EP3156752B1 - Échangeur thermique - Google Patents

Échangeur thermique Download PDF

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Publication number
EP3156752B1
EP3156752B1 EP14894720.3A EP14894720A EP3156752B1 EP 3156752 B1 EP3156752 B1 EP 3156752B1 EP 14894720 A EP14894720 A EP 14894720A EP 3156752 B1 EP3156752 B1 EP 3156752B1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
fins
flat pipes
heat transfer
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
EP14894720.3A
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German (de)
English (en)
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EP3156752A4 (fr
EP3156752A1 (fr
Inventor
Yuki UGAJIN
Takashi Okazaki
Akira Ishibashi
Atsushi Mochizuki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP3156752A1 publication Critical patent/EP3156752A1/fr
Publication of EP3156752A4 publication Critical patent/EP3156752A4/fr
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Publication of EP3156752B1 publication Critical patent/EP3156752B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F2009/0285—Other particular headers or end plates
    • F28F2009/029—Other particular headers or end plates with increasing or decreasing cross-section, e.g. having conical shape

Definitions

  • the present invention relates to a heat exchanger in which lower ends of a plurality of heat transfer pipes disposed in parallel with spaces therebetween and extending in a vertical direction are connected by a distribution header for distributing a refrigerant.
  • JP2013126817 proposes a cooling unit of an air conditioner for a vehicle.
  • JP2006170601 proposes an evaporator for an air conditioning unit.
  • JP2009299963 proposes a heat exchanger with header pipes arranged in parallel.
  • JPS6189449 proposes an air-cooled heat pump type refrigeration cycle.
  • US 2004/0016535 proposes a heat exchanger for cooling air.
  • KR20100073217 proposes an inner partition type oil cooler.
  • JPH11108583 proposes an evaporator for an air conditioning unit.
  • EP0325844 proposes an evaporator with improved condensate collection.
  • a problem that the heat exchanger described above faces is that, in a case where frost formed on the flat pipes and corrugated fins flows down to the top surfaces of the distribution headers, the overall circular arc cross-sectional shape of this top surface where the middle portion thereof in the front-back direction is the highest portion and the sides of the same sag gradually from the highest portion toward the front and back, causes the drops of water flowing along the arc and the direction of the wind to confront each other, making it impossible to drain the water smoothly from the distribution headers.
  • the present invention aims to solve such problem and an object thereof is to provide a heat exchanger that has a simple structure and the improved drainage capability of the distribution header and thereby prevents frosting.
  • a heat exchanger has: a plurality of heat transfer pipes that are disposed in parallel with spaces therebetween; distribution headers that are respectively connected to each of lower ends of the plurality of heat transfer pipes so as to communicate with the heat transfer pipes and distributes a refrigerant; and a plurality of fins that are provided in an air duct between the heat transfer pipes adjacent to each other, wherein the distribution headers have upper surfaces inclined downward from a windward side to a leeward side, and are arranged at least in two rows, with a space therebetween, toward a direction of wind, and opposing surfaces of the distribution headers that face each other are inclined surfaces that are configured such that a distance therebetween increases toward a lower side.
  • each distribution header is inclined downward from the windward side to the leeward side, gravity and the force of the wind can facilitate downward flow of drops of water on the top surface, improving the drainage capability of the distribution headers and anti-frosting performance of the distribution headers themselves.
  • Fig. 1 is a circuit diagram showing an air conditioner 51 incorporated with a heat exchanger 1.
  • Fig. 1 the solid arrows each show how a refrigerant flows during a cooling operation, the dotted lines each show how the refrigerant flows during a heating operation, and the chain arrows each show how the refrigerant flows during a defrosting operation.
  • the air conditioner 51 has a compressor 52, a four-way valve 53 connected to the compressor 52 by a first solenoid valve 60A, a throttle device 55 connected by a first solenoid valve 60C, a heat source-side heat exchanger 54 connected to the four-way valve 53 by a first solenoid valve 60B, the throttle device 55 connected to the heat source-side heat exchanger 54 by the first solenoid valve 60C, and a load-side heat exchanger 56 having one side connected to the throttle device 55 and the other side connected to the four-way valve 53.
  • the air conditioner 51 also has a heat source-side fan 57 facing the heat source-side heat exchanger 54, a load-side fan 58 facing the load-side heat exchanger 56, a second solenoid valve 61, and a controller 59.
  • the compressor 52, four-way valve 53, heat source-side heat exchanger 54, throttle device 55, and load-side heat exchanger 56 are connected to one another by refrigerant piping, configuring a refrigerant circulation circuit.
  • the compressor 52, four-way valve 53, throttle device 55, heat source-side fan 57, load-side fan 58, first solenoid valves 60A to C, second solenoid valve 61, and various other sensors are connected to the controller 59.
  • the controller 59 switches a flow channel of the four-way valve 53, thereby switching between the cooling operation and the heating operation.
  • the heat source-side heat exchanger 54 acts as a condenser in the cooling operation and as an evaporator in the heating operation.
  • the load-side heat exchanger 56 acts as an evaporator in the cooling operation and as a condenser in the heating operation.
  • the first solenoid valves 60A to C are opened during the cooling operation and the heating operation but are closed during the defrosting operation.
  • the second solenoid valve 61 is closed during the cooling operation and the heating operation but is opened during the defrosting operation.
  • the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the heat source-side heat exchanger 54 through the first solenoid valve 60A, four-way valve 53 and first solenoid valve 60B, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54.
  • the low-pressure gaseous refrigerant that flows out of the load-side heat exchanger 56 is suctioned by the compressor 52 through the four-way valve 53.
  • the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the load-side heat exchanger 56 through the first solenoid valve 60A and four-way valve 53, turns into a high-pressure liquid refrigerant by being condensed through heat exchange with the indoor air supplied by the load-side fan 58, and flows out of the load-side heat exchanger 56.
  • the high-pressure liquid refrigerant that flows out of the load-side heat exchanger 56 flows into the throttle device 55 and becomes a low-pressure gas-liquid two-phase refrigerant.
  • the low-pressure gas-liquid two-phase refrigerant that flows out of the throttle device 55 flows into the heat source-side heat exchanger 54 through the first solenoid valve 60C, turns into a low-pressure gaseous refrigerant by being vaporized through heat exchange with the outside air supplied by the heat source-side fan 57, and flows out of the heat source-side heat exchanger 54.
  • the low-pressure gaseous refrigerant that flows out of the heat source-side heat exchanger 54 is suctioned by the compressor 52 through the first solenoid valve 60B and four-way valve 53.
  • the refrigerant in a state of a high pressure and high temperature gas that is discharged from the compressor 52 flows into the heat source-side heat exchanger 54 through the second solenoid valve 61, turns into a gas-liquid two-phase or gaseous refrigerant by being subjected to heat exchange while melting frost adhering to the heat source-side heat exchanger 54, and flows out of the heat source-side heat exchanger 54.
  • the high-pressure gas-liquid two-phase or gaseous refrigerant that flows out of the heat source-side heat exchanger 54 flows into the throttle device 55 and becomes a low-pressure gas-liquid two-phase or gaseous refrigerant.
  • the low-pressure gas-liquid two-phase or gaseous refrigerant that flows out of the throttle device 55 passes through the load-side heat exchanger 56.
  • the low-pressure gas-liquid two-phase or gaseous refrigerant that passes through the load-side heat exchanger 56 is suctioned by the compressor 52 through the four-way valve 53.
  • the air conditioner performs defrosting in the direction of the flow of the refrigeration in the cooling operation, and thus it takes a while to defrost a section where frost grows.
  • the high-temperature gas can be caused to flow from the section where frost grows, improving the defrosting efficiency and consequently reducing the defrosting time.
  • Fig. 2 is a diagram in which the heat exchanger 1 is the heat source-side heat exchanger 54 shown in Fig. 1 , is viewed from the windward side.
  • Fig. 3 is a perspective view of main portions, showing the heat exchanger 1 shown in Fig. 2 in a design which is not subject of this invention.
  • Fig. 4 is a diagram showing internal configurations of distribution headers 2, 7 shown in Fig. 3 .
  • Fig. 5 is a flat cross-sectional diagram showing a folded-back header shown in Fig. 2 . Note that Fig. 3 only shows corrugated fins 5 held between a pair of flat pipes 4 and corrugated fins 5 held between a pair of flat pipes 6 and does not show the other flat pipes 4, 6 and corrugated fins 5 that are arranged in parallel.
  • This heat exchanger 1 has a first distribution header 2 that is disposed in a direction perpendicular to the direction of the wind shown by the arrow C when seen in the vertical direction, a second distribution header 7 provided in parallel with the first distribution header 2, a plurality of first flat pipes 4, which are first heat transfer pipes that have lower ends connected to the first distribution header 2, have upper ends extending vertically, and are disposed at equal intervals, a folded-back header 3 that is provided in such a manner as to face the first distribution header 2 and the second distribution header 7 and has an upper portion of each of the first flat pipes 4 connected thereto, a plurality of second flat pipes 6, which are second heat transfer pipes that have upper ends connected to this folded-back header 3, have lower ends connected to the second distribution header 7, and are disposed at equal intervals, and the corrugated fins 5 that are provided in an air duct between the first flat pipes 4 adjacent to each other and an air duct between the second flat pipes 6 adjacent to each other.
  • the first distribution header 2 and the second distribution header 7 are in the same shape and have a rectangular cross section.
  • the first distribution header 2 has a refrigerant inflow portion 2A extending in a horizontal direction, to which the refrigerant flows in.
  • the refrigerant piping is connected to this refrigerant inflow portion 2A.
  • the first distribution header 2 is also provided with a distribution pipe 2B that extends internally in the horizontal direction. A tip end of the refrigerant inflow portion 2A is connected vertically to this distribution pipe 2B.
  • the hollow second distribution header 7 has a refrigerant outflow portion 7A extending in the horizontal direction, of which the refrigerant flows out.
  • the refrigerant piping is connected to this refrigerant outflow portion 7A.
  • a plurality of holes into which the lower ends of the first flat pipes 4 are inserted are formed in the first distribution header 2.
  • a plurality of holes into which the lower ends of the second flat pipes 6 are inserted are formed in the second distribution header 7.
  • the first distribution header 2 and the second distribution header 7 have, respectively, inclined surfaces 10, 11 having top surfaces thereof inclined downward from the windward side to the leeward side.
  • the starting points of the inclined surfaces 10, 11 are located higher than upper connecting points of the first flat pipes 4 extending vertically from the first distribution header 2.
  • a partition plate may be provided on the inside of each of the distribution headers 2, 7 in order to adjust the distribution ratio of each of the first and second flat pipes 4, 6.
  • first flat pipes 4 and second flat pipes 6 Holes into which the upper ends of the first flat pipes 4 and second flat pipes 6 are inserted are formed in the folded-back header 3.
  • the first flat pipes 4 and the second flat pipes 6 face each other in a longitudinal direction.
  • a partition wall 8 is provided between a pair of first and second flat pipes 4 and 6 and a pair of first and second flat pipes 4 and 6 adjacent thereto. This partition wall 8 regulates the refrigerant to flow in the direction of the arrow A shown in Fig. 5 .
  • the first distribution header 2, folded-back header 3, second distribution header 7, first flat pipes 4, second flat pipes 6, corrugated fins 5, and distribution pipe 2B are made of, for example, aluminum.
  • the refrigerant inflow portion 2A and the refrigerant outflow portion 7A may be provided in plurality.
  • the first flat pipes 4 and the second flat pipes 6 are flat pipes that internally have a plurality of flow channels 4a, 6a extending individually in the vertical direction.
  • the longitudinal direction of these rectangular first flat pipes 4 and second flat pipes 6 are the vertical direction, and the short direction thereof are positioned along the direction of the wind.
  • the corrugated fins 5 and the first flat pipes 4 are preferably joined together by brazing, as well as the corrugated fins 5 and the second flat pipes 6. It should be noted that, needless to say, the number of first flat pipes 4 and the number of second flat pipes 6 are not limited to the numbers shown in Fig. 2 .
  • the refrigerant flowing through the refrigerant piping flows into the first distribution header 2 through the refrigerant inflow portion 2A, is then distributed, and then flows upward through each of the flow channels 4a of the plurality of first flat pipes 4 from the lower ends of the first flat pipes 4. While flowing through the first flat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through the corrugated fins 5 by the fans.
  • the refrigerant that is circulated through the first flat pipes 4 reaches the folded-back header 3, turns back at the folded-back header 3, and flows down each of the flow channels 6a of the second flat pipes 6. While flowing through the first flat pipes 4, this refrigerant is subjected to heat exchange with air that is circulated through the corrugated fins 5 by the fans.
  • the refrigerant that flows down each of the second flat pipes 6 joins at the second distribution header 7 and flows out to the refrigerant piping through the refrigerant outflow portion 7A.
  • the direction of the flow of the refrigerant can be reversed.
  • Fig. 7 is a perspective view of main portions, showing a modification of the heat exchanger 1 according to a design which is not subject of this invention.
  • the inclined surfaces 10, 11 are in the shape of an arc, sagging from the windward side to the leeward side.
  • the starting point of the inclined surface 10 is located higher than the upper connecting points of the first flat pipes 4 extending vertically from the first distribution header 2.
  • the starting point of the inclined surface 11 is located higher than the upper connecting points of the second flat pipes 6 extending vertically from the second distribution header 7.
  • the drops of water 12 drained into the first distribution header 2 and the second distribution header 7 flow in the direction of gravity due to the inclination of the inclined surfaces 10, 11.
  • the inclined surfaces 10, 11 at the top surfaces of the distribution headers 2, 7 have a streamlined shape, the wind flowing through the heat exchanger 1 flows along the distribution headers 2, 7 more as compared to a linear-shaped inclined surface, and thus, the gravity and the force of the wind facilitate the flow of the drops of water 12.
  • Fig. 8 is a perspective view of main portions, showing the heat exchanger 1 according to Embodiment 1 of the present invention.
  • the inclined surfaces 10, 11 at the top surfaces are in the same shape as those shown in Fig. 3 ; however it differs therefrom in that the surface of the first distribution header 2 and the surface of the second distribution header 7 that face each other have inclined surfaces 13, 14, respectively, which are configured such that a distance therebetween increases as the inclined surfaces 13, 14 incline downward.
  • each first distribution header 2 and each second distribution header 7 needs to be reduced due to limitations in installation space.
  • the first distribution header 2 and the second distribution header 7 have, on the surfaces thereof facing each other, the inclined surfaces 13, 14 that are inclined vertically, wherein the distance between the inclined surfaces 13, 14 increases gradually toward the lower side thereof.
  • the drops of water 12 do not bridge the space between the first distribution header 2 and the second distribution header 7 easily, improving anti-frosting performance of the first distribution header 2 and the second distribution header 7.
  • Fig. 10 is a perspective view showing main portions of a heat exchanger in a design which is not subject of this invention.
  • front edge portions of the corrugated fins 5 protrude toward the windward side from the windward end surfaces of the first flat pipes 4 and second flat pipes 6.
  • corrugated fins 5 are inclined gradually downward from the windward side toward the leeward side.
  • the downward inclination of the corrugated fins 5 from the windward side to the leeward side enables drainage of water using both the gravity and the force of the wind, further improving the drainage capability of the corrugated fins 5.
  • Fig. 11 is a side view showing main portions of a heat exchanger 1 in a design which is not subject of this invention.
  • the both sides of the fins 5 are brazed by the flat pipes 4, 6 at joint portions 15 and inclined downward from the windward side to the leeward side.
  • drainage grooves 9, which are inclined along the joint portions 15 between the flat pipes 4, 6 and the corrugated fins 5 and extend linearly, are formed in the flat pipes 4, 6.
  • drops of water 12 are transferred from the corrugated fins 5 to the first flat pipes 4 and the second flat pipes 6 and pool in the drainage grooves 9 due to gravity.
  • the drops of water 12 pooling in the drainage grooves 9 are pushed out by both the gravity and the force of the wind, improving the drainage capability of the first flat pipes 4 and second flat pipes 6.
  • the heat exchanger is used in the air conditioner; however, needless to say, the applications of the heat exchanger are not limited to an air conditioner.
  • the heat exchanger may be used in other refrigeration cycle devices having a refrigerant circulation circuit.
  • corrugated fins 5 are merely an example; thus, the shape of the fins does not have to be corrugated.
  • the first flat pipes 4 and the second flat pipes 6, too, are merely an example; thus, the shape of the pipes does not have to be flat.

Claims (9)

  1. Echangeur de chaleur (1), comprenant :
    une pluralité de tuyaux de transfert de chaleur (4, 6) qui sont disposés en parallèle avec des espaces entre eux ;
    des collecteurs de distribution (2, 7) qui sont connectés respectivement aux extrémités inférieures de la pluralité de tuyaux de transfert de chaleur (4, 6) de manière à communiquer avec les tuyaux de transfert de chaleur (4, 6) et à distribuer un réfrigérant ; et
    une pluralité d'ailettes (5) qui sont prévues dans un conduit d'air entre les tuyaux de transfert de chaleur (4, 6) adjacentes les unes aux autres,
    dans lequel les collecteurs de distribution (2, 7) ont des surfaces supérieures inclinées vers le bas depuis un côté au vent vers un côté sous le vent, et sont agencés au moins en deux rangées, avec un espace entre eux, vers une direction de vent, et caractérisé en ce que
    des surfaces opposées des collecteurs de distribution (2, 7) qui se font face mutuellement sont des surfaces inclinées qui sont configurées de telle sorte qu'une distance entre elles augmente vers un côté inférieur.
  2. Echangeur de chaleur (1) selon la revendication 1, dans lequel des surfaces inclinées (10, 11), qui sont les surfaces supérieures inclinées, ont chacune une forme d'arc faisant saillie vers le haut au niveau d'une partie médiane.
  3. Echangeur de chaleur (1) selon la revendication 1 ou 2, dans lequel des surfaces d'extrémité des ailettes (5) du côté au vent font saillie vers le côté au vent depuis des surfaces d'extrémité des tuyaux de transfert de chaleur (4, 6) du côté au vent.
  4. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 3, dans lequel les ailettes (5) sont prévues pour être inclinées vers le bas depuis le côté au vent vers le côté sous le vent.
  5. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 4, dans lequel des rainures (9) qui sont inclinées vers le bas du côté au vent vers le côté sous le vent sont formées sur des surfaces de parties de joint entre les tuyaux de transfert de chaleur (4, 6) et les ailettes (5) .
  6. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 5, dans lequel les tuyaux de transfert de chaleur (4, 6) sont des tuyaux plats (4, 6) qui ont une pluralité de canaux d'écoulement, et dont la direction longitudinale est une direction verticale.
  7. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 6, dans lequel les ailettes (5) sont des ailettes ondulées (5).
  8. Echangeur de chaleur côté source de chaleur pour un climatiseur (51) comprenant l'échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 7, dans lequel une direction d'écoulement du réfrigérant dans l'échangeur de chaleur côté source de chaleur (54) est la même pour un dégivrage et un chauffage.
  9. Echangeur de chaleur (1) selon l'une quelconque des revendications 1 à 8, dans lequel les surfaces opposées sont des surfaces inclinées (13, 14) qui sont inclinées verticalement de telle sorte que la distance entre les surfaces inclinées (13, 14) augmente graduellement vers le côté inférieur de celui-ci.
EP14894720.3A 2014-06-13 2014-06-13 Échangeur thermique Active EP3156752B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/065766 WO2015189990A1 (fr) 2014-06-13 2014-06-13 Échangeur thermique

Publications (3)

Publication Number Publication Date
EP3156752A1 EP3156752A1 (fr) 2017-04-19
EP3156752A4 EP3156752A4 (fr) 2018-02-21
EP3156752B1 true EP3156752B1 (fr) 2020-11-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP14894720.3A Active EP3156752B1 (fr) 2014-06-13 2014-06-13 Échangeur thermique

Country Status (3)

Country Link
EP (1) EP3156752B1 (fr)
JP (1) JP6300915B2 (fr)
WO (1) WO2015189990A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3805651B1 (fr) * 2018-06-11 2023-11-22 Mitsubishi Electric Corporation Unité extérieure de climatiseur et climatiseur associé

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018155479A (ja) * 2017-03-16 2018-10-04 ダイキン工業株式会社 伝熱管ユニットを有する熱交換器
WO2018168759A1 (fr) * 2017-03-16 2018-09-20 ダイキン工業株式会社 Échangeur de chaleur ayant une unité de tubes de transfert de chaleur
JP6717256B2 (ja) * 2017-05-10 2020-07-01 株式会社デンソー 冷媒蒸発器およびその製造方法
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EP3156752A1 (fr) 2017-04-19

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