfer tube 12 is bent so that the lower end thereof faces the same direction as the refrigerant flow direction in the header 10. As shown in FIG. 15, the upper end of the heat transfer tube 12 extends straight without being bent.
  • the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12.
  • the direction is opposite to the direction of the opening provided.
  • the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
  • the outdoor heat exchanger 5 has a part of the heat transfer tube 12 including a part located at the most upstream side of the air flow at least at one end in the longitudinal direction.
  • the opening provided is configured to be in the direction opposite to the refrigerant flow direction inside the header 10, and the opening of the remaining portion located on the header 10 side is the same as the refrigerant flow direction inside the header 10. It is comprised so that it may become a direction. For this reason, it is only necessary to bend the lower end of the heat transfer tube 12, it is not necessary to bend the upper end of the heat transfer tube 12, and for example, a circular tube having an insertion port for the heat transfer tube 12 is used.
  • the processing can be simplified as compared with the first one.
  • the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so that the lower end thereof is oriented in the same direction as the refrigerant flow direction in the header 10. Pressure loss on the flow paths 15d to 15f side increases. Therefore, in the second embodiment, the gas refrigerant is less likely to enter the refrigerant flow paths 15d to 15f than in the first embodiment, and a larger amount of gas refrigerant can be supplied to the refrigerant flow paths 15a to 15c.
  • Embodiment 3 FIG.
  • the portion having the refrigerant flow paths 15a to 15c of the heat transfer tube 12 is inserted and bent to the center height of the header 10.
  • items that are not particularly described are the same as those in Embodiment 1, and the same functions and configurations are described using the same reference numerals.
  • FIG. 17 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention.
  • FIG. 18 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention.
  • the gas refrigerant out of the gas-liquid two-phase refrigerant flowing inside the header 10 flows like an annular flow that tends to gather at a position corresponding to the center height of the header 10. It is assumed that this occurs.
  • the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is the center of the header 10 in the radial direction than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. It is bent so that it is located on the side. Also, as shown in FIG. 17, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is such that the position of the opening provided at the lower end thereof is shortened to the height near the side wall of the header 10. It is configured by cutting.
  • the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the opening provided at the lower end of the portion of the heat transfer pipe 12 having the refrigerant flow paths 15d to 15f.
  • the gas refrigerant inside the header 10 is supplied to the refrigerant flow paths 15a to 15c more than the refrigerant flow paths 15d to 15f.
  • the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is smaller in diameter of the header 10 than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. You may comprise so that it may extend linearly so that it may be located in the direction center side.
  • the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is arranged such that the position of the opening provided at the lower end thereof is located at a height near the side wall of the header 10. It is bent.
  • the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the opening provided at the lower end of the portion of the heat transfer pipe 12 having the refrigerant flow paths 15d to 15f.
  • the gas refrigerant inside the header 10 is supplied to the refrigerant flow paths 15a to 15c more than the refrigerant flow paths 15d to 15f.
  • the header 10 has a hollow cylindrical shape, and is connected to the header 10 in the longitudinal direction of the plurality of heat transfer tubes 12.
  • the openings provided in some parts including the part located on the most upstream side of the air flow are located closer to the center side in the radial direction of the header 10 than the openings of the remaining parts located on the header 10 side. Yes.
  • it can be set as the header 10 with a small cross-sectional area where an annular flow tends to occur, and the cost of the header 10 can be reduced.
  • more gas refrigerant in the header 10 is supplied to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
  • Embodiment 4 FIG.
  • the flat surface of the heat transfer tube 12 is cut open, for example, to the half surface in the minor axis direction.
  • items not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 19 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention.
  • FIG. 20 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention.
  • the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c has a through portion 12A in which a portion located inside the header 10 penetrates from the outer surface to the inner surface. It is configured. With this configuration, the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
  • the portion located on the upper end side by a predetermined distance from the lower end of the header 10 is not provided with the penetration portion 12A, and the location where the penetration portion 12A is provided more than in FIG. Good. Even if it does in this way, there can exist an effect similar to the case where it is set as a structure like FIG.
  • the outdoor heat exchanger 5 has a portion located on the most upstream side of the air flow at one end located on the header 10 side in the longitudinal direction of the plurality of heat transfer tubes 12. Some of the parts including the through-hole 12 ⁇ / b> A have a part located inside the header 10 cut out from the outer surface to the inner surface. For this reason, in the fourth embodiment, unlike the first embodiment, the process of inserting the heat transfer tube 12 into the header 10 and bending the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is performed. Without it, the outdoor heat exchanger 5 can be manufactured. Therefore, this Embodiment 4 can manufacture the outdoor heat exchanger 5 by a simpler process than Embodiment 1. FIG. In the fourth embodiment, the same effect as in the first embodiment can be obtained.
  • Embodiment 5 FIG.
  • the lower end of the heat transfer tube 12 is bent in the same direction as the refrigerant inflow direction in the header 10.
  • items that are not particularly described are the same as those in the fourth embodiment, and the same functions and configurations are described using the same reference numerals.
  • FIG. 21 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention.
  • FIG. 22 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention.
  • FIG. 23 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention.
  • the opening provided at the lower end is positioned above the liquid level of the liquid refrigerant in the header 10, and the traveling direction of the gas refrigerant in the header 10 is as follows. It is bent to face the same direction.
  • the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS. 22 and 23 are the same as the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS.
  • the structure has a through portion 12A.
  • the opening provided at the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is located in the direction opposite to the direction of the refrigerant flowing through the header 10, the refrigerant loses pressure loss. The gas refrigerant becomes difficult to flow.
  • the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is located in the same direction as the direction of refrigerant flowing through the header 10, the structure in which gas refrigerant flows easily It has become.
  • the outdoor heat exchanger 5 according to the fifth embodiment is cut out in the heat transfer tube 12 and bent in the same direction as the refrigerant inflow direction in the header 10 as in the configuration of the fourth embodiment. It is a thing. Therefore, in the fifth embodiment, the height of the refrigerant inserted into the header 10 can be shortened while obtaining the same effect as in the first to third embodiments. Therefore, the total pressure loss of the refrigerant passing through the outdoor heat exchanger 5 can be reduced.
  • Embodiment 6 FIG.
  • the shape of the header 10 into which the heat transfer tube 12 is inserted has a shape that becomes narrower in the insertion direction of the heat transfer tube 12.
  • items not particularly described are the same as those in the first to fifth embodiments, and the same functions and configurations are described using the same reference numerals.
  • FIG. 24 is a diagram showing a first example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention.
  • FIG. 25 is a diagram showing a second example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention.
  • the header 10 is configured to have a triangular cross section. Specifically, the header 10 may be provided such that one of the sides is located at the bottom and the top facing the above-described bottom is located at the top.
  • the header 10 may have a hexagonal cross section. Specifically, the header 10 may be provided such that one of the sides is positioned at the lowest position as the bottom and the top portion facing the above-described bottom is positioned at the highest position.
  • the outdoor heat exchanger 5 configures the header 10 so that the horizontal internal cross-sectional area decreases from the lower end side of the heat transfer tube 12 toward the upper end side of the heat transfer tube 12. is doing. For this reason, it becomes easy to accumulate gas refrigerant above the inside of the header 10, and the effects of the first, second, and fourth embodiments can be further exhibited.
  • the upper end of the heat transfer tube 12 is bent or the flow path length is shortened so as to correspond to a plurality of refrigerant flow paths so that the pressure losses are different. It is good also as a structure cut
  • Embodiment 7 FIG. In the seventh embodiment, unlike the first to sixth embodiments, the shape of the outdoor heat exchanger 5 is changed. In the seventh embodiment, items not particularly described are the same as those in the first to sixth embodiments, and the same functions and configurations are described using the same reference numerals.
  • FIG. 26 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. As shown in FIG. 26, the headers 10 and 11 are provided in the vertical direction, and the heat transfer tubes 12 are provided in the horizontal direction.
  • FIG. 27 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention.
  • FIG. 28 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention.
  • FIG. 27 a case where liquid refrigerant is accumulated on the inner wall side of the header 10 in the header 10 and gas refrigerant is accumulated in the direction away from the inner wall of the header 10 inside the header 10 will be described as an example.
  • the gas-liquid two-phase refrigerant flows in the header 10 from below to above.
  • a portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so as to face the direction opposite to the refrigerant flow direction. Thereby, the gas refrigerant inside the header 10 is easily supplied to the refrigerant flow paths 15a to 15c.
  • the gas refrigerant flows in the header 11 from below to above.
  • Parts of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are bent so as to face the same direction as the refrigerant flow direction.
  • one end located on the header 10 side among the longitudinal ends of the plurality of heat transfer tubes 12 is the interior of the header 10, as in the first embodiment.
  • the openings provided in a part of the plurality of heat transfer tubes 12 including the part located on the most upstream side of the air flow are the openings of the remaining parts located on the header 10 side and the header 10. It has a different orientation inside. For this reason, also in this Embodiment 7, the same effect as Embodiment 1 can be show
  • the heat exchanger is the outdoor heat exchanger 5
  • the present invention is not limited to this.
  • the present invention can be similarly applied to the case where the heat exchanger is an indoor heat exchanger.
  • the refrigeration cycle apparatuses 100 of Embodiments 1 to 7 described above can be applied to, for example, a heat pump apparatus, a hot water supply apparatus, a refrigeration apparatus, and the like.

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  • Physics & Mathematics (AREA)
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Abstract

To provide a heat exchanger and a method for manufacturing a heat exchanger, with which it is possible to improve defrosting efficiency and suppress frost formation to a greater extent than in the prior art. A heat exchanger for exchanging heat between internally flowing coolant and peripherally flowing air, wherein: the heat exchanger is provided with a plurality of heat transfer tubes 12 extending in a straight line, and hollow headers 10, 11 into which both ends of each of the plurality of transfer tubes are inserted to constitute a part of a coolant flow route; each of the plurality of transfer tubes has openings 15A–15F at both ends, and internally has a plurality of coolant flow paths 15a–15f through which the coolant flows; and in at least at one end connected to the header in the long direction of the plurality of the heat transfer tubes, the openings 15A–15C provided at some locations including the location positioned farthest to the upstream side of the flow of air are orientated differently inside the header relative to the openings 15D–15F at the remaining locations provided at the one end.

Description

熱交換器及び熱交換器の製造方法HEAT EXCHANGER AND HEAT EXCHANGER MANUFACTURING METHOD
　本発明は、熱交換器、冷凍サイクル装置、及び熱交換器の製造方法に関し、例えば、除霜運転及び暖房運転可能な空気調和機に用いられる熱交換器及び熱交換器の製造方法に関する。 The present invention relates to a heat exchanger, a refrigeration cycle apparatus, and a heat exchanger manufacturing method, for example, a heat exchanger used in an air conditioner capable of defrosting operation and heating operation, and a heat exchanger manufacturing method.
　従来、例えばカーエアコン用の熱交換器として、上下で水平に対峙する一対のヘッダと、一対のヘッダに一定の間隔を保って平行に接続される複数の扁平伝熱管と、扁平伝熱管同士の隙間に密着介入させるコルゲートフィンと、を備え、熱交換媒体である冷媒を複数の扁平伝熱管に対して供給するものがあった。 Conventionally, for example, as a heat exchanger for a car air conditioner, a pair of headers that are horizontally opposed to each other, a plurality of flat heat transfer tubes that are connected in parallel to the pair of headers at a constant interval, and between flat heat transfer tubes There is a corrugated fin that intervenes closely in a gap and supplies a refrigerant as a heat exchange medium to a plurality of flat heat transfer tubes.
　しかしながら、例えばヒートポンプ型の冷暖兼用の空調用室外機において、上述した熱交換器を用いて暖房運転を行った場合、上述の熱交換器は蒸発器として機能することとなる。このため、寒冷時に暖房運転を行った場合、蒸発器におけるフィンや伝熱管の表面温度は氷点下まで温度が低下し、空気中の水分がフィンや伝熱管表面に着霜する場合がある。 However, when the heating operation is performed using the above-described heat exchanger in, for example, a heat pump type cooling / heating air conditioning outdoor unit, the above-described heat exchanger functions as an evaporator. For this reason, when heating operation is performed during cold weather, the surface temperature of the fins and heat transfer tubes in the evaporator decreases to below the freezing point, and moisture in the air may form frost on the fins and heat transfer tube surfaces.
　このような着霜が生じると、蒸発器のフィン間を通過する空気の通風抵抗が大幅に増大することや、フィンと空気の熱交換における熱抵抗の増大を招き、熱交換効率が低下するため、空調用室外機において上述した熱交換器の実用化はされていないのが実状である。 When such frost formation occurs, the resistance to air passing between the fins of the evaporator is significantly increased, and the heat resistance in the heat exchange between the fins and the air is increased, resulting in a decrease in heat exchange efficiency. In fact, the heat exchanger described above has not been put to practical use in the outdoor unit for air conditioning.
　ここで、上述した着霜が生じないようにするために、伝熱促進のために設けられたコルゲートフィン表面上にあるルーバーの風上側一部が熱伝導抑制部となるように構成した熱交換器が提案されている（例えば、特許文献１参照）。また、上述した着霜が生じないようにするために、扁平伝熱管の風上側における冷媒流路を閉塞した空調用熱交換器が提案されている（例えば、特許文献２参照）。 Here, in order to prevent the above-described frost formation, heat exchange configured such that a part of the windward side of the louver on the surface of the corrugated fin provided for promoting heat transfer becomes a heat conduction suppressing portion. A device has been proposed (see, for example, Patent Document 1). In order to prevent the above-described frost formation, a heat exchanger for air conditioning in which the refrigerant flow path on the windward side of the flat heat transfer tube is closed has been proposed (see, for example, Patent Document 2).
特開２０１２－７２９５５号公報JP 2012-72955 A 特許第３７３８４０４号公報Japanese Patent No. 3738404
　しかしながら、特許文献１に記載された熱交換器は、伝熱管の風上側に位置するフィンに対して熱伝導抑制部が設けられているため、除霜運転を行う場合において、熱が伝わりにくく、フィンの表面温度が上昇しにくい。このため、フィン上の霜が融解されるのに時間がかかり、除霜時間が長くなってしまう。 However, since the heat exchanger described in Patent Document 1 is provided with a heat conduction suppression unit for the fin located on the windward side of the heat transfer tube, when performing a defrosting operation, heat is not easily transmitted, Fin surface temperature is unlikely to rise. For this reason, it takes time for the frost on the fins to melt, and the defrosting time becomes longer.
　また、特許文献２に記載された空調用熱交換器においては、伝熱管の風上側に位置する伝熱管内の冷媒流路に冷媒が流れないため、除霜運転を行う場合において、特許文献１に記載の熱交換器と同様に、伝熱管の風上側のフィン表面温度が上昇しにくく、除霜時間が長くなってしまう。 Further, in the air conditioner heat exchanger described in Patent Document 2, since the refrigerant does not flow in the refrigerant flow path in the heat transfer tube located on the windward side of the heat transfer tube, when performing the defrosting operation, Patent Document 1 As in the heat exchanger described in 1., the fin surface temperature on the windward side of the heat transfer tube is unlikely to rise, and the defrosting time becomes long.
　このように、特許文献１、２に記載された技術においては、除霜効率が悪く、結果として暖房効率が低下するという課題があった。また、冷房運転を行う場合に、室外熱交換器の有効な風上側温度差領域を効率低下させる可能性があるという課題もあった。 As described above, the techniques described in Patent Documents 1 and 2 have a problem that the defrosting efficiency is poor and as a result, the heating efficiency is lowered. Moreover, when performing cooling operation, there also existed a subject that the effective windward side temperature difference area | region of an outdoor heat exchanger may reduce efficiency.
　本発明は、上述のような課題を背景としてなされたものであり、従来よりも除霜効率を向上させ、従来よりも着霜を抑制することができる熱交換器及び熱交換器の製造方法を提供することを目的としている。 The present invention has been made against the background of the problems described above, and provides a heat exchanger and a heat exchanger manufacturing method that can improve the defrosting efficiency than before and suppress frosting than before. It is intended to provide.
　本発明に係る熱交換器は、内部を流れる冷媒と周囲を流れる空気とを熱交換する熱交換器であって、直線状に延びる複数の伝熱管と、前記複数の伝熱管の両端の各々が挿入され、冷媒の流れ道を構成する各々中空のヘッダと、を備え、前記複数の伝熱管の各々は、両端に開口部を有し、冷媒が流れる複数の冷媒流路を内部に有し、前記複数の伝熱管の長手方向のうち前記ヘッダと接続している少なくとも一端において、前記空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる前記開口部は、前記一端に設けられる残りの部位の前記開口部と前記ヘッダの内部で異なる向きとなるものである。 The heat exchanger according to the present invention is a heat exchanger for exchanging heat between the refrigerant flowing inside and the air flowing around, and each of the plurality of heat transfer tubes extending linearly and each of both ends of the plurality of heat transfer tubes Each of the plurality of heat transfer tubes has openings at both ends and has a plurality of refrigerant flow paths through which the refrigerant flows, In at least one end connected to the header in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located on the most upstream side of the air flow is at the one end. The opening of the remaining part to be provided and the inside of the header have different orientations.
　本発明に係る熱交換器の製造方法は、中空筒状の前記ヘッダを構成する２つの断面弧形状の弧状部材のうち一方の弧状部材に前記複数の伝熱管を挿入する第１工程と、前記第１工程の後に、前記複数の伝熱管のうち前記空気の流れの最も上流側に位置する伝熱管を含む一部の部位を、前記一方のヘッダ側に位置する一端に設けられる開口部が残りの部位の前記一方のヘッダ側に設けられる開口部よりも他端側に位置するように曲折する第２工程と、前記第２工程の後に、前記複数の伝熱管のうち曲折された部位が前記ヘッダの内部に位置するように前記一方の弧状部材と他方の弧状部材とを組み合わせて前記ヘッダを作製する第３工程と、を有するものである。 The manufacturing method of the heat exchanger according to the present invention includes a first step of inserting the plurality of heat transfer tubes into one arcuate member of two arcuate members having an arcuate cross section constituting the hollow tubular header, After the first step, a part of the plurality of heat transfer tubes including the heat transfer tube located on the most upstream side of the air flow is left with an opening provided at one end located on the one header side. The second step of bending so as to be located on the other end side of the opening provided on the one header side of the portion of the portion, and the bent portion of the plurality of heat transfer tubes after the second step And a third step of producing the header by combining the one arcuate member and the other arcuate member so as to be located inside the header.
　本発明によれば、除霜運転時において、蒸発器として機能する熱交換器に流入したガス冷媒は、従来よりも、伝熱管のうち風上側に位置する伝熱管の内部を流れて当該伝熱管における熱交換を促進し、暖房運転時において、蒸発器として機能する熱交換器に流入したガス冷媒は、従来よりも、伝熱管のうち風上側に位置する伝熱管の内部を流れて当該伝熱管における熱交換を抑制することができる。したがって、従来よりも除霜効率を向上させることができ、従来よりも着霜を抑制することができる。 According to the present invention, during the defrosting operation, the gas refrigerant flowing into the heat exchanger functioning as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared to the conventional heat transfer tube. In the heating operation, the gas refrigerant that has flowed into the heat exchanger that functions as an evaporator flows through the inside of the heat transfer tube located on the windward side of the heat transfer tube, compared with the conventional heat transfer tube. The heat exchange in can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.
本発明の実施の形態１に係る冷凍サイクル装置１００の構成図である。1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の室外熱交換器５の外観図である。It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の室外熱交換器５の概要を示す斜視図である。It is a perspective view which shows the outline | summary of the outdoor heat exchanger 5 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２のフィン１３上の霜の様子を示す図である。It is a figure which shows the mode of the frost on the fin 13 of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の温度との関係を示す図である。It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 12, and the temperature of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の熱交換量との関係を示す図である。It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 12, and the heat exchange amount of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の冷媒流量との関係を示す図である。It is a figure which shows the relationship between the refrigerant flow path of the heat exchanger tube 12, and the refrigerant | coolant flow rate of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。It is the perspective view and front sectional drawing explaining the assembly process of the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の斜視図である。It is a perspective view of the heat exchanger tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. 本発明の実施の形態２に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態２に係る冷凍サイクル装置１００の伝熱管１２の斜視図である。It is a perspective view of the heat exchanger tube 12 of the refrigeration cycle apparatus 100 which concerns on Embodiment 2 of this invention. 本発明の実施の形態３に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 3 of this invention. 本発明の実施の形態３に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 3 of this invention. 本発明の実施の形態４に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 4 of this invention. 本発明の実施の形態４に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。It is the front view and perspective view which show the shape of the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 4 of this invention. 本発明の実施の形態５に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. 本発明の実施の形態５に係る冷凍サイクル装置１００の伝熱管１２を示す斜視図である。It is a perspective view which shows the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. 本発明の実施の形態５に係る冷凍サイクル装置１００の伝熱管１２を示す斜視図である。It is a perspective view which shows the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 5 of this invention. 本発明の実施の形態６に係る冷凍サイクル装置１００の伝熱管１２及びヘッダ１０の形状の第１の例を示す図である。It is a figure which shows the 1st example of the shape of the heat exchanger tube 12 and the header 10 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 6 of this invention. 本発明の実施の形態６に係る冷凍サイクル装置１００の伝熱管１２及びヘッダ１０の形状の第２の例を示す図である。It is a figure which shows the 2nd example of the shape of the heat exchanger tube 12 and the header 10 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 6 of this invention. 本発明の実施の形態７に係る冷凍サイクル装置１００の室外熱交換器５の外観図である。It is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. 本発明の実施の形態７に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。It is a figure which shows the header 10 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. 本発明の実施の形態７に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。It is a figure which shows the header 11 and the heat exchanger tube 12 of the refrigerating-cycle apparatus 100 which concerns on Embodiment 7 of this invention. 従来の冷凍サイクル装置のヘッダ１１０及び伝熱管１１２を示す図である。It is a figure which shows the header 110 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. 従来の冷凍サイクル装置のヘッダ１１１及び伝熱管１１２を示す図である。It is a figure which shows the header 111 and the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. 従来の冷凍サイクル装置の伝熱管１１２のフィン１１３上の霜の様子を示す図である。It is a figure which shows the mode of the frost on the fin 113 of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. 従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の温度との関係を示す図である。It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus, and the temperature of the heat exchanger tube 112. FIG. 従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の熱交換量との関係を示す図である。It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 and the heat exchange amount of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus. 従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の冷媒流量との関係を示す図である。It is a figure which shows the relationship between the refrigerant | coolant flow path of the heat exchanger tube 112 of the conventional refrigeration cycle apparatus, and the refrigerant | coolant flow volume of the heat exchanger tube 112. FIG.
　以下、本発明を実施するための形態について、図面を参照して説明する。ここで、図１を含めた、以下の図面において、同一の符号を付したものは、同一又はこれに相当するものであり、以下に記載する実施の形態の全文において共通することとする。そして、明細書全文に表わされている構成要素の形態は、あくまでも例示であって、明細書に記載された形態に限定するものではない。 Hereinafter, modes for carrying out the present invention will be described with reference to the drawings. Here, in the following drawings including FIG. 1, the same reference numerals denote the same or corresponding parts, and are common to all the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.
実施の形態１．
　図１は本発明の実施の形態１に係る冷凍サイクル装置１００の構成図である。図１に示されるように、冷凍サイクル装置１００は、圧縮機１と、四方弁２と、室内熱交換器３と、膨張弁４と、室外熱交換器５と、を備えている。 Embodiment 1 FIG.
FIG. 1 is a configuration diagram of a refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 1, the refrigeration cycle apparatus 100 includes a compressor 1, a four-way valve 2, an indoor heat exchanger 3, an expansion valve 4, and an outdoor heat exchanger 5.
　圧縮機１は、吸入された冷媒を圧縮して高温及び高圧の冷媒として吐出する、可変容量の圧縮機である。四方弁２は、圧縮機１の吐出側に設けられている冷媒の流路を切り替えるためのものである。図１においては、暖房運転を行うように四方弁２が切り替えられた状態における冷媒流れを実線で示している。また、図１においては、除霜運転を行うように四方弁２が切り替えられた状態における冷媒流れを点線で示している。 The compressor 1 is a variable capacity compressor that compresses sucked refrigerant and discharges it as a high-temperature and high-pressure refrigerant. The four-way valve 2 is for switching the refrigerant flow path provided on the discharge side of the compressor 1. In FIG. 1, the refrigerant flow in a state where the four-way valve 2 is switched so as to perform the heating operation is indicated by a solid line. Moreover, in FIG. 1, the refrigerant | coolant flow in the state in which the four-way valve 2 was switched so that a defrost operation may be performed is shown with the dotted line.
　室内熱交換器３は、冷房運転時に蒸発器として機能し、暖房運転時に凝縮器として機能する熱交換器である。膨張弁４は、冷房運転時において室外熱交換器５から流出した冷媒を減圧膨張し、暖房運転時において室内熱交換器３から流出した冷媒を減圧膨張するためのものである。室外熱交換器５は、冷房運転時に凝縮器として機能し、暖房運転時に蒸発器として機能する熱交換器である。 The indoor heat exchanger 3 is a heat exchanger that functions as an evaporator during cooling operation and functions as a condenser during heating operation. The expansion valve 4 is for decompressing and expanding the refrigerant flowing out of the outdoor heat exchanger 5 during the cooling operation and decompressing and expanding the refrigerant flowing out of the indoor heat exchanger 3 during the heating operation. The outdoor heat exchanger 5 is a heat exchanger that functions as a condenser during cooling operation and functions as an evaporator during heating operation.
　以下に、冷凍サイクル装置１００において暖房運転を実行した場合における冷媒流れについて説明する。暖房運転を実行する場合において、四方弁２は暖房側に切り替えられ、室内熱交換器３は凝縮器として機能し、室外熱交換器５は蒸発器として機能する。 Hereinafter, the refrigerant flow when the heating operation is performed in the refrigeration cycle apparatus 100 will be described. When performing the heating operation, the four-way valve 2 is switched to the heating side, the indoor heat exchanger 3 functions as a condenser, and the outdoor heat exchanger 5 functions as an evaporator.
　まず、圧縮機１に供給された冷媒は圧縮されて高温高圧のガス冷媒となり、四方弁２を通過し、室内熱交換器３に流入する。室内熱交換器３に流入した冷媒は、室内熱交換器３に導入された室内空気と熱交換して冷却されて液化する。液化された冷媒は、膨張弁４を通過することで低温低圧のガス冷媒と液冷媒が混在した二相冷媒状態となり、室外熱交換器５に流入する。室外熱交換器５に流入した冷媒は、室外熱交換器５に導入された室外空気と熱交換して加熱されてガス化した状態で圧縮機１に戻る。暖房運転を実行し、室外熱交換器５の累積霜量が多くなると、除霜運転が開始される。 First, the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the indoor heat exchanger 3. The refrigerant that has flowed into the indoor heat exchanger 3 is cooled and liquefied by heat exchange with the indoor air introduced into the indoor heat exchanger 3. The liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the outdoor heat exchanger 5. The refrigerant flowing into the outdoor heat exchanger 5 returns to the compressor 1 in a state where it is heated and gasified by exchanging heat with outdoor air introduced into the outdoor heat exchanger 5. When the heating operation is executed and the cumulative amount of frost in the outdoor heat exchanger 5 increases, the defrosting operation is started.
　以下に、冷凍サイクル装置１００において除霜運転を実行した場合における冷媒流れについて説明する。除霜運転を実行する場合において、四方弁２は冷房側に切り替えられ、室内熱交換器３は蒸発器として機能し、室外熱交換器５は凝縮器として機能する。除霜運転時における冷媒流れは、暖房運転時における冷媒流れとは逆方向となる。 Hereinafter, the refrigerant flow when the defrosting operation is performed in the refrigeration cycle apparatus 100 will be described. When performing the defrosting operation, the four-way valve 2 is switched to the cooling side, the indoor heat exchanger 3 functions as an evaporator, and the outdoor heat exchanger 5 functions as a condenser. The refrigerant flow during the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.
　まず、圧縮機１に供給された冷媒は圧縮されて高温高圧のガス冷媒となり、四方弁２を通過し、室外熱交換器５に流入する。室外熱交換器５に流入した冷媒は、室外熱交換器５に導入された室内空気と熱交換して冷却されて液化する。液化された冷媒は、膨張弁４を通過することで低温低圧のガス冷媒と液冷媒が混在した二相冷媒状態となり、室内熱交換器３に流入する。室内熱交換器３に流入した冷媒は、室内熱交換器３に導入された室外空気と熱交換して加熱されてガス化した状態で圧縮機１に戻る。 First, the refrigerant supplied to the compressor 1 is compressed to become a high-temperature and high-pressure gas refrigerant, passes through the four-way valve 2, and flows into the outdoor heat exchanger 5. The refrigerant that has flowed into the outdoor heat exchanger 5 is cooled and liquefied by exchanging heat with the indoor air introduced into the outdoor heat exchanger 5. The liquefied refrigerant passes through the expansion valve 4 to become a two-phase refrigerant state in which low-temperature and low-pressure gas refrigerant and liquid refrigerant are mixed, and flows into the indoor heat exchanger 3. The refrigerant flowing into the indoor heat exchanger 3 returns to the compressor 1 in a state of being heated and gasified by exchanging heat with outdoor air introduced into the indoor heat exchanger 3.
　図２は本発明の実施の形態１に係る冷凍サイクル装置１００の室外熱交換器５の外観図である。図３は本発明の実施の形態１に係る冷凍サイクル装置１００の室外熱交換器５の概要を示す斜視図である。なお、図２，図３内の矢印は空気の流れを示している。空気は、送風手段（図示省略）を駆動させることでフィン間の隙間を通過する。 FIG. 2 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 3 is a perspective view showing an outline of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. The arrows in FIGS. 2 and 3 indicate the flow of air. The air passes through the gaps between the fins by driving the blowing means (not shown).
　図２に示されるように、室外熱交換器５は、ヘッダ１０，１１と、伝熱管１２と、フィン１３と、を備える。ヘッダ１０は室外熱交換器５の下方に設けられ、ヘッダ１１は室外熱交換器５の下方に設けられている。ヘッダ１０，１１は、例えば、中空筒状の形状で構成されている。伝熱管１２は、冷媒が流れる複数の流路を内部に有し、直線上に延びる扁平状のものであり、ヘッダ１０，１１に挿入されている。なお、フィン１３は、例えば、コルゲート状のフィンであり、隣接する伝熱管１２同士の隙間に密着介入されている。 As shown in FIG. 2, the outdoor heat exchanger 5 includes headers 10 and 11, heat transfer tubes 12, and fins 13. The header 10 is provided below the outdoor heat exchanger 5, and the header 11 is provided below the outdoor heat exchanger 5. The headers 10 and 11 are configured in, for example, a hollow cylindrical shape. The heat transfer tube 12 has a plurality of flow paths through which the refrigerant flows and has a flat shape extending linearly and is inserted into the headers 10 and 11. In addition, the fin 13 is a corrugated fin, for example, and is closely intervened in the gap between the adjacent heat transfer tubes 12.
　図２に示されるように、ヘッダ１０は冷媒配管１０１と接続されている。冷媒配管１０１は膨張弁４と接続されている。ヘッダ１１は冷媒配管１０２と接続されている。冷媒配管１０２は四方弁２と接続されている。 As shown in FIG. 2, the header 10 is connected to the refrigerant pipe 101. The refrigerant pipe 101 is connected to the expansion valve 4. The header 11 is connected to the refrigerant pipe 102. The refrigerant pipe 102 is connected to the four-way valve 2.
　なお、伝熱管１２は複数の冷媒流路を有するように構成される例に限定されず、複数の伝熱管の各々が単一の冷媒流路を有するように構成されていてもよい。また、フィン１３は、上述の例に限定されるものではなく、プレートタイプのフィンを用いてもよく、また、フィンを用いないフィンレスタイプを採用してもよい。 In addition, the heat transfer tube 12 is not limited to the example configured to have a plurality of refrigerant flow paths, and each of the plurality of heat transfer tubes may be configured to have a single refrigerant flow path. Moreover, the fin 13 is not limited to the above-mentioned example, A plate type fin may be used and the finless type which does not use a fin may be employ | adopted.
　ここで、暖房運転時には、気液二相冷媒が、冷媒配管１０１を通ってヘッダ１０に流入し、ヘッダ１０内に流入した冷媒が伝熱管１２に分配される。そして、伝熱管１２内を流れる気液二相冷媒は、空気と熱交換してガス冷媒となってヘッダ１１に流出する。ヘッダ１１に流出したガス冷媒は冷媒配管１０２に導かれる。 Here, during the heating operation, the gas-liquid two-phase refrigerant flows into the header 10 through the refrigerant pipe 101, and the refrigerant that has flowed into the header 10 is distributed to the heat transfer pipe 12. The gas-liquid two-phase refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes a gas refrigerant and flows out to the header 11. The gas refrigerant that has flowed out to the header 11 is guided to the refrigerant pipe 102.
　一方、冷房運転時や除霜運転時においては、ガス冷媒が冷媒配管１０２を通ってヘッダ１１内に流入し、ヘッダ１１内に流入した冷媒が複数の伝熱管１２に分配される。そして、伝熱管１２内を流れるガス冷媒は、空気と熱交換して液冷媒となってヘッダ１０に流出する。ヘッダ１０に流出した液冷媒は冷媒配管１０１に導かれる。このように、冷房運転時や除霜運転時における冷媒流れは、暖房運転時における冷媒流れとは逆方向となっている。 On the other hand, during the cooling operation or the defrosting operation, the gas refrigerant flows into the header 11 through the refrigerant pipe 102, and the refrigerant that has flowed into the header 11 is distributed to the plurality of heat transfer tubes 12. Then, the gas refrigerant flowing in the heat transfer tube 12 exchanges heat with air and becomes liquid refrigerant and flows out to the header 10. The liquid refrigerant that has flowed out to the header 10 is guided to the refrigerant pipe 101. Thus, the refrigerant flow during the cooling operation or the defrosting operation is in the opposite direction to the refrigerant flow during the heating operation.
　図３に示されるように、伝熱管１２の端部には風上側から順に開口部１５Ａ～１５Ｆが設けられている。図３においては、伝熱管１２の一端側に開口部が設けられる例を図示しているが、伝熱管１２の他端側においても同様に開口部が設けられる構成となっている。また、図３に示されるように、伝熱管１２の内部には複数の冷媒流路１５が設けられている。複数の冷媒流路１５のうち風上側から順に冷媒流路１５ａ，１５ｂ，１５ｃ，１５ｄ，１５ｅ，１５ｆと称する。なお、以後の説明において、冷媒流路１５ａ，１５ｂ，１５ｃを冷媒流路１５ａ～１５ｃと記載することがあるものとする。また、以後の説明において、冷媒流路１５ｄ，１５ｅ，１５ｆを冷媒流路１５ｄ～１５ｆと記載することがあるものとする。 As shown in FIG. 3, openings 15A to 15F are provided at the end of the heat transfer tube 12 in order from the windward side. Although FIG. 3 illustrates an example in which an opening is provided on one end side of the heat transfer tube 12, the opening is similarly provided on the other end side of the heat transfer tube 12. Further, as shown in FIG. 3, a plurality of refrigerant flow paths 15 are provided inside the heat transfer tube 12. Among the plurality of refrigerant channels 15, the refrigerant channels 15a, 15b, 15c, 15d, 15e, and 15f are sequentially called from the windward side. In the following description, the refrigerant channels 15a, 15b, and 15c may be referred to as refrigerant channels 15a to 15c. In the following description, the refrigerant channels 15d, 15e, and 15f may be referred to as refrigerant channels 15d to 15f.
　伝熱管１２の風上側の部位を風上側伝熱管１２ａと称する。また、フィン１３の風上側の部位を風上側フィン１３ａと称する。また、フィン１３の表面にはルーバー１４が設けられている。ルーバー１４は、伝熱を促進させるように切り起こされた形状を有する。 The portion on the windward side of the heat transfer tube 12 is referred to as the windward heat transfer tube 12a. A portion on the windward side of the fin 13 is referred to as a windward fin 13a. A louver 14 is provided on the surface of the fin 13. The louver 14 has a shape cut and raised so as to promote heat transfer.
　室外熱交換器５には、暖房運転時において、上述したようにガス冷媒及び液冷媒が混在した二相冷媒が流入するため、ヘッダ１０から伝熱管１２の複数の冷媒流路１５に分配されるとき、ヘッダ１０と冷媒流路１５の関係によって、各々の冷媒流路１５に流れる冷媒の流量比率やガス冷媒と液冷媒の比率が異なる流れが生じる。 Since the two-phase refrigerant mixed with the gas refrigerant and the liquid refrigerant flows into the outdoor heat exchanger 5 during the heating operation as described above, the refrigerant is distributed from the header 10 to the plurality of refrigerant flow paths 15 of the heat transfer pipe 12. Depending on the relationship between the header 10 and the refrigerant flow path 15, there are flows in which the flow rate ratio of the refrigerant flowing in each refrigerant flow path 15 and the ratio of the gas refrigerant and the liquid refrigerant are different.
　図４は本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。図５は本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。図６は本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２のフィン１３上の霜の様子を示す図である。なお、本実施の形態１においては、ヘッダ１０に供給されるガス冷媒及び液冷媒のうち、ガス冷媒がヘッダ１０の上部に集まりやすい層状流、波状流、気泡流、プラグ流のような流れが生じる場合を想定している。 FIG. 4 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 5 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 6 is a diagram showing a state of frost on the fins 13 of the heat transfer tubes 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. In the first embodiment, among the gas refrigerant and liquid refrigerant supplied to the header 10, there is a flow such as a laminar flow, a wavy flow, a bubble flow, and a plug flow in which the gas refrigerant is likely to collect on the upper portion of the header 10. It is assumed that it will occur.
　図４に示されるように、ヘッダ１０の内部のうち下方には液冷媒が溜まっており、ヘッダ１０の内部のうち上方にはガス冷媒が溜まっている。例えば、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、下端に設けられる開口部が液冷媒の液面よりも上方に位置し、ヘッダ１０の内部におけるガス冷媒の進行方向とは反対方向を向くように曲折されている。例えば、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、下端に設けられる開口部が液冷媒の液面よりも下方に位置するように構成されている。 As shown in FIG. 4, liquid refrigerant is accumulated in the lower part of the header 10, and gas refrigerant is accumulated in the upper part of the header 10. For example, in the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12, the opening provided at the lower end is located above the liquid level of the liquid refrigerant and is opposite to the traveling direction of the gas refrigerant inside the header 10. It is bent to face the direction. For example, the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is configured such that the opening provided at the lower end is positioned below the liquid level of the liquid refrigerant.
　なお、以上の説明においては、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位が曲折される例について説明したが、これに限定されない。例えば、伝熱管１２のうち冷媒流路１５ａを有する伝熱管のみ曲折するようにしてもよい。伝熱管１２のうち空気の流れの最も上流側に位置する冷媒流路１５を含む１又は連続する２以上の冷媒流路１５を有する部位を曲折する構成となっていればよい。 In addition, in the above description, although the example in which the site | part which has the refrigerant flow paths 15a-15c among the heat exchanger tubes 12 was bent was demonstrated, it is not limited to this. For example, only the heat transfer tube having the refrigerant flow path 15a among the heat transfer tubes 12 may be bent. What is necessary is just to be the structure which bends the site | part which has 1 or 2 or more continuous refrigerant | coolant flow paths 15 including the refrigerant flow path 15 located in the most upstream side of the air flow among the heat exchanger tubes 12. FIG.
　図４のように伝熱管１２を構成することで、ヘッダ１０の内部の上方を流れるガス冷媒は、慣性力により冷媒流路１５ａ～１５ｃに流入しやすくなる。一方、ヘッダ１０の内部の下方を流れる液冷媒は、冷媒流路１５ｄ～１５ｆの内部に吸い上げられる。すなわち、冷媒流路１５ｄ～１５ｆを流れる二相冷媒は、冷媒流路１５ａ～１５ｃを流れる二相冷媒よりも、ガス冷媒の比率が小さくなる。冷媒流路１５ａ～１５ｆを通過した二相冷媒は、空気と熱交換してガス単相の冷媒へと変化し、ヘッダ１１に供給される。 By configuring the heat transfer tube 12 as shown in FIG. 4, the gas refrigerant flowing inside the header 10 is likely to flow into the refrigerant flow paths 15a to 15c due to inertial force. On the other hand, the liquid refrigerant flowing under the header 10 is sucked into the refrigerant flow paths 15d to 15f. That is, the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller gas refrigerant ratio than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c. The two-phase refrigerant that has passed through the refrigerant flow paths 15a to 15f exchanges heat with air, changes to a gas single-phase refrigerant, and is supplied to the header 11.
　図５に示されるように、ヘッダ１１の内部にはガス冷媒が溜められている。例えば、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、直線状に延びるように構成されている。例えば、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、ヘッダ１１の内部におけるガス冷媒の進行方向とは反対方向を向くように曲折されている。これにより、冷媒流路１５ａ～１５ｃと冷媒流路１５ｄ～１５ｆの管内圧力損失を同等、又は冷媒流路１５ａ～１５ｃよりも冷媒流路１５ｄ～１５ｆの管内圧力損失を大きくし、冷媒流路１５ａ～１５ｃに流れるガス冷媒の流量をより多くすることができる。これは、同等の流量の二相冷媒を比べた場合、ガス冷媒の割合が多くなるほど管内圧力損失が増加してしまうこと、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位が曲折して圧力損失が増加することで、伝熱管１２のうち冷媒流路１５ａ～１５ｃの流量が低減してしまうのを抑制するためである。 As shown in FIG. 5, a gas refrigerant is stored inside the header 11. For example, portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are configured to extend linearly. For example, a portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so as to face the direction opposite to the traveling direction of the gas refrigerant inside the header 11. As a result, the in-tube pressure loss of the refrigerant channels 15a to 15c and the refrigerant channels 15d to 15f are equal, or the in-tube pressure loss of the refrigerant channels 15d to 15f is made larger than that of the refrigerant channels 15a to 15c. The flow rate of the gas refrigerant flowing to ˜15c can be increased. This is because, when comparing two-phase refrigerants of the same flow rate, the pressure loss in the pipe increases as the proportion of the gas refrigerant increases, and the part of the heat transfer pipe 12 having the refrigerant flow paths 15a to 15c is bent. This is to prevent the flow rate of the refrigerant flow paths 15a to 15c in the heat transfer tube 12 from being reduced due to an increase in pressure loss.
　図４に示されるように伝熱管１２を構成することで、暖房運転時においては、冷媒流路１５ａ～１５ｃを流れる二相冷媒は、冷媒流路１５ｄ～１５ｆを流れる二相冷媒よりも、ガス冷媒の比率が大きく、冷媒流路１５ｄ～１５ｆを流れる二相冷媒は、冷媒流路１５ａ～１５ｃを流れる二相冷媒よりも、ガス冷媒の比率が小さくなる。このため、伝熱管１２のうち風上側に設けられる冷媒流路を流れる冷媒が空気と熱交換する熱交換量を抑制することができ、図６に示されるように、フィンに付着する霜は風上側から風下側に向かって均等になる。 By configuring the heat transfer tube 12 as shown in FIG. 4, during the heating operation, the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c is more gas than the two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f. The two-phase refrigerant flowing through the refrigerant flow paths 15d to 15f has a smaller ratio of the gas refrigerant than the two-phase refrigerant flowing through the refrigerant flow paths 15a to 15c. For this reason, the heat exchange amount in which the refrigerant flowing through the refrigerant flow path provided on the windward side of the heat transfer tube 12 exchanges heat with air can be suppressed, and as shown in FIG. It becomes uniform from the upper side toward the leeward side.
　図５に示されるように伝熱管１２を構成することで、冷房運転や除霜運転時には、ヘッダ１１の内部のガス単相冷媒が、冷媒流路１５に供給される場合に、冷媒流路１５ａ～１５ｃを流れる冷媒は、冷媒流路１５ｄ～１５ｆを流れる冷媒よりも多くなるため、冷媒流路１５ａ～１５ｃにおける熱交換量を増加させることができる。 By configuring the heat transfer tube 12 as shown in FIG. 5, when the gas single-phase refrigerant inside the header 11 is supplied to the refrigerant channel 15 during the cooling operation or the defrosting operation, the refrigerant channel 15 a Since the refrigerant flowing through the refrigerant channels 15-15c is larger than the refrigerant flowing through the refrigerant channels 15d-15f, the amount of heat exchange in the refrigerant channels 15a-15c can be increased.
　図７は本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の温度との関係を示す図である。図８は本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の熱交換量との関係を示す図である。図９は本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の冷媒流路と伝熱管１２の冷媒流量との関係を示す図である。 FIG. 7 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the temperature of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 8 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the heat exchange amount of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 9 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 12 and the refrigerant flow rate of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
　図７の横軸には伝熱管１２の冷媒流路を規定し、図７の縦軸には伝熱管１２の温度を規定している。図８の横軸には伝熱管１２の冷媒流路を規定し、図８の縦軸には伝熱管１２の熱交換量を規定している。図９の横軸には伝熱管１２の冷媒流路を規定し、図９の縦軸には伝熱管１２の冷媒流量を規定している。 7, the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 7. The horizontal axis in FIG. 8 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis in FIG. 8 defines the heat exchange amount of the heat transfer tube 12. The horizontal axis of FIG. 9 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 9 defines the refrigerant flow rate of the heat transfer tube 12.
　図７に示されるように、冷媒の温度は冷媒流路の風上側から冷媒流路の風下側に亘って一定となっている。図７に示されるように、空気の温度は冷媒流路の風上側から冷媒流路の風下側に向かうにつれて温度が低下している。図８に示されるように、室外熱交換器５の熱交換量は冷媒流路の風上側から冷媒流路の風下側に向かって増加するようになっている。 As shown in FIG. 7, the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 7, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 8, the heat exchange amount of the outdoor heat exchanger 5 is increased from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
　図９に示されるように、伝熱管１２の内部を流れるガス冷媒の流量は冷媒流路の風上側から冷媒流路の風下側に向かって減少するようになっている。図９に示されるように、伝熱管１２の内部を流れる液冷媒の流量は冷媒流路の風上側から冷媒流路の風下側に増加するようになっている。 As shown in FIG. 9, the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path. As shown in FIG. 9, the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 increases from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path.
　本実施の形態１においては、図７のように、風上側の冷媒温度と空気温度の温度差が大きくとも、図８のように、風上側の熱交換量を抑制し、風下側の熱交換量を促進するようになっている。このため、本実施の形態１においては、図９のように、ガス冷媒の割合が多い二相冷媒が風上側の冷媒流路を流れ、液冷媒の割合が多い二相冷媒が風下側の冷媒流路を流れることで、冷媒の潜熱をより多く得ることが可能となる風下側における熱交換が促進される。また、フィン１３上を流れる空気は上流側から下流側に流れるにつれて、空気が持つ水蒸気量が低下する。 In the first embodiment, as shown in FIG. 7, even if the temperature difference between the refrigerant temperature on the windward side and the air temperature is large, the amount of heat exchange on the windward side is suppressed and the heat exchange on the leeward side is suppressed as shown in FIG. To promote the amount. Therefore, in the first embodiment, as shown in FIG. 9, the two-phase refrigerant having a high ratio of gas refrigerant flows through the refrigerant channel on the leeward side, and the two-phase refrigerant having a high ratio of liquid refrigerant is the refrigerant on the leeward side. By flowing through the flow path, heat exchange on the leeward side that can obtain more latent heat of the refrigerant is promoted. Further, as the air flowing on the fins 13 flows from the upstream side to the downstream side, the amount of water vapor that the air has decreases.
　図１０は本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。図１１は本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。図１２は本発明の実施の形態１に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２の組み立て工程を説明する斜視図及び正面断面図である。 FIG. 10 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 11 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. FIG. 12 is a perspective view and a front sectional view for explaining an assembly process of the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention.
　図１０に示されるように、ヘッダ１０は、例えば、弧状部材１０ａ及び弧状部材１０ｂで構成されている。弧状部材１０ａ及び弧状部材１０ｂは、例えば、断面弧形状の部材で構成されている。以下に、ヘッダ１０及び伝熱管１２を組み立てる工程について説明する。 As shown in FIG. 10, the header 10 includes, for example, an arc member 10a and an arc member 10b. The arc-shaped member 10a and the arc-shaped member 10b are configured by, for example, members having a cross-sectional arc shape. Below, the process of assembling the header 10 and the heat transfer tube 12 will be described.
　まず、伝熱管１２は、例えば冷媒流路１５ｃと冷媒流路１５ｄとの間で伝熱管１２の長手方向に切れ目が入っている状態にして、図１０に示されるように、弧状部材１０ａに挿入される。挿入された伝熱管１２のうち、冷媒流路１５ａ～１５ｃ側にあたる伝熱管１２端部の一方は、例えば、曲げ加工機によって冷媒流路開口部がヘッダ長手方向に向かって曲折され、図１１の状態になる。 First, the heat transfer tube 12 is inserted into the arc-shaped member 10a as shown in FIG. 10, for example, in a state where there is a cut in the longitudinal direction of the heat transfer tube 12 between the refrigerant flow channel 15c and the refrigerant flow channel 15d. Is done. Among the inserted heat transfer tubes 12, one of the end portions of the heat transfer tubes 12 corresponding to the refrigerant flow paths 15a to 15c is bent in the longitudinal direction of the header by a bending machine, for example, as shown in FIG. It becomes a state.
　次に、図１１に示されるように、伝熱管１２が弧状部材１０ａに挿入されて伝熱管１２の一部が曲折された状態で、弧状部材１０ａと弧状部材１０ｂとを嵌め合わせることでヘッダ１０が形成される。具体的には、例えば、弧状部材１０ａと弧状部材１０ｂとの嵌め会わせは、例えば、ベルトコンベア式一体ろう付け工程等により行われる。これにより、図１２の状態になる。 Next, as shown in FIG. 11, in a state where the heat transfer tube 12 is inserted into the arcuate member 10a and a part of the heat transfer tube 12 is bent, the arcuate member 10a and the arcuate member 10b are fitted to each other to fit the header 10. Is formed. Specifically, for example, the fitting of the arc-shaped member 10a and the arc-shaped member 10b is performed by, for example, a belt conveyor type integrated brazing process or the like. As a result, the state shown in FIG. 12 is obtained.
　なお、上述した組み立て工程は、図１２に記載のような円管型ヘッダの場合に限らず、複数の部材によって構成されるヘッダの場合においても、曲げ加工機が伝熱管１２を曲げる工程の障害とならない限り、適用することができる。上述したように伝熱管１２に対して曲げ加工を施すことで、ヘッダ１０に挿入された伝熱管１２は、ベルトコンベア式一体ろう付け工程の途中において、伝熱管１２が熱膨張して伝熱管１２がヘッダ１０から抜けてしまう問題を解決できる効果も併せ持つ。 The above-described assembly process is not limited to the case of the circular pipe header as shown in FIG. 12, but also in the case of a header constituted by a plurality of members, the obstacle in the process of bending the heat transfer tube 12 by the bending machine. As long as it is not, it can be applied. By bending the heat transfer tube 12 as described above, the heat transfer tube 12 inserted into the header 10 is thermally expanded in the course of the belt conveyor type integrated brazing process so that the heat transfer tube 12 is thermally expanded. Has the effect of solving the problem of missing from the header 10.
　図１３は本発明の実施の形態１に係る冷凍サイクル装置１００の伝熱管１２の斜視図である。図１３に示されるように、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は曲折され、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は曲折されずに直線上に延びている。このように、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位のヘッダ１０側の端部に設けられる開口部の方向は、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する伝熱管のヘッダ１０側の端部に設けられる開口部の方向と相違している。 FIG. 13 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 1 of the present invention. As shown in FIG. 13, portions of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c are bent, and portions of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are not bent and extend in a straight line. Yes. As described above, the direction of the opening provided in the end portion on the header 10 side of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the same as that of the heat transfer tube having the refrigerant flow paths 15d to 15f in the heat transfer tube 12. This is different from the direction of the opening provided at the end on the header 10 side.
　図２９は従来の冷凍サイクル装置のヘッダ１１０及び伝熱管１１２を示す図である。図３０は従来の冷凍サイクル装置のヘッダ１１１及び伝熱管１１２を示す図である。図３１は従来の冷凍サイクル装置の伝熱管１１２のフィン１１３上の霜の様子を示す図である。 FIG. 29 is a diagram showing a header 110 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus. FIG. 30 is a diagram showing a header 111 and a heat transfer tube 112 of a conventional refrigeration cycle apparatus. FIG. 31 is a diagram showing a state of frost on the fin 113 of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
　図２９に示されるように、従来の伝熱管１１２は、全ての冷媒流路１１５に対応して、ヘッダ１１０の内部に位置する下端側の部位は曲折されず直線状に平行に延びている。また、図３０に示されるように、従来の伝熱管１１２は、ヘッダ１１１の内部に位置する上端側の部位は曲折されず直線状に平行に延びている。 As shown in FIG. 29, the conventional heat transfer tube 112 corresponds to all the refrigerant flow paths 115, and the lower end portion located inside the header 110 extends in a straight line without being bent. In addition, as shown in FIG. 30, the conventional heat transfer tube 112 extends in a straight line without being bent at the upper end portion located inside the header 111.
　図３２は従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の温度との関係を示す図である。図３３は従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の熱交換量との関係を示す図である。図３４は従来の冷凍サイクル装置の伝熱管１１２の冷媒流路と伝熱管１１２の冷媒流量との関係を示す図である。 FIG. 32 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the temperature of the heat transfer tube 112 of the conventional refrigeration cycle apparatus. FIG. 33 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the heat exchange amount of the heat transfer tube 112 of the conventional refrigeration cycle apparatus. FIG. 34 is a diagram showing the relationship between the refrigerant flow path of the heat transfer tube 112 and the refrigerant flow rate of the heat transfer tube 112 of the conventional refrigeration cycle apparatus.
　図３２の横軸には伝熱管１２の冷媒流路を規定し、図３２の縦軸には伝熱管１２の温度を規定している。図３３の横軸には伝熱管１２の冷媒流路を規定し、図３３の縦軸には伝熱管１２の熱交換量を規定している。図３４の横軸には伝熱管１２の冷媒流路を規定し、図３４の縦軸には伝熱管１２の冷媒流量を規定している。 32, the horizontal axis of the heat transfer tube 12 is defined on the horizontal axis, and the temperature of the heat transfer tube 12 is defined on the vertical axis of FIG. 32. The horizontal axis of FIG. 33 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 33 defines the heat exchange amount of the heat transfer tube 12. The horizontal axis of FIG. 34 defines the refrigerant flow path of the heat transfer tube 12, and the vertical axis of FIG. 34 defines the refrigerant flow rate of the heat transfer tube 12.
　図３２に示されるように、冷媒の温度は冷媒流路の風上側から冷媒流路の風下側に亘って一定となっている。図３２に示されるように、空気の温度は冷媒流路の風上側から冷媒流路の風下側に向かうにつれて温度が低下している。図３３に示されるように、室外熱交換器５の熱交換量は冷媒流路の風上側から冷媒流路の風下側に向かって減少するようになっている。 32, the temperature of the refrigerant is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel. As shown in FIG. 32, the temperature of the air decreases as it goes from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 33, the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path.
　図３４に示されるように、伝熱管１２の内部を流れるガス冷媒の流量は冷媒流路の風上側から冷媒流路の風下側に亘って一定となっている。図３４に示されるように、伝熱管１２の内部を流れる液冷媒の流量は冷媒流路の風上側から冷媒流路の風下側に亘って一定となっている。 As shown in FIG. 34, the flow rate of the gas refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant flow path to the leeward side of the refrigerant flow path. As shown in FIG. 34, the flow rate of the liquid refrigerant flowing inside the heat transfer tube 12 is constant from the windward side of the refrigerant channel to the leeward side of the refrigerant channel.
　図２９，図３０に示されるように伝熱管１１２を構成した場合には、図３４に示されるように、ガス冷媒と液冷媒の比率が同様で同量の二相冷媒がヘッダ１１０から分配されることになる。ここで、図３３に示されるように、室外熱交換器５の熱交換量は冷媒流路の風上側から冷媒流路の風下側に向かって減少するようになっているため、空気がフィン１１３の隙間を流れながら冷媒と熱交換する場合に、図３２に示されるように、伝熱管１１２のうち風上側に位置する部位において、最も空気と冷媒との温度差が大きく、風上側から風下側に向かって空気と冷媒との温度差は低くなる。このため、図３１に示されるように、空気と冷媒とが熱交換される熱交換量は、伝熱管１１２のうち風上側に位置する部位において最も多く、霜は最も発生しやすい。そして、従来の伝熱管１１２の風上側に累積した霜は、やがて風路を妨げるため熱交換器を通過する風量低下に繋がること、フィン表面にある霜が熱抵抗となり空気との熱交換効率が低下するといった問題が発生する。 When the heat transfer tube 112 is configured as shown in FIGS. 29 and 30, two-phase refrigerants having the same ratio of gas refrigerant to liquid refrigerant and the same amount are distributed from the header 110 as shown in FIG. Will be. Here, as shown in FIG. 33, the heat exchange amount of the outdoor heat exchanger 5 decreases from the windward side of the refrigerant flow path toward the leeward side of the refrigerant flow path. When the heat exchange with the refrigerant is performed while flowing through the gap, as shown in FIG. 32, the temperature difference between the air and the refrigerant is the largest in the portion located on the windward side of the heat transfer tube 112, and the windward side to the leeward side. The temperature difference between the air and the refrigerant becomes lower. For this reason, as shown in FIG. 31, the amount of heat exchange in which air and refrigerant exchange heat is the largest in the portion located on the windward side of the heat transfer tube 112, and frost is most likely to occur. And the frost accumulated on the windward side of the conventional heat transfer tube 112 eventually leads to a decrease in the air volume passing through the heat exchanger because it obstructs the air path, and the frost on the fin surface becomes a thermal resistance and the heat exchange efficiency with the air is increased. The problem of deteriorating occurs.
　これに対して、本実施の形態１に係る室外熱交換器５は、内部を流れる冷媒と周囲を流れる空気とを熱交換する熱交換器であって、直線状に延びる複数の伝熱管１２と、複数の伝熱管１２の両端の各々が挿入され、冷媒の流れ道を構成する各々中空のヘッダと、を備え、複数の伝熱管１２の各々は、両端に開口部を有し、冷媒が流れる複数の冷媒流路を内部に有し、複数の伝熱管１２の長手方向のうちヘッダ１０と接続している一端において、空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる開口部は、ヘッダ１０側に位置する残りの部位の開口部とヘッダ１０の内部で異なる向きとなっている。特に、１つの伝熱管１２において、ヘッダ１０の長手方向と交差する方向に並ぶ複数の流路のうち、一部の流路の開口部は他の流路の開口部とヘッダ１０内の冷媒流れ方向に対して異なる向きとなるようにする。このため、冷媒流れの慣性力によって一部の流路と他の流路とに冷媒の入りやすさに違いが生じる。本実施の形態１では、ガスと液体とが混在するヘッダ側では一部の流路の開口部は他の流路の開口部とでヘッダ１０内の高さ位置の違いも利用した。しかしながら、ヘッダ内部の冷媒の気体と液体との分布は種々の場合がある。特に高さ方向で分布が定まらないような場合は、流路同士で開口部の高さを必ずしも変える必要はない。また、ガス冷媒のみが流れるヘッダでも高さ位置を異ならせる必要はない。それらの場合は、開口部の向きの違いを流路間でガスと液体と流入分布を生じさせることに利用すればよい。また、ヘッダ１０内で一部の流路の開口部が他の流路の開口部と異なるように曲げ部分を形成し、流路の抵抗が異なるようにすることで冷媒の流入を異ならせるようにしてもよい。このような曲げの違いを冷媒の流入の違いに利用してもよい。また、伝熱管１２の両端のヘッダのうち、一方のヘッダ内にのみ、このような開口部の向きが異なるようにしてもよい。このような構造を利用することにより、除霜運転時において、室外熱交換器５に流入したガス冷媒は、従来よりも、伝熱管１２のうち風上側に位置する伝熱管１２の内部を流れて当該伝熱管１２における熱交換を促進し、暖房運転時において、室外熱交換器５に流入したガス冷媒は、従来よりも、伝熱管１２のうち風上側に位置する伝熱管１２の内部を流れて当該伝熱管１２における熱交換を抑制することができる。したがって、従来よりも除霜効率を向上させることができ、従来よりも着霜を抑制することができる。 On the other hand, the outdoor heat exchanger 5 according to the first embodiment is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air flowing around, and includes a plurality of heat transfer tubes 12 extending linearly. Each end of each of the plurality of heat transfer tubes 12 is inserted, and each of the plurality of heat transfer tubes 12 has an opening at each end so that the refrigerant flows. Provided in some parts including the part located at the most upstream side of the air flow at one end having a plurality of refrigerant flow paths inside and connected to the header 10 in the longitudinal direction of the plurality of heat transfer tubes 12 The opening to be formed has a different orientation in the inside of the header 10 and the opening of the remaining part located on the header 10 side. In particular, in one heat transfer tube 12, among a plurality of flow paths arranged in a direction intersecting with the longitudinal direction of the header 10, the openings of some of the flow paths are the openings of other flow paths and the refrigerant flow in the header 10. Try to have a different orientation to the direction. For this reason, a difference arises in the ease of a refrigerant | coolant entering into a some flow path and another flow path by the inertial force of a refrigerant | coolant flow. In the first embodiment, on the header side where the gas and the liquid are mixed, the difference in the height position in the header 10 is also used between the openings of some of the flow paths and the openings of the other flow paths. However, the distribution of the refrigerant gas and liquid inside the header may be various. In particular, when the distribution is not determined in the height direction, it is not always necessary to change the height of the opening between the flow paths. Moreover, it is not necessary to change the height position even in the header through which only the gas refrigerant flows. In those cases, the difference in the direction of the opening may be used to generate gas, liquid, and inflow distribution between the flow paths. Further, in the header 10, a bent portion is formed so that the openings of some of the flow paths are different from the openings of the other flow paths, and the flow of the refrigerant is made different by making the resistance of the flow paths different. It may be. Such a difference in bending may be used for a difference in refrigerant inflow. Moreover, you may make it the direction of such an opening part differ only in one header among the headers of the both ends of the heat exchanger tube 12. FIG. By using such a structure, during the defrosting operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows inside the heat transfer tube 12 located on the windward side of the heat transfer tube 12 as compared with the conventional case. Heat exchange in the heat transfer tube 12 is promoted, and during the heating operation, the gas refrigerant flowing into the outdoor heat exchanger 5 flows through the heat transfer tube 12 located on the windward side of the heat transfer tube 12 than before. Heat exchange in the heat transfer tube 12 can be suppressed. Therefore, the defrosting efficiency can be improved as compared with the conventional case, and frost formation can be suppressed as compared with the conventional case.
実施の形態２．
　本実施の形態２においては、実施の形態１とは異なるように、伝熱管１２を構成したものである。なお、本実施の形態２において、特に記述しない項目については実施の形態１と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 2. FIG.
In the second embodiment, the heat transfer tube 12 is configured differently from the first embodiment. In the second embodiment, items that are not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
　図１４は本発明の実施の形態２に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。図１５は本発明の実施の形態２に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。図１６は本発明の実施の形態２に係る冷凍サイクル装置１００の伝熱管１２の斜視図である。 FIG. 14 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention. FIG. 15 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention. FIG. 16 is a perspective view of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 2 of the present invention.
　図１４に示されるように、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、その下端がヘッダ１０内の冷媒流れ方向と反対方向に向くように曲折されている。また、図１４に示されるように、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、その下端がヘッダ１０内の冷媒流れ方向と同一方向に向くように曲折されている。図１５に示されるように、伝熱管１２の上端は曲折されずに直線状に延びている。 As shown in FIG. 14, the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so that the lower end thereof faces in the direction opposite to the refrigerant flow direction in the header 10. Further, as shown in FIG. 14, the portion having the refrigerant flow paths 15 d to 15 f in the heat transfer tube 12 is bent so that the lower end thereof faces the same direction as the refrigerant flow direction in the header 10. As shown in FIG. 15, the upper end of the heat transfer tube 12 extends straight without being bent.
　図１６に示されるように、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位の下端に設けられる開口部の向きは、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端に設けられる開口部の向きと反対方向となっている。これにより、ヘッダ１０の内部のガス冷媒は、冷媒流路１５ｄ～１５ｆよりも冷媒流路１５ａ～１５ｃに多く供給される。 As shown in FIG. 16, the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12. The direction is opposite to the direction of the opening provided. As a result, the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
　以上のように、本実施の形態２に係る室外熱交換器５は、複数の伝熱管１２の長手方向の少なくとも一端において、空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる開口部は、ヘッダ１０の内部において冷媒流れ方向と逆向きとなるように構成されており、ヘッダ１０側に位置する残りの部位の開口部は、ヘッダ１０の内部において冷媒流れ方向と同一方向となるように構成されている。
　このため、伝熱管１２の下端のみに曲げ加工するだけでよく、伝熱管１２の上端を曲げ加工する必要がなく、伝熱管１２の挿入口がある例えば円管などを用いることで、実施の形態１のものと比べて加工の簡易化を図ることができる。 As described above, the outdoor heat exchanger 5 according to the second embodiment has a part of the heat transfer tube 12 including a part located at the most upstream side of the air flow at least at one end in the longitudinal direction. The opening provided is configured to be in the direction opposite to the refrigerant flow direction inside the header 10, and the opening of the remaining portion located on the header 10 side is the same as the refrigerant flow direction inside the header 10. It is comprised so that it may become a direction.
For this reason, it is only necessary to bend the lower end of the heat transfer tube 12, it is not necessary to bend the upper end of the heat transfer tube 12, and for example, a circular tube having an insertion port for the heat transfer tube 12 is used. The processing can be simplified as compared with the first one.
　また、本実施の形態２においては、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、その下端がヘッダ１０内の冷媒流れ方向と同一方向に向くように曲折されているため、冷媒流路１５ｄ～１５ｆ側の圧力損失は増大する。したがって、本実施の形態２においては、実施の形態１よりも、ガス冷媒が冷媒流路１５ｄ～１５ｆに浸入しにくくなり、冷媒流路１５ａ～１５ｃに多くのガス冷媒を供給することができる。 In the second embodiment, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is bent so that the lower end thereof is oriented in the same direction as the refrigerant flow direction in the header 10. Pressure loss on the flow paths 15d to 15f side increases. Therefore, in the second embodiment, the gas refrigerant is less likely to enter the refrigerant flow paths 15d to 15f than in the first embodiment, and a larger amount of gas refrigerant can be supplied to the refrigerant flow paths 15a to 15c.
実施の形態３．
　本実施の形態３においては、実施に形態１とは異なり、例えば、伝熱管１２の冷媒流路１５ａ～１５ｃを有する部位をヘッダ１０の中央高さまで挿入して曲折したものである。なお、本実施の形態３において、特に記述しない項目については実施の形態１と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 3 FIG.
In the third embodiment, unlike the first embodiment, for example, the portion having the refrigerant flow paths 15a to 15c of the heat transfer tube 12 is inserted and bent to the center height of the header 10. In Embodiment 3, items that are not particularly described are the same as those in Embodiment 1, and the same functions and configurations are described using the same reference numerals.
　図１７は本発明の実施の形態３に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。図１８は本発明の実施の形態３に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。本実施の形態３においては、実施の形態１とは異なり、ヘッダ１０の内部を流れる気液二相冷媒のうちガス冷媒が、ヘッダ１０の中央高さにあたる位置に集まりやすい環状流のような流れが生じる場合を想定している。 FIG. 17 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention. FIG. 18 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 3 of the present invention. In the third embodiment, unlike the first embodiment, the gas refrigerant out of the gas-liquid two-phase refrigerant flowing inside the header 10 flows like an annular flow that tends to gather at a position corresponding to the center height of the header 10. It is assumed that this occurs.
　図１７に示されるように、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位の下端は、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端よりもヘッダ１０の径方向中心側に位置するように曲折されている。また、図１７に示されるように、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、その下端に設けられる開口部の位置がヘッダ１０の側壁付近の高さまで短くしてなるように切断して構成されている。 As shown in FIG. 17, the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is the center of the header 10 in the radial direction than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. It is bent so that it is located on the side. Also, as shown in FIG. 17, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is such that the position of the opening provided at the lower end thereof is shortened to the height near the side wall of the header 10. It is configured by cutting.
　このようにして、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位の下端に設けられる開口部の向きは、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端に設けられる開口部と相違し、ヘッダ１０の内部のガス冷媒が、冷媒流路１５ｄ～１５ｆよりも冷媒流路１５ａ～１５ｃに多く供給される。 Thus, the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the opening provided at the lower end of the portion of the heat transfer pipe 12 having the refrigerant flow paths 15d to 15f. Unlike the above, the gas refrigerant inside the header 10 is supplied to the refrigerant flow paths 15a to 15c more than the refrigerant flow paths 15d to 15f.
　なお、図１８に示されるように、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端は、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端よりもヘッダ１０の径方向中心側に位置するように直線状に延びるように構成してもよい。このとき、図１８に示されるように、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、その下端に設けられる開口部の位置がヘッダ１０の側壁付近の高さに位置するように曲折されている。 As shown in FIG. 18, the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is smaller in diameter of the header 10 than the lower end of the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f. You may comprise so that it may extend linearly so that it may be located in the direction center side. At this time, as shown in FIG. 18, the portion of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f is arranged such that the position of the opening provided at the lower end thereof is located at a height near the side wall of the header 10. It is bent.
　このようにして、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位の下端に設けられる開口部の向きは、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端に設けられる開口部と相違し、ヘッダ１０の内部のガス冷媒が、冷媒流路１５ｄ～１５ｆよりも冷媒流路１５ａ～１５ｃに多く供給される。 Thus, the orientation of the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is the opening provided at the lower end of the portion of the heat transfer pipe 12 having the refrigerant flow paths 15d to 15f. Unlike the above, the gas refrigerant inside the header 10 is supplied to the refrigerant flow paths 15a to 15c more than the refrigerant flow paths 15d to 15f.
　以上のように、本実施の形態３に係る室外熱交換器５は、ヘッダ１０が中空筒状で構成されており、複数の伝熱管１２の長手方向のうちヘッダ１０と接続している一端において、空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる開口部は、ヘッダ１０側に位置する残りの部位の開口部よりもヘッダ１０の径方向中心側に位置している。このため、本実施の形態３においては、環状流が起こりやすい断面積が小さなヘッダ１０とすることができ、ヘッダ１０のコストを削減することができる。また、本実施の形態３においては、実施の形態１と同様に、ヘッダ１０の内部のガス冷媒は、冷媒流路１５ｄ～１５ｆよりも冷媒流路１５ａ～１５ｃに多く供給される。 As described above, in the outdoor heat exchanger 5 according to the third embodiment, the header 10 has a hollow cylindrical shape, and is connected to the header 10 in the longitudinal direction of the plurality of heat transfer tubes 12. The openings provided in some parts including the part located on the most upstream side of the air flow are located closer to the center side in the radial direction of the header 10 than the openings of the remaining parts located on the header 10 side. Yes. For this reason, in this Embodiment 3, it can be set as the header 10 with a small cross-sectional area where an annular flow tends to occur, and the cost of the header 10 can be reduced. In the third embodiment, as in the first embodiment, more gas refrigerant in the header 10 is supplied to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
実施の形態４．
　本実施の形態４においては、実施の形態１とは異なり、伝熱管１２の扁平面において短軸方向の例えば半面までを切り開くようにしたものである。なお、本実施の形態４において、特に記述しない項目については実施の形態１と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 4 FIG.
In the fourth embodiment, unlike the first embodiment, the flat surface of the heat transfer tube 12 is cut open, for example, to the half surface in the minor axis direction. In the fourth embodiment, items not particularly described are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.
　図１９は本発明の実施の形態４に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。図２０は本発明の実施の形態４に係る冷凍サイクル装置１００の伝熱管１２の形状を示す正面図及び斜視図である。 FIG. 19 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention. FIG. 20 is a front view and a perspective view showing the shape of the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 4 of the present invention.
　図１９に示されるように、例えば、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、ヘッダ１０の内部に位置する部位が外面から内面に亘って貫通する貫通部１２Ａを有するように構成されている。このように構成することで、ヘッダ１０の内部のガス冷媒は、冷媒流路１５ｄ～１５ｆよりも冷媒流路１５ａ～１５ｃに多く供給される。 As shown in FIG. 19, for example, the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c has a through portion 12A in which a portion located inside the header 10 penetrates from the outer surface to the inner surface. It is configured. With this configuration, the gas refrigerant inside the header 10 is supplied more to the refrigerant flow paths 15a to 15c than to the refrigerant flow paths 15d to 15f.
　なお、図２０に示されるように、ヘッダ１０の下端から所定距離だけ上端側に位置する箇所は貫通部１２Ａを設けないようにして、図１９よりも貫通部１２Ａを設ける箇所を限定してもよい。このようにしても、図１９のような構成にした場合と同様の効果を奏することができる。 Note that, as shown in FIG. 20, the portion located on the upper end side by a predetermined distance from the lower end of the header 10 is not provided with the penetration portion 12A, and the location where the penetration portion 12A is provided more than in FIG. Good. Even if it does in this way, there can exist an effect similar to the case where it is set as a structure like FIG.
　以上のように、本実施の形態４に係る室外熱交換器５は、複数の伝熱管１２の長手方向のうちヘッダ１０側に位置する一端において、空気の流れの最も上流側に位置する部位を含む一部の部位は、ヘッダ１０の内部に位置する部位が外面から内面に亘って切り欠かれた貫通部１２Ａを有する。
　このため、本実施の形態４においては、実施の形態１とは異なり、伝熱管１２をヘッダ１０に挿入して伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位を曲折するという工程を経ないで室外熱交換器５を製造することができる。したがって、本実施の形態４は、実施の形態１よりも簡易な工程で室外熱交換器５を製造できる。また、本実施の形態４においては、実施の形態１と同様の効果を得ることができる。 As described above, the outdoor heat exchanger 5 according to the fourth embodiment has a portion located on the most upstream side of the air flow at one end located on the header 10 side in the longitudinal direction of the plurality of heat transfer tubes 12. Some of the parts including the through-hole 12 </ b> A have a part located inside the header 10 cut out from the outer surface to the inner surface.
For this reason, in the fourth embodiment, unlike the first embodiment, the process of inserting the heat transfer tube 12 into the header 10 and bending the portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is performed. Without it, the outdoor heat exchanger 5 can be manufactured. Therefore, this Embodiment 4 can manufacture the outdoor heat exchanger 5 by a simpler process than Embodiment 1. FIG. In the fourth embodiment, the same effect as in the first embodiment can be obtained.
実施の形態５．
　本実施の形態５においては、実施の形態４とは異なり、伝熱管１２の下端をヘッダ１０内の冷媒流入方向と同一方向に曲げるように構成したものである。なお、本実施の形態５において、特に記述しない項目については実施の形態４と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 5 FIG.
In the fifth embodiment, unlike the fourth embodiment, the lower end of the heat transfer tube 12 is bent in the same direction as the refrigerant inflow direction in the header 10. In the fifth embodiment, items that are not particularly described are the same as those in the fourth embodiment, and the same functions and configurations are described using the same reference numerals.
　図２１は本発明の実施の形態５に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。図２２は本発明の実施の形態５に係る冷凍サイクル装置１００の伝熱管１２を示す斜視図である。図２３は本発明の実施の形態５に係る冷凍サイクル装置１００の伝熱管１２を示す斜視図である。 FIG. 21 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention. FIG. 22 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention. FIG. 23 is a perspective view showing heat transfer tube 12 of refrigeration cycle apparatus 100 according to Embodiment 5 of the present invention.
　図２１～図２３に示されるように、伝熱管１２は、下端に設けられる開口部がヘッダ１０の内部において液冷媒の液面よりも上方に位置し、ヘッダ１０の内部におけるガス冷媒の進行方向と同一方向を向くように曲折されている。また、図２２，図２３に示される伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、図１９，図２０に示される伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位と同様に、貫通部１２Ａを有する構成となっている。 As shown in FIGS. 21 to 23, in the heat transfer tube 12, the opening provided at the lower end is positioned above the liquid level of the liquid refrigerant in the header 10, and the traveling direction of the gas refrigerant in the header 10 is as follows. It is bent to face the same direction. Further, the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS. 22 and 23 are the same as the portions having the refrigerant flow paths 15a to 15c in the heat transfer tubes 12 shown in FIGS. In addition, the structure has a through portion 12A.
　このとき、伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位の下端に設けられる開口部は、ヘッダ１０の内部を流れる冷媒進行方向と反対の向きに位置しているため、冷媒が圧力損失が高くなり、ガス冷媒が流れにくい。一方、伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位の下端に設けられる開口部が、ヘッダ１０の内部を流れる冷媒進行方向と同一方向に位置しているため、ガス冷媒が流れやすい構造となっている。 At this time, since the opening provided at the lower end of the portion having the refrigerant flow paths 15d to 15f in the heat transfer tube 12 is located in the direction opposite to the direction of the refrigerant flowing through the header 10, the refrigerant loses pressure loss. The gas refrigerant becomes difficult to flow. On the other hand, since the opening provided at the lower end of the portion having the refrigerant flow paths 15a to 15c in the heat transfer tube 12 is located in the same direction as the direction of refrigerant flowing through the header 10, the structure in which gas refrigerant flows easily It has become.
　以上のように、本実施の形態５に係る室外熱交換器５は、実施の形態４の構成と同様に伝熱管１２を切り欠いて更にヘッダ１０内の冷媒流入方向と同一方向に曲げるようにしたものである。このため、本実施の形態５においては、実施の形態１～３と同等の効果を得つつ、ヘッダ１０に差し込む冷媒高さを短くすることができる。したがって、室外熱交換器５を通過する冷媒の合計圧力損失を低減することが出来る。 As described above, the outdoor heat exchanger 5 according to the fifth embodiment is cut out in the heat transfer tube 12 and bent in the same direction as the refrigerant inflow direction in the header 10 as in the configuration of the fourth embodiment. It is a thing. Therefore, in the fifth embodiment, the height of the refrigerant inserted into the header 10 can be shortened while obtaining the same effect as in the first to third embodiments. Therefore, the total pressure loss of the refrigerant passing through the outdoor heat exchanger 5 can be reduced.
実施の形態６．
　本実施の形態６においては、実施の形態１～５とは異なり、伝熱管１２が挿入されるヘッダ１０の形状を伝熱管１２の挿入方向に向かって幅が細くなる形状としたものである。なお、本実施の形態６において、特に記述しない項目については実施の形態１～５と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 6 FIG.
In the sixth embodiment, unlike the first to fifth embodiments, the shape of the header 10 into which the heat transfer tube 12 is inserted has a shape that becomes narrower in the insertion direction of the heat transfer tube 12. In the sixth embodiment, items not particularly described are the same as those in the first to fifth embodiments, and the same functions and configurations are described using the same reference numerals.
　図２４は本発明の実施の形態６に係る冷凍サイクル装置１００の伝熱管１２及びヘッダ１０の形状の第１の例を示す図である。図２５は本発明の実施の形態６に係る冷凍サイクル装置１００の伝熱管１２及びヘッダ１０の形状の第２の例を示す図である。 FIG. 24 is a diagram showing a first example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention. FIG. 25 is a diagram showing a second example of the shape of the heat transfer tube 12 and the header 10 of the refrigeration cycle apparatus 100 according to Embodiment 6 of the present invention.
　図２４に示されるように、ヘッダ１０の形状を断面三角形となるように構成されている。具体的には、ヘッダ１０は、何れかの辺を底部として最も下方に位置させ、上述の底部と対向する頂部が上方に位置するようにヘッダ１０を設けてもよい。 As shown in FIG. 24, the header 10 is configured to have a triangular cross section. Specifically, the header 10 may be provided such that one of the sides is located at the bottom and the top facing the above-described bottom is located at the top.
　なお、図２５に示されるように、ヘッダ１０の形状が断面六角形となるように構成されていてもよい。具体的には、何れかの辺を底部として最も下方に位置させ、上述の底部と対向する頂部が最も上方に位置するようにヘッダ１０を設けてもよい。 Note that, as shown in FIG. 25, the header 10 may have a hexagonal cross section. Specifically, the header 10 may be provided such that one of the sides is positioned at the lowest position as the bottom and the top portion facing the above-described bottom is positioned at the highest position.
　以上のように、本実施の形態６に係る室外熱交換器５は、伝熱管１２の下端側から伝熱管１２の上端側に向かって水平方向の内部断面積が小さくなるようにヘッダ１０を構成している。このため、ヘッダ１０内部の上方にガス冷媒が溜まりやすくなり、実施の形態１，２，４の効果を一層発揮することができる。 As described above, the outdoor heat exchanger 5 according to the sixth embodiment configures the header 10 so that the horizontal internal cross-sectional area decreases from the lower end side of the heat transfer tube 12 toward the upper end side of the heat transfer tube 12. is doing. For this reason, it becomes easy to accumulate gas refrigerant above the inside of the header 10, and the effects of the first, second, and fourth embodiments can be further exhibited.
　なお、以上説明した実施の形態３～６において、必要に応じて、伝熱管１２の上端において、複数の冷媒流路に対応して、各々圧力損失を異なるように曲げ加工あるいは流路長を短く切断する構成としてもよい。 In the third to sixth embodiments described above, if necessary, the upper end of the heat transfer tube 12 is bent or the flow path length is shortened so as to correspond to a plurality of refrigerant flow paths so that the pressure losses are different. It is good also as a structure cut | disconnected.
実施の形態７．
　本実施の形態７においては、実施の形態１～６とは異なり、室外熱交換器５の形状を変更したものである。なお、本実施の形態７において、特に記述しない項目については実施の形態１～６と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 7 FIG.
In the seventh embodiment, unlike the first to sixth embodiments, the shape of the outdoor heat exchanger 5 is changed. In the seventh embodiment, items not particularly described are the same as those in the first to sixth embodiments, and the same functions and configurations are described using the same reference numerals.
　図２６は本発明の実施の形態７に係る冷凍サイクル装置１００の室外熱交換器５の外観図である。図２６に示されるように、ヘッダ１０，１１が上下方向に設けられ、伝熱管１２を左右方向に設けられるようになっている。 FIG. 26 is an external view of the outdoor heat exchanger 5 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. As shown in FIG. 26, the headers 10 and 11 are provided in the vertical direction, and the heat transfer tubes 12 are provided in the horizontal direction.
　図２７は本発明の実施の形態７に係る冷凍サイクル装置１００のヘッダ１０及び伝熱管１２を示す図である。図２８は本発明の実施の形態７に係る冷凍サイクル装置１００のヘッダ１１及び伝熱管１２を示す図である。なお、図２７においては、液冷媒がヘッダ１０の内部においてヘッダ１０の内壁側に溜まり、ガス冷媒がヘッダ１０の内部においてヘッダ１０の内壁から遠ざかる方向に溜まっている場合を例として説明する。 FIG. 27 is a diagram showing the header 10 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. FIG. 28 is a diagram showing the header 11 and the heat transfer tube 12 of the refrigeration cycle apparatus 100 according to Embodiment 7 of the present invention. In FIG. 27, a case where liquid refrigerant is accumulated on the inner wall side of the header 10 in the header 10 and gas refrigerant is accumulated in the direction away from the inner wall of the header 10 inside the header 10 will be described as an example.
　図２７に示されるように、気液二相冷媒はヘッダ１０の内部において下方から上方に向かって流れるようになっている。伝熱管１２のうち冷媒流路１５ａ～１５ｃを有する部位は、冷媒流れ方向とは反対側に向くように曲折されている。これにより、ヘッダ１０の内部のガス冷媒は冷媒流路１５ａ～１５ｃに供給されやすくなる。 As shown in FIG. 27, the gas-liquid two-phase refrigerant flows in the header 10 from below to above. A portion of the heat transfer tube 12 having the refrigerant flow paths 15a to 15c is bent so as to face the direction opposite to the refrigerant flow direction. Thereby, the gas refrigerant inside the header 10 is easily supplied to the refrigerant flow paths 15a to 15c.
　図２８に示されるように、ガス冷媒はヘッダ１１の内部において下方から上方に向かって流れるようになっている。伝熱管１２のうち冷媒流路１５ｄ～１５ｆを有する部位は、冷媒流れ方向とは同一方向を向くように曲折されている。 As shown in FIG. 28, the gas refrigerant flows in the header 11 from below to above. Parts of the heat transfer tube 12 having the refrigerant flow paths 15d to 15f are bent so as to face the same direction as the refrigerant flow direction.
　以上のように、本実施の形態７に係る冷凍サイクル装置１００は、実施の形態１と同様に、複数の伝熱管１２の長手方向の両端のうちヘッダ１０側に位置する一端はヘッダ１０の内部に位置し、複数の伝熱管１２のうち空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる開口部は、ヘッダ１０側に位置する残りの部位の開口部とヘッダ１０の内部で異なる向きとなっている。このため、本実施の形態７においても、実施の形態１と同一の効果を奏することができる。 As described above, in the refrigeration cycle apparatus 100 according to the seventh embodiment, one end located on the header 10 side among the longitudinal ends of the plurality of heat transfer tubes 12 is the interior of the header 10, as in the first embodiment. Of the plurality of heat transfer tubes 12, the openings provided in a part of the plurality of heat transfer tubes 12 including the part located on the most upstream side of the air flow are the openings of the remaining parts located on the header 10 side and the header 10. It has a different orientation inside. For this reason, also in this Embodiment 7, the same effect as Embodiment 1 can be show | played.
　また、以上の説明においては、熱交換器が室外熱交換器５である例について説明したが、これに限定されない。熱交換器が室内熱交換器である場合についても同様に本発明を適用することができる。 In the above description, the example in which the heat exchanger is the outdoor heat exchanger 5 has been described, but the present invention is not limited to this. The present invention can be similarly applied to the case where the heat exchanger is an indoor heat exchanger.
　以上説明した実施の形態１～７の冷凍サイクル装置１００は、例えば、ヒートポンプ装置等、給湯装置、冷凍装置等に適用することができる。 The refrigeration cycle apparatuses 100 of Embodiments 1 to 7 described above can be applied to, for example, a heat pump apparatus, a hot water supply apparatus, a refrigeration apparatus, and the like.
　１　圧縮機、２　四方弁、３　室内熱交換器、４　膨張弁、５　室外熱交換器、１０　ヘッダ、１０ａ，１０ｂ　弧状部材、１１　ヘッダ、１２　伝熱管、１２Ａ　貫通部、１２ａ　風上側伝熱管、１３　フィン、１３ａ　風上側フィン、１４　ルーバー、１５，１５ａ～１５ｆ　冷媒流路、１５Ａ～１５Ｆ　開口部、１００　冷凍サイクル装置、１０１　冷媒配管、１０２　冷媒配管、１１０　ヘッダ、１１１　ヘッダ、１１２　伝熱管、１１３　フィン、１１５　冷媒流路。 1 compressor, 2-way valve, 3 indoor heat exchanger, 4 expansion valve, 5 outdoor heat exchanger, 10 header, 10a, 10b arc member, 11 header, 12 heat transfer tube, 12A through section, 12a upwind heat transfer tube, 13 fin, 13a upwind fin, 14 louver, 15, 15a-15f refrigerant flow path, 15A-15F opening, 100 refrigeration cycle device, 101 refrigerant piping, 102 refrigerant piping, 110 header, 111 header, 112 heat transfer tube, 113 Fin, 115 refrigerant flow path.

Claims (9)

  1. 　内部を流れる冷媒と周囲を流れる空気とを熱交換する熱交換器であって、
    　直線状に延びる複数の伝熱管と、
    　前記複数の伝熱管の両端の各々が挿入され、冷媒の流れ道を構成する各々中空のヘッダと、を備え、
    　前記複数の伝熱管の各々は、両端に開口部を有し、冷媒が流れる複数の冷媒流路を内部に有し、
    　前記複数の伝熱管の長手方向のうち前記ヘッダと接続している少なくとも一端において、前記空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる前記開口部は、前記一端に設けられる残りの部位の前記開口部と前記ヘッダの内部で異なる向きとなる
    　熱交換器。     A heat exchanger that exchanges heat between refrigerant flowing inside and air flowing around.
    A plurality of heat transfer tubes extending in a straight line;
    Each end of each of the plurality of heat transfer tubes is inserted, and each includes a hollow header that constitutes a flow path of the refrigerant,
    Each of the plurality of heat transfer tubes has openings at both ends, and has a plurality of refrigerant flow paths through which the refrigerant flows,
    In at least one end connected to the header in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located on the most upstream side of the air flow is at the one end. The heat exchanger which becomes a different direction in the inside of the said opening part and the said header of the remaining site | parts provided.
  2. 　前記複数の伝熱管の長手方向の少なくとも一端において、前記空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる前記開口部は、前記ヘッダの内部において冷媒流れ方向と逆向きになるように構成されている
    　請求項１に記載の熱交換器。     At least one end in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located at the most upstream side of the air flow is opposite to the refrigerant flow direction inside the header. The heat exchanger according to claim 1, wherein the heat exchanger is configured as follows.
  3. 　前記複数の伝熱管の長手方向の少なくとも一端において、前記空気の流れの最も上流側に位置する部位を含む一部の部位に設けられる前記開口部は、前記一端に設けられる残りの部位の前記開口部よりも前記ヘッダの径方向中心側に位置している
    　請求項１又は請求項２に記載の熱交換器。     At least one end in the longitudinal direction of the plurality of heat transfer tubes, the opening provided in a part of the part including the part located at the most upstream side of the air flow is the opening of the remaining part provided at the one end. The heat exchanger according to claim 1 or 2, wherein the heat exchanger is located on a radial center side of the header rather than a portion.
  4. 　前記複数の伝熱管の長手方向の少なくとも一端において、前記空気の流れの最も上流側に位置する部位を含む一部の部位は、前記ヘッダの内部に位置する部位が外面から内面に亘って切り欠かれた貫通部を有するように構成されている
    　請求項１に記載の熱交換器。     At least one end in the longitudinal direction of the plurality of heat transfer tubes, some of the parts including the part located at the most upstream side of the air flow are notched from the outer surface to the inner surface. The heat exchanger according to claim 1, wherein the heat exchanger is configured to have a penetrating portion.
  5. 　前記複数の伝熱管の長手方向の少なくとも一端は、前記ヘッダの内部において、冷媒流れ方向と同一方向に曲げられている
    　請求項４に記載の熱交換器。     The heat exchanger according to claim 4, wherein at least one end in the longitudinal direction of the plurality of heat transfer tubes is bent in the same direction as the refrigerant flow direction inside the header.
  6. 　前記複数の伝熱管の長手方向の一端が挿入されている前記ヘッダは、前記伝熱管の下方に設けられている
    　請求項１～請求項５の何れか一項に記載の熱交換器。     The heat exchanger according to any one of claims 1 to 5, wherein the header into which one end in the longitudinal direction of the plurality of heat transfer tubes is inserted is provided below the heat transfer tubes.
  7. 　前記伝熱管の下方に設けられた前記ヘッダは、
    　前記伝熱管の下端側から前記伝熱管の上端側に向かって水平方向の内部断面積が小さくなるように構成されている
    　請求項６に記載の熱交換器。     The header provided below the heat transfer tube is:
    The heat exchanger according to claim 6, wherein a horizontal internal cross-sectional area is reduced from a lower end side of the heat transfer tube toward an upper end side of the heat transfer tube.
  8. 　前記一端に設けられる残りの部位の前記開口部は、前記ヘッダの内部において冷媒流れ方向と同一方向となるように構成されている
    　請求項１、請求項２、請求項３、請求項６、又は請求項７に記載の熱交換器。     The said opening part of the remaining site | part provided in the said one end is comprised so that it may become the same direction as a refrigerant | coolant flow direction inside the said header. Claim 1, Claim 2, Claim 3, Claim 6, or The heat exchanger according to claim 7.
  9. 　請求項１～８の何れか一項に記載の熱交換器の製造方法であって、
    　中空筒状の前記ヘッダを構成する２つの断面弧形状の弧状部材のうち一方の弧状部材に前記複数の伝熱管を挿入する第１工程と、
    　前記第１工程の後に、前記複数の伝熱管のうち前記空気の流れの最も上流側に位置する伝熱管を含む一部の部位を、前記一方のヘッダ側に位置する一端に設けられる開口部が残りの部位の前記一方のヘッダ側に設けられる開口部よりも他端側に位置するように曲折する第２工程と、
    　前記第２工程の後に、前記複数の伝熱管のうち曲折された部位が前記ヘッダの内部に位置するように前記一方の弧状部材と他方の弧状部材とを組み合わせて前記ヘッダを作製する第３工程と、を有する
    　熱交換器の製造方法。     A method of manufacturing a heat exchanger according to any one of claims 1 to 8,
    A first step of inserting the plurality of heat transfer tubes into one arcuate member of two arcuate members having an arcuate cross section constituting the hollow cylindrical header;
    After the first step, an opening provided at one end of the plurality of heat transfer tubes including the heat transfer tube located on the most upstream side of the air flow is provided at one end located on the one header side. A second step of bending so as to be positioned on the other end side than the opening provided on the one header side of the remaining portion;
    After the second step, the third step of producing the header by combining the one arcuate member and the other arcuate member so that the bent portion of the plurality of heat transfer tubes is located inside the header. And a method of manufacturing a heat exchanger.
PCT/JP2015/074366 2015-08-28 2015-08-28 Heat exchanger and method for manufacturing same WO2017037772A1 (en)

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