EP3760957B1 - Appareil de conditionnement d'air - Google Patents

Appareil de conditionnement d'air Download PDF

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Publication number
EP3760957B1
EP3760957B1 EP19761287.2A EP19761287A EP3760957B1 EP 3760957 B1 EP3760957 B1 EP 3760957B1 EP 19761287 A EP19761287 A EP 19761287A EP 3760957 B1 EP3760957 B1 EP 3760957B1
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EP
European Patent Office
Prior art keywords
heat transfer
airflow
header
heat exchanger
portions
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19761287.2A
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German (de)
English (en)
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EP3760957A1 (fr
EP3760957A4 (fr
Inventor
Hiroyuki Nakano
Tooru ANDOU
Hideyuki KUSAKA
Shun Yoshioka
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Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
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Publication of EP3760957A1 publication Critical patent/EP3760957A1/fr
Publication of EP3760957A4 publication Critical patent/EP3760957A4/fr
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Publication of EP3760957B1 publication Critical patent/EP3760957B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/26—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means being integral with the element
    • 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
    • F28D1/0246—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 heat-exchange elements having several adjacent conduits forming a whole, e.g. blocks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/16—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means being integral with the element, e.g. formed by extrusion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
    • F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions

Definitions

  • the present disclosure relates to an air conditioner.
  • Some heat exchangers used in an air conditioner or the like include a small-diameter heat transfer tube unit that is formed by stacking heat transfer fin plates (see, for example, PTL 1 ( Japanese Unexamined Patent Application Publication No. 2006-90636 ) and the like).
  • EP 0 683 371 A1 discloses an air conditioner comprising: a heat exchanger including a plurality of heat transfer units in each of which a plurality of heat transfer channel portions and a plurality of auxiliary heat transfer portions, each of which extends in a first direction, are formed so as to be arranged in a second direction that intersects with or is perpendicular to the first direction, the heat transfer units being arranged in a third direction that is different from both of the first direction and the second direction, and a fan configured to generate airflow flowing in the second direction and passing through spaces between the heat transfer units, wherein the heat transfer units are each divided into an airflow-upstream region and an airflow-downstream region in the second direction.
  • JP 2014137172 A discloses an air conditioner according to the preamble of claim 1 comprising: a heat exchanger including a plurality of heat transfer units arranged in a third direction that is different from both of a first direction and a second direction, the second direction intersecting with or being perpendicular to the first direction; and a fan configured to generate airflow (W) flowing in the second direction and passing through spaces between the heat transfer units, wherein the heat transfer units are each divided into an airflow-upstream region and an airflow-downstream region in the second direction.
  • frosting may concentratedly occur in a part of the heat exchanger due to internal heat flux distribution. Then, blockage of an air passage may occur in the part where frosting has concentratedly occurred, and the performance of the heat exchanger may decrease.
  • An air conditioner according to the invention is defined according to claim 1.
  • a heat exchanger 10 performs heat exchange between a fluid that flows inside and air that flows outside.
  • a first pipe 41 and a second pipe 42, through which a refrigerant flows into or out from the heat exchanger 10, are attached to the heat exchanger 10.
  • a fan 6, for sending air to the heat exchanger 10 is disposed near the heat exchanger 10. The fan 6 generates airflow toward the heat exchanger 10, and, when the airflow passes through the heat exchanger 10, heat exchange is performed between the heat exchanger 10 and air.
  • the heat exchanger 10 functions as an evaporator that absorbs heat from air and as a condenser (radiator) that releases heat to air, and can be installed in an air conditioner or the like.
  • the heat exchanger 10 includes a heat transfer unit group 15, a first header 21, and a second header 22.
  • the heat transfer unit group 15 includes a plurality of heat transfer units 30.
  • the heat transfer unit group 15 is disposed so that airflow generated by the fan 6 passes through spaces between the heat transfer units 30. Details of the arrangement of these members will be described below.
  • the first header 21 is a hollow member that is configured so that a refrigerant in a gas phase, a liquid phase, and a gas-liquid two-phase can flow through the inside thereof.
  • the first header 21 is connected to the heat transfer units 30 at a position above the heat transfer units 30.
  • a connection surface 21S, to which the heat transfer units 30 are connected, is formed on the lower side of the first header 21. Coupling holes, into which end portions 31e of heat transfer channel portions 31 (described below) are inserted, are formed in the connection surface 21S.
  • Fig. 3 illustrates a cross section of the first header 21 when seen in a third direction D3. The definition of the third direction D3 will be described below.
  • the second header 22 is connected to the first pipe 41, the second pipe 42, and the heat transfer unit 30 at a position below the heat transfer units 30; and allows a refrigerant to flow into and flow out of the first pipe 41, the second pipe 42, and the heat transfer units 30.
  • the second header 22 is a hollow member that is configured so that a refrigerant in a gas phase, a liquid phase, and a gas-liquid two-phase can flow through the inside thereof.
  • the second header 22 has a partition member 22p that extends in the third direction D3 and partitions the inside of the second header 22. In the example shown in Fig.
  • the second header 22 is partitioned by the partition member 22p into an airflow-upstream second header 22U and an airflow-downstream second header 22L.
  • the airflow-upstream second header 22U and the airflow-downstream second header 22L are respectively connected to the second header 22 and the first header 21.
  • the partition member 22p may be integrally formed with the second header 22 or may be formed as an independent object.
  • a connection surface 22S, to which the heat transfer units 30 are connected, is formed on the upper side of the second header 22. Coupling holes, into which end portions 31e of heat transfer channel portions 31 (described below) are inserted, are formed in the connection surface 22S.
  • Fig. 4 illustrates the cross-sectional shape of the second header 22 when seen in a third direction D3. The definition of the third direction D3 will be described below.
  • a plurality of heat transfer channel portions 31 and a plurality of auxiliary heat transfer portions 32 are formed so as to be arranged in a "second direction D2" that intersects with or is perpendicular to the first direction D1.
  • the heat transfer channel portions 31 each have a substantially cylindrical shape
  • the auxiliary heat transfer portions 32 each have a substantially flat plate-like shape.
  • the heat transfer channel portions 31 are formed so as to be aligned in the second direction D2 at a predetermined pitch PP.
  • the heat transfer unit group 15 includes at least three or more heat transfer units 30 that are arranged in a stacked manner.
  • first direction D1, the second direction D2, and the third direction D3 are perpendicular to each other.
  • these directions D1 to D3 need not be completely perpendicular to each other, and it is possible to realize the heat exchanger 10 according to the present embodiment as long as these directions intersect with each other.
  • the heat transfer units 30 are connected to the first header 21 and the second header 22 at the connection surfaces 21S and 22S of the first header 21 and the second header 22.
  • end portions 31e of the heat transfer channel portions 31 protrude from end portions 32e of the auxiliary heat transfer portions 32.
  • the end portions 31e of the heat transfer channel portions 31 are inserted into the coupling holes formed in the connection surfaces 21S and 22S of the first header 21 and the second header 22.
  • the heat transfer units 30 are fixed in place between the first header 21 and the second header 22 by, for example, brazing the connection portions (see Fig. 8 ).
  • the heat transfer channel portion 31 enables a refrigerant to move between the first header 21 and the second header 22.
  • a substantially cylindrical passage is formed in the heat transfer channel portion 31, and the refrigerant moves in the passage.
  • the heat transfer channel portion 31 according to the present embodiment has a linear shape in the first direction D1.
  • the auxiliary heat transfer portion 32 accelerates heat exchange between a refrigerant that flows in adjacent heat transfer channel portions 31 and ambient air.
  • the auxiliary heat transfer portion 32 is formed so as to extend in the first direction D1 and is disposed so as to be in contact with the adjacent heat transfer channel portions 31.
  • the auxiliary heat transfer portion 32 may be integrally formed with or may be independently formed from the heat transfer channel portions 31.
  • At least eight or more heat transfer channel portions 31 are formed in the heat transfer unit 30 according to the present embodiment. At least two or more of the heat transfer channel portions 31 are disposed in an airflow-upstream region.
  • Fig. 8 illustrates an example of such a configuration.
  • ten heat transfer channel portions 31 are formed in one heat transfer unit 30.
  • the inside of the second header 22 is partitioned by the partition member 22p into the airflow-upstream second header 22U, which is disposed in an airflow-upstream region WU, and the airflow-downstream second header 22L, which is disposed in an airflow-downstream region WL.
  • Three heat transfer channel portions 31U are connected to the airflow-upstream second header 22U, and seven heat transfer channel portions 31L are connected to the airflow-downstream second header 22L.
  • An auxiliary heat transfer portion 32g is formed at an end portion on the most airflow-upstream side of the heat transfer unit 30.
  • Fig. 8 is a schematic view illustrating the cross-sectional shape of the heat exchanger 10 when seen in the third direction D3.
  • the refrigerant F flows into the airflow-downstream second header 22L via the heat transfer channel portions 31L, which are connected to the first header 21 and the airflow-downstream second header 22L. While the refrigerant F flows through the heat transfer channel portions 31U and 31L, the refrigerant F exchanges heat with the airflow W. Thus, the refrigerant F evaporates and changes into a gas phase. Then, the refrigerant F in the gas phase flows out from the first pipe 41.
  • Fig. 10 illustrates a state when the heat transfer unit 30 is seen in a third direction D3.
  • the refrigerant F flows in a direction opposite from that when the heat exchanger 10 is used as an evaporator. That is, the refrigerant F in a gas phase flows through the first pipe 41 into the heat exchanger 10, and the refrigerant F in a liquid phase flows through the second pipe 42 out from the heat exchanger 10.
  • the heat transfer unit 30 is manufactured from, for example, a metal material such as aluminum or an aluminum alloy.
  • a metal material such as aluminum or an aluminum alloy.
  • extrusion of a metal material is performed by using a die corresponding to the cross-sectional shape of Fig. 5 , and the heat transfer channel portions 31 and the auxiliary heat transfer portions 32 are integrally formed.
  • cutouts 33 are formed by cutting off parts of the auxiliary heat transfer portions 32.
  • the cutouts 33 are formed, for example, by punching and cutting off a plurality of parts of the auxiliary heat transfer portions 32.
  • the first header 21 and the second header 22 are manufactured by processing a metal material into a tubular shape. Coupling holes for inserting the end portions 31e of the heat transfer channel portions 31 are formed in the first header 21 and the second header 22.
  • the coupling holes are circular through-holes that are formed by using, for example, a drill.
  • the end portions 31e of the heat transfer channel portions 31 of the heat transfer units 30 are inserted into the coupling holes of the first header 21 and the second header 22.
  • the end portions 32e of the auxiliary heat transfer portions 32 are brought into contact with the connection surfaces 21S and 22S of the first header 21 and the second header 22.
  • the heat transfer units 30, the first header 21, and the second header 22 are fixed by, for example, brazing.
  • the heat exchanger 10 includes the heat transfer unit 30 in which the plurality of heat transfer channel portions 31 and the plurality of auxiliary heat transfer portions 32, each of which extends in the first direction D1, are formed so as to be arranged in the second direction D2 that intersects with or is perpendicular to the first direction D1.
  • a plurality of heat transfer units 30 are arranged in the third direction D3 that is different from both of the first direction D1 and the second direction D2, and form the heat transfer unit group 15.
  • the heat transfer units 30 are each divided into the airflow-upstream region WU and the airflow-downstream region WL in the second direction D2.
  • the heat exchanger 10 causes a refrigerant F to flow into the heat transfer channel portions 31U disposed in the airflow-upstream region WU, and then causes the refrigerant F to flow out to the heat transfer channel portions 31L disposed in the airflow-downstream region WL.
  • the refrigerant channel is folded back at least once in the second direction D2 in which airflow W is generated.
  • a heat exchanger having high heat exchange performance can be provided.
  • a heat exchanger 10Z illustrated in Fig. 11 which is configured to cause a refrigerant F to flow through the heat transfer units 30Z only once from a lower position to an upper position in the first direction D1
  • a low temperature environment for example, 7°C or lower
  • frosting may occur between the heat transfer units 30Z, because the heat transfer amount in the heat transfer channel portions on the airflow-upstream side is large.
  • blockage of the air passage may occur due to frosting.
  • a partition member or the like is not provided inside of a first header 21Z and a second header 22Z illustrated in Fig. 11 .
  • the heat exchanger 10 because the number of channels of a refrigerant F flowing from the second pipe 42 is limited to the number of the airflow-upstream heat transfer channel portions 31U, pressure loss of the refrigerant occurs. Due to the pressure loss, the refrigerant temperature in the airflow-upstream heat transfer channel portions 31U increases. Therefore, when the heat exchanger 10 is used as an evaporator, the heat exchange amount in the airflow-upstream heat transfer channel portions 31U is suppressed. Thus, variation of heat flux in accordance with the position in the heat transfer unit group 15 can be suppressed. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7°C or lower), local occurrence of frosting can be avoided, and a heat exchanger having high heat exchange performance can be provided.
  • a low temperature environment for example, 7°C or lower
  • the heat exchange amount of the heat transfer channel portions on the airflow-upstream side is large, compared with the heat exchange amount of the heat transfer channel portions on the airflow-downstream side. Therefore, when the refrigerant F flowing from the second pipe 42 is caused to flow to a plurality of heat transfer channel portions, the refrigerant F may completely evaporate in the heat transfer channel portions on the airflow-upstream side. As a result, sufficient heat exchange may not be performed in the heat exchanger X10Z.
  • the number of heat transfer channel portions 31L disposed in the airflow-downstream region WL is larger than the number of heat transfer channel portions 31U disposed in the airflow-upstream region WU.
  • Each of the heat transfer units 30 includes at least eight or more heat transfer channel portions 31, and at least two or more heat transfer channel portions 31U are disposed in the airflow-upstream region WU.
  • the heat exchanger 10 further includes the first header 21 (upper header) and the second header 22 (lower header) that are connected to the heat transfer units 30 from above and below in the first direction D1 and that form a part of the refrigerant channel.
  • the longitudinal direction of the heat transfer units 30 can be directed in the vertical direction, and water adhered to the heat transfer units 30 (dew condensation water and the like) can be easily discharged.
  • ease of assembling and processing can be also increased.
  • the heat exchanger 10 does not exclude a configuration such that the first header 21 and the second header 22 are arranged in the left-right direction instead of the up-down direction.
  • the airflow-upstream region WU and the airflow-downstream region WL are formed by the partition member 22p disposed inside of the second header 22 (lower header).
  • the airflow-upstream region WU and the airflow-downstream region WL can be easily formed without performing special processing or the like on the heat transfer units 30.
  • a partition member may be provided in the first header 21, instead of in the second header 22, in accordance with the flow path of refrigerant.
  • partition members may be provided in both of the first header 21 and the second header 22, in accordance with the flow path of refrigerant.
  • each heat transfer unit 30 can be formed from a single member by extrusion of a metal material.
  • the plurality of cutouts 33 can be simultaneously formed by punching. Accordingly, it is possible to provide the heat exchanger 10 that can be easily assembled and processed.
  • a heat exchanger 10 according to the present embodiment may further include a decompressing mechanism that decompresses a refrigerant.
  • the heat exchanger 10 may include a decompressing mechanism 25, which is an electromagnetic valve or the like, between the refrigerant channel (heat transfer channel portions 31U) in the airflow-upstream region WU and the refrigerant channel (heat transfer channel portions 31L) in the airflow-downstream region WL. Because the decompressing mechanism 25 expands the refrigerant F, the refrigerant temperature in the airflow-upstream region can be optimized. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7°C or lower), occurrence of frosting can be further suppressed.
  • a heat exchanger 10 according to the present embodiment is not limited to the configuration described above. That is, the heat exchanger 10 according to the present embodiment may have any configuration in which the refrigerant channel is folded back at least once in the second direction D2 in which airflow W is generated.
  • a heat exchanger 10Y having a refrigerant channel as illustrated in Fig. 13 may be used.
  • Fig. 13 is a schematic view for describing the refrigerant channel formed in the heat exchanger 10Y.
  • a partition member 22ps is provided inside of the airflow-upstream second header 22U in the second direction D2.
  • the airflow-upstream second header 22U is partitioned into two regions, which are an airflow-upstream upstream second header 22UA and an airflow-upstream downstream second header 22UB.
  • a partition member 21p and the like are disposed inside of the first header 21, and the first header 21 is partitioned into an airflow-upstream first header 21U and an airflow-downstream first header 21L in the second direction D2.
  • a refrigerant F that has flowed into the airflow-upstream upstream second header 22UA from the second pipe 42 flows into the airflow-upstream first header 21U through the heat transfer channel portions in the airflow-upstream upstream region.
  • the refrigerant F flows into the heat transfer channel portions in the airflow-upstream downstream region via the airflow-upstream first header 21U.
  • the refrigerant that has flowed into the airflow-upstream downstream second header 22UB flows into the airflow-downstream second header 22L via a connection pipe and the like (not shown).
  • the refrigerant F that has flowed into the airflow-downstream second header 22L flows into the first pipe 41 via the airflow-downstream first header 21L.
  • the first pipe 41 is connected to the airflow-downstream first header 21L.
  • a heat insulator I when seen in the first direction D1, a heat insulator I may be applied to an end portion of the heat transfer unit 30 on the airflow-upstream side in the second direction D2 (here, the auxiliary heat transfer portion 32g) (see Figs. 14 and 15 ).
  • the auxiliary heat transfer portion 32g decrease of temperature at the end portion can be suppressed.
  • the heat exchanger 10 when used as an evaporator in a low temperature environment (for example, 7°C or lower), frosting can be suppressed, and blockage of the air passage can be avoided or retarded.
  • the end portion of the heat transfer unit 30 is the auxiliary heat transfer portion 32g.
  • the auxiliary heat transfer portion 32g on the most airflow-upstream side (first auxiliary heat transfer portion) has a closed shape.
  • the term "closed shape” refers to a flat shape without a hole or a cutout.
  • auxiliary heat transfer portion 32g water generated by defrosting may be retained in the hole, the cutout, or the like. In this case, next frosting may spread from a portion where water is retained.
  • the heat exchanger 10 according to the modification C because the auxiliary heat transfer portion 32g has a shape without a hole, a cutout, or the like, occurrence of frosting after a defrosting operation can be suppressed.
  • the heat transfer channel portion 31 is not limited to the one described above, and may have another configuration.
  • the cross-sectional shape of the heat transfer channel portions 31 when seen in the first direction D1 may be any of: a semicircular shape, an elliptical shape, a flat shape, a shape like an upper half of an airfoil, and/or a shape like a lower half of an airfoil; or any combination of these.
  • the heat exchanger 10 may have any shape that optimizes heat exchange performance.
  • the heat transfer unit group 15 may have a configuration as illustrated in Figs. 16 and 17.
  • Fig. 17 is a partial enlarged view of Fig. 16 (corresponding to a dotted-line part of Fig. 16 ).
  • the heat transfer unit 30 (including 30a, 30b, and 30c) includes a first bulging portion 31p (including 31pa, 31pb, and 31pc) that bulges at a first position L1 (including L1a, L1b, and L1c) in the second direction D2 and forms the heat transfer channel portion 31, and a first flat surface portion 31q (including 31qa, 31qb, and 31qc) that is formed at the first position L1 so as to face in a direction opposite from the direction in which the first bulging portion 31p is formed.
  • the "first position" is defined for each heat transfer unit, and the first position L1a of the heat transfer unit 30a and the first positions L1b and L1c of the heat transfer units 30b and 30c are different positions.
  • At least one heat transfer unit 30a is disposed in a direction such that, with respect to a heat transfer unit 30b adjacent on one side, a surface on which the first bulging portion 31pa is formed and a surface of the adjacent heat transfer unit 30b on which the first bulging portion 31pb is formed face each other.
  • the heat transfer unit 30a is disposed in a direction such that, with respect to the heat transfer unit 30c adjacent on the other side, a surface on which the first flat surface portion 31qa is formed and a surface of the other heat transfer unit 30c on which the first flat surface portion 31qc is formed face each other.
  • the first positions L1a and L1b of the adjacent heat transfer units 30a and 30b are arranged so as not to overlap.
  • the first bulging portions 31 pa and 30pb are arranged in a staggered pattern. Therefore, the channel cross-sectional area of the air passage between the adjacent heat transfer units 31a and 31b can be increased, compared with a configuration in which the bulging portions are disposed close to each other as illustrated in Fig. 7 . Accordingly, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7°C or lower), blockage of the air passage due to frosting can be further suppressed.
  • a low temperature environment for example, 7°C or lower
  • the heat transfer unit 30 may have a second bulging portion that bulges to a smaller degree than the first bulging portion 31p, instead of the first flat surface portion 31q.
  • the heat transfer unit group 15 may have a configuration as illustrated in Figs. 18 and 19.
  • Fig. 19 is a partial enlarged view of Fig. 18 (corresponding to a dotted-line part of Fig. 18 ).
  • the heat transfer unit 30 includes: a first bulging portion 31p (including 31pa, 31pb, and 31pc) that bulges at a first position L1 (including L1a, L1b, and L1c) in the second direction D2 and forms the heat transfer channel portion 31; a first flat surface portion 31q (including 31qa, 31qb, and 31qc) that is formed at the first position L1 so as to face in a direction opposite from the direction in which the first bulging portion 31p is formed; a third bulging portion 31r (including 31ra, 31rb, and 31rc) that bulges at a second position L2 (including L2a, L2b, and L2c) in the second direction D2 so as to face in a direction opposite from the direction in which the first bulging portion 31p is formed, and that forms the heat transfer channel portion 31; and a second flat surface portion 31s (including 31s
  • At least one heat transfer unit 30a is disposed in a direction such that, with respect to a heat transfer unit 30b adjacent on one side, a surface on which the first bulging portion 31pa is formed and a surface of the adjacent heat transfer unit 30b on which the first flat portion 31qb is formed face each other.
  • the heat transfer unit 30a is disposed in a direction such that, with respect to the heat transfer unit 30c adjacent on the other side, a surface on which the third bulging portion 31ra is formed and a surface of the other adjacent heat transfer unit 30c on which the second flat surface portion 30sc is formed face each other.
  • first positions L1a and L1b (or L1a and L1c) in the adjacent heat transfer units 30a and 30b (or 30a and 30c) are arranged so as to overlap when seen in the first direction D1.
  • the second positions L2a and L2b (or L2a and L2c) are arranged so as to overlap when seen in the first direction D1.
  • first position L1" and the "second position L2" are defined for each heat transfer unit, here, these positions are the same in the heat transfer units 30a, 30b, and 30c.
  • the first bulging portions 31pa and 31pb and the like do not face each other, but are formed in opposite directions. Therefore, compared with a configuration in which the first bulging portions 31pa and 31pb and the like face each other, occurrence of contraction can be suppressed. As a result, it is possible to suppress increase of airflow resistance, and to realize optimal heat exchange performance.
  • the heat exchanger 10 having a configuration described above when used as an evaporator (for example, 7°C or lower), local frosting can be suppressed, compared with a heat exchanger in which substantially the same bulging portions are formed on both sides of the heat transfer units as illustrated in Fig. 7 .
  • the heat transfer unit 30 may have a second bulging portion that bulges to a smaller degree than the first bulging portion 31p, instead of the first flat surface portion 31q, and may have a fourth bulging portion that bulges to a smaller degree than the third bulging portion 31r, instead of the second flat surface portion 31s.
  • an auxiliary heat transfer portion 32g (first auxiliary heat transfer portion) that is longer than the other auxiliary heat transfer portions 32 may be formed at an end portion of the heat transfer unit 30 in the second direction D2.
  • the distance between the heat transfer channel portion 31g on the most airflow-upstream side and an adjacent auxiliary heat transfer portion 32g is large, the amount of heat transferred from the heat transfer channel portion 31g on the most airflow-upstream side to the auxiliary heat transfer portion 32g can be reduced.
  • heat flux distribution on the surface of the heat transfer unit 30 can be made uniform.
  • the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7°C or lower), local occurrence of frosting at an inlet portion of the air passage can be suppressed or avoided.
  • end portions of adjacent heat transfer units 30 may be arranged in a staggered pattern so that the lengths of the auxiliary heat transfer portions 32g in the second direction D2 differ from each other between the adjacent heat transfer units 30.
  • a portion having a large area is formed at an inlet portion of the air passage. Accordingly, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7°C or lower), frosting at the inlet portion of the air passage can be suppressed or avoided.
  • the heat transfer unit 30 when seen in the first direction D1, the heat transfer unit 30 may be processed so as to have a wave-like shape in addition to a linear shape.
  • the heat transfer unit 30 has a linear shape, air passage resistance can be suppressed.
  • the heat transfer units 30 has a wave-like shape, heat exchange amount between airflow and a refrigerant can be increased. In short, it is possible to provide a heat exchanger having optimal heat exchange performance in accordance with a use environment.
  • the heat exchanger 10 according to the present embodiment can be applied to a vessel heat exchanger (small-diameter multi-pipe heat exchanger) in which heat transfer tubes and fins are arranged in one direction although it is not limited to this configuration.
  • a vessel heat exchanger small-diameter multi-pipe heat exchanger
  • heat transfer tubes and fins are arranged in one direction although it is not limited to this configuration.
  • a microchannel heat exchanger flat multi-hole-pipe heat exchanger
  • the present disclosure may be modified into various disclosures by using appropriate combinations of a plurality of constituent elements disclosed in the embodiments. For example, from all of the constituent elements of the embodiments, some constituent elements may be omitted. Moreover, constituent elements of different embodiments may be combined as appropriate.

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

Claims (7)

  1. Climatiseur, comprenant :
    un échangeur de chaleur (10) comprenant une pluralité d'unités de transfert de chaleur (30) disposées dans une troisième direction (D3) différente d'une première direction (D1) et d'une deuxième direction (D2), la deuxième direction croisant la première direction ou étant perpendiculaire à celle-ci ; et
    un ventilateur (6) prévu pour générer un flux d'air (W) s'écoulant dans la deuxième direction et passant par des espaces entre les unités de transfert de chaleur,
    où
    les unités de transfert de chaleur sont divisées chacune en une zone d'amont du flux d'air (WU) et une zone d'aval du flux d'air (WL) dans la deuxième direction,
    caractérisé en ce que :
    dans chacune des unités de transfert de chaleur, une pluralité de sections de canal de transfert de chaleur (31) et une pluralité de sections de transfert de chaleur auxiliaires (32) sont formées, chacune des sections de canal de transfert de chaleur (31) s'étendant dans la première direction, chacune des sections de transfert de chaleur auxiliaires (32) s'étendant dans la première direction, les sections de canal de transfert de chaleur (31) étant disposées dans la deuxième direction, les sections de transfert de chaleur auxiliaires (32) étant disposées dans la deuxième direction ;
    quand il est mis en service comme évaporateur, l'échangeur de chaleur est prévu pour entraîner l'écoulement d'un réfrigérant dans les sections de canal de transfert de chaleur (31U) disposées dans la zone d'amont du flux d'air, puis entraîner l'écoulement du réfrigérant vers les sections de canal de transfert de chaleur (31L) disposées dans la zone d'aval du flux d'air ; et le nombre des sections de canal de transfert de chaleur disposées dans la zone d'aval du flux d'air est supérieur au nombre des sections de canal de transfert de chaleur disposées dans la zone d'amont du flux d'air.
  2. Climatiseur selon la revendication 1, comprenant en outre :
    un mécanisme de détente (25) prévu pour détendre le réfrigérant, ledit climatiseur étant prévu pour entraîner l'écoulement du réfrigérant de la section de canal de transfert de chaleur disposée dans la zone d'amont du flux d'air vers la section de canal de transfert de chaleur disposée dans la zone d'aval du flux d'air via le mécanisme de détente.
  3. Climatiseur selon la revendication 1 ou la revendication 2, comprenant en outre :
    un collecteur supérieur (21) et un collecteur inférieur (22) reliés aux unités de transfert de chaleur par le haut et le bas dans la première direction et formant une partie d'un canal de réfrigérant.
  4. Climatiseur selon la revendication 3,
    où la zone d'amont du flux d'air et la zone d'aval du flux d'air sont formées par un élément de cloisonnement (21p, 22p) disposé à l'intérieur du collecteur supérieur et/ou du collecteur inférieur.
  5. Climatiseur selon l'une des revendications 1 à 4,
    où chacune des unités de transfert de chaleur comprend au moins huit sections de canal de transfert de chaleur, et où au moins deux des sections de canal de transfert de chaleur sont disposées dans la zone d'amont du flux d'air.
  6. Climatiseur selon l'une des revendications 1 à 5, où, en vue dans la première direction, un isolant thermique (I) est appliqué à une partie d'extrémité de chacune des unités de transfert de chaleur dans la deuxième direction.
  7. Climatiseur selon la revendication 6,
    où, dans chacune des unités de transfert de chaleur, une première section de transfert de chaleur auxiliaire (32g) étant une des sections de transfert de chaleur auxiliaires est formée à une partie d'extrémité dans la deuxième direction en vue dans la première direction, et
    où la première section de transfert de chaleur auxiliaire a une forme fermée.
EP19761287.2A 2018-03-01 2019-02-22 Appareil de conditionnement d'air Active EP3760957B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018036981A JP7406297B2 (ja) 2018-03-01 2018-03-01 熱交換器
PCT/JP2019/006840 WO2019167839A1 (fr) 2018-03-01 2019-02-22 Échangeur de chaleur

Publications (3)

Publication Number Publication Date
EP3760957A1 EP3760957A1 (fr) 2021-01-06
EP3760957A4 EP3760957A4 (fr) 2021-04-21
EP3760957B1 true EP3760957B1 (fr) 2022-11-30

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US (1) US20210003350A1 (fr)
EP (1) EP3760957B1 (fr)
JP (1) JP7406297B2 (fr)
CN (1) CN111801541A (fr)
WO (1) WO2019167839A1 (fr)

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59153493U (ja) * 1983-03-31 1984-10-15 三菱重工業株式会社 熱交換器
JPH06117790A (ja) * 1992-10-06 1994-04-28 Sanden Corp 熱交換器
JPH07305986A (ja) * 1994-05-16 1995-11-21 Sanden Corp 多管式熱交換器
JPH09159386A (ja) * 1995-12-13 1997-06-20 Sanden Corp 多管式熱交換器
JPH10300275A (ja) * 1997-04-25 1998-11-13 Daikin Ind Ltd 空調室外機
JP2001091101A (ja) * 1999-09-20 2001-04-06 Fujitsu General Ltd 空気調和機の熱交換器
JP2006090636A (ja) 2004-09-24 2006-04-06 Daikin Ind Ltd 細径多管式熱交換器の細径伝熱管ユニット
JP2006322698A (ja) * 2005-04-22 2006-11-30 Denso Corp 熱交換器
JP2010117091A (ja) * 2008-11-13 2010-05-27 Denso Corp 熱交換器
JP5513093B2 (ja) * 2009-12-11 2014-06-04 東芝キヤリア株式会社 熱交換器、冷凍サイクル装置
JP5920178B2 (ja) * 2011-12-05 2016-05-18 株式会社デンソー ヒートポンプサイクル
JP2014137172A (ja) * 2013-01-16 2014-07-28 Daikin Ind Ltd 熱交換器及び冷凍装置
JP2014137177A (ja) 2013-01-16 2014-07-28 Daikin Ind Ltd 熱交換器および冷凍装置
WO2016013100A1 (fr) * 2014-07-25 2016-01-28 三菱電機株式会社 Échangeur de chaleur et appareil de climatisation et de réfrigération muni d'un échangeur de chaleur
JP6387858B2 (ja) 2015-02-26 2018-09-12 株式会社デンソー 冷媒熱交換器
CN205505498U (zh) * 2015-09-15 2016-08-24 北京旭日双圆制冷设备有限公司 高效节能多通道温度交换器
EP3477227B1 (fr) * 2016-06-24 2020-12-23 Mitsubishi Electric Corporation Dispositif à cycle de réfrigération et échangeur de chaleur extérieur utilisé dans celui-ci

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CN111801541A (zh) 2020-10-20
US20210003350A1 (en) 2021-01-07
EP3760957A1 (fr) 2021-01-06
EP3760957A4 (fr) 2021-04-21
JP2019152362A (ja) 2019-09-12
JP7406297B2 (ja) 2023-12-27
WO2019167839A1 (fr) 2019-09-06

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