EP4775920A1 - Indoor heat exchanger and air-conditioning indoor machine - Google Patents

Indoor heat exchanger and air-conditioning indoor machine

Info

Publication number
EP4775920A1
EP4775920A1 EP24871397.6A EP24871397A EP4775920A1 EP 4775920 A1 EP4775920 A1 EP 4775920A1 EP 24871397 A EP24871397 A EP 24871397A EP 4775920 A1 EP4775920 A1 EP 4775920A1
Authority
EP
European Patent Office
Prior art keywords
plate
heat exchanger
flow path
stack
plate portion
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.)
Pending
Application number
EP24871397.6A
Other languages
German (de)
French (fr)
Inventor
Shota AGO
Shutaro YAMAMOTO
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.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Publication of EP4775920A1 publication Critical patent/EP4775920A1/en
Pending legal-status Critical Current

Links

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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • 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
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes

Landscapes

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

Abstract

A plate stack (50, 60) of an indoor heat exchanger is adjacent to a heat exchange portion (B) in a first direction, and includes a first plate portion (50A, 60A) having one or more of plates (52, 62), and a second plate portion (50B, 60B) which has one or more of plates (52, 62) and which is disposed on a surface of the first plate portion (50A, 60A) that is opposite to a surface facing the heat exchange portion (B), the plate stack (50, 60) has a step portion (X) in a peripheral portion of a first surface (501, 601) facing the heat exchange portion (B), and the step portion (X) is formed by the first plate portion (50A, 60A) and the second plate portion (50B, 60B).

Description

    TECHNICAL FIELD
  • The present disclosure relates to an indoor heat exchanger and an air-conditioning indoor unit.
    • BACKGROUND ART
  • Patent Document 1 discloses a stacked header connected to a heat exchanger. Each plate of the stacked header has a groove. When the plates with such grooves are stacked, the grooves form a refrigerant flow path in the stacked header.
    • CITATION LIST PATENT DOCUMENT
  • Patent Document 1: WO 2014/184917
    • SUMMARY OF THE INVENTION TECHNICAL PROBLEM
  • The plates that form the plate stack are all formed in the same shape. The shape and position of the groove formed in the plate vary with the structure of the refrigerant flow path. Therefore, the area of the region in which the groove is not formed varies with the plate. The region in which the groove is not formed is useless, and therefore if the region is relatively large, the space in the air conditioner cannot be used effectively.
  • An object of the present disclosure is to provide an indoor heat exchanger with stacked plates that allow an effective use of a space in an air-conditioning unit.
    • SOLUTION TO THE PROBLEM
  • A first aspect is directed to an indoor heat exchanger including:
    • a heat exchange portion (B) including a plurality of fins (41) and a plurality of heat transfer tubes (42) penetrating the plurality of fins (41); and
    • a plate stack (50, 60) in which a flow path (51, 61) communicating with the heat transfer tube (42) is provided and in which a plurality of plates (52, 62) are stacked in a first direction in which the heat transfer tube (42) extends,
    • wherein
    • the plate stack (50, 60)
      • is adjacent to the heat exchange portion (B) in the first direction, and includes
      • a first plate portion (50A, 60A) having one or more of the plates (52, 62), and
      • a second plate portion (50B, 60B) which has one or more of the plates (52, 62) that is different in shape from the plates (52, 62) of the first plate portion (50A, 60A) and which is disposed on a surface of the first plate portion (50A, 60A) that is opposite to a surface facing the heat exchange portion (B),
    • the plate stack (50, 60) has a step portion (X) in a peripheral portion of a first surface (501, 601) facing the heat exchange portion (B), and
    • the step portion (X) is formed by the first plate portion (50A, 60A) and the second plate portion (50B, 60B).
  • In the first aspect, the step portion (X) is provided in the plate stack (50, 60), whereby it is possible to form a space at a position facing the step portion (X). It is possible to use this space effectively, such as disposing a predetermined component in this space.
  • A second aspect is an embodiment of the first embodiment. In the second aspect,
    • the plate stack (50, 60) has the plates (52, 62) including three or more plates (52, 62), and
    • in the plate stack (50, 60),
      • one of the plates (52, 62) of the first plate portion (50A, 60A) that is closest to the heat exchange portion (B) is defined as a first end plate (521),
      • one of the plates (52, 62) of the second plate portion (50B, 60B) that is most distant from the heat exchange portion (B) is defined as a second end plate (525), and
      • the plate (52, 62) disposed between the first end plate (521) and the second end plate (525) is defined as an intermediate plate (522 to 524),
    • the flow path (51, 61) runs through the intermediate plate (522 to 524, 622 to 624), and
    • a thickness of the intermediate plate (522 to 524) is greater than a thickness of the first end plate (521) and the second end plate (525).
  • In the second aspect, the thickness of the plate (52, 62) disposed at the center of the plate stack (50, 60) is greater than the thickness of the plate (52, 62) disposed at both the ends of the plate stack (50, 60), whereby it is possible to increase the area or the inner diameter of the cross section of the refrigerant flow path (51, 61) formed in the plate stack (50, 60). Accordingly, it is possible to reduce an increase in pressure loss of the refrigerant flowing through the refrigerant flow path (51, 61).
  • A third aspect is an embodiment of the first or second aspect. In the third aspect,
    in the plate stack (50, 60), at least part of the first surface (501, 601) and a second surface (502, 602) that is opposite to the first surface (501, 601) is subjected to anti-corrosion treatment.
  • In the third aspect, while both the side surfaces of the plate stack (50, 60) may be electrolytically corroded by dew condensation or others, it is possible to reduce such electrolytic corrosion by the anti-corrosion treatment.
  • A fourth aspect is an embodiment of any one of the first to third aspects. In the fourth aspect,
    when the plate stack (50, 60) is viewed from an opposite direction of the first direction, an area of part of the second plate portion (50B, 60B) that does not overlap with the first plate portion (50A, 60A) is smaller than an area of part of the second plate portion (50B, 60B) that overlaps with the first plate portion (50A, 60A).
  • Part of the plate stack (50, 60) in which the first plate portion (50A, 60A) and the second plate portion (50B, 60B) overlap with each other is thicker than part of the plate stack (50, 60) in which only the first plate portion (50A, 60A) is present, and therefore a larger number of flow paths (51, 61) can be formed. Accordingly, it is possible to increase the flow rate of the refrigerant flowing through the heat transfer tubes (42) of the heat exchange portion (B), and as a result, the heat exchange is promoted. In the fourth aspect, when the portion in which the front first plate portion (50A, 60A) and the front second plate portion (50B, 60B) overlap with each other is larger than the portion in which only the front first plate portion (50A, 60A) is present, it is possible to secure a sufficient number of flow paths in the front plate stack (50, 60), and therefore it is possible to promote the indoor heat exchanger exchanging heat between air and a refrigerant.
  • A fifth aspect is an embodiment of any one of the first to fourth aspects. In the fifth aspect,
    • the flow path (51, 61) includes
      • a first flow path (51A) provided in the first plate portion (50A, 60A), and
      • a second flow path (51B) provided between the first plate portion (50A, 60A) and the second plate portion (50B, 60B), and
    • the second flow path (51B) is formed to intersect the first flow path (51A).
  • In the fifth aspect, in part of the plate stack (50, 60) in which the flow paths (51, 61) do not intersect each other, only the first plate portion (50A, 60A) may be provided with the flow paths (51, 61). Such a part does not require the second plate portion (50B, 60B) and thus can be provided with the step portion (X). In this manner, it is possible to effectively use the space formed by the step portion (X).
  • A sixth aspect is an embodiment of any one of the first to fifth aspects. In the sixth aspect,
    • the heat exchange portion (B) includes a connection pipe (400) having a U-shape, disposed between the heat exchange portion (B) and the plate stack (50, 60), and connecting two of the heat transfer tubes (42), and
    • the connection pipe (400) is disposed at a position facing the step portion (X) when viewed from the opposite direction of the first direction.
  • It is necessary to form a gap between the heat exchange portion (B) and the plate stack (50, 60) into an enough size to dispose the U-shaped connection pipe (400), and in the sixth aspect, since the connection pipe (400) is disposed in the space formed by the step portion (X), the gap between the heat exchange portion (B) and the plate stack (50, 60) can be relatively small. Accordingly, it is possible to make the indoor heat exchanger compact.
  • A seventh aspect is an embodiment of the sixth aspect. In the seventh aspect, the inner heat exchanger further includes:
    • a detecting unit (70) configured to detect a temperature of a refrigerant flowing through the heat transfer tube (42),
    • wherein
    • the detecting unit (70) is provided in the connection pipe (400).
  • In the seventh aspect, it is possible to provide the detecting unit (70) by effectively using the space formed by the step portion (X).
  • An eighth aspect is an embodiment of the sixth or seventh aspect. In the eighth aspect,
    in the connection pipe (400),
    • a refrigerant in a superheated region flows if the indoor heat exchanger functions as an evaporator, and
    • a refrigerant in a supercooled region flows if the indoor heat exchanger functions as a radiator.
  • The temperature of the refrigerant in the superheated region is relatively high, and the temperature of the refrigerant in the supercooled region is relatively low. If there is another flow path near the flow path through which the refrigerant in the superheated region or the supercooled region flows, the refrigerant passing through the other flow path exchanges heat with the refrigerant passing through the superheated region or the supercooled region. To solve this problem, in the eighth aspect, the refrigerant in the superheated region or the supercooled region is allowed to flow through the connection pipe (400), whereby it is possible to reduce heat exchange with the refrigerant flowing through the flow path in the plate stack (50, 60).
  • A ninth aspect is directed to an air-conditioning indoor unit including:
    • the indoor heat exchanger of any one of the first to eighth aspects; and
    • a gas pipe (12a) configured to transfer compressed refrigerant gas to the indoor heat exchanger (40),
    • wherein
    • the gas pipe (12a) is connected to the flow path (51, 61) formed in part of the plate stack (50, 60) in which the first plate portion (50A, 60A) and the second plate portion (50B, 60B) overlap with each other.
  • In the ninth aspect, among the flow paths (51, 61) extending in the stacking direction of the plates (52, 62), the flow paths (51, 61) extending in the stacking direction of the first plate portion (50A, 60A) and the second plate portion (50B, 60B) is relatively long. Accordingly, by allowing the compressed gas refrigerant to flow through these flow paths (51,61), it is possible to reduce the pressure loss of the gas refrigerant passing through the flow path (51, 61).
    • BRIEF DESCRIPTION OF THE DRAWINGS
    • [FIG. 1] FIG. 1 is a piping system diagram of an air conditioner according to an embodiment.
    • [FIG. 2] FIG. 2 is a front view of an air-conditioning indoor unit.
    • [FIG. 3] FIG. 3 is a cross-sectional view of the air-conditioning indoor unit taken along line II-II.
    • [FIG. 4] FIG. 4 is a front view of an internal structure of the air-conditioning indoor unit.
    • [FIG. 5] FIG. 5 is an enlarged perspective view of a main part of an indoor heat exchanger.
    • [FIG. 6] FIG. 6 shows plate stacks as viewed from the left side.
    • [FIG. 7] FIG. 7 is a cross-sectional view that illustrates refrigerant flow paths of the plate stacks.
    • [FIG. 8] FIG. 8 is a schematic view of a front plate stack as viewed from the front.
    • [FIG. 9] FIG. 9 is a cross-sectional view of the front plate stack for describing a configuration of a first flow path.
    • [FIG. 10] FIG. 10 is a cross-sectional view of the front plate stack for describing a configuration of a second flow path.
    • [FIG. 11] FIG. 11 is a schematic view showing that the first flow path and the second flow path intersect each other when the plate stack is viewed from the first direction (the right direction).
    • [FIG. 12] FIG. 12A is a perspective view of a temperature sensor attached to a U-shaped connection pipe. FIG. 12B is a plan view of the temperature sensor attached to the U-shaped connection pipe.
    • [FIG. 13] FIG. 13 is a schematic view corresponding to FIG. 8 and showing an indoor heat exchanger according to a first variation.
    • [FIG. 14] FIG. 14 is a schematic view of a main part of an indoor heat exchanger as viewed from above according to a second variation.
    DESCRIPTION OF EMBODIMENTS
  • An embodiment of the present disclosure will be described in detail below with reference to the drawings. The present disclosure is not limited to the embodiment shown below, and various changes can be made within the scope without departing from the technical concept of the present disclosure. Since each of the drawings is intended to illustrate the present disclosure conceptually, dimensions, ratios, or numbers may be exaggerated or simplified as necessary for the sake of ease of understanding.
    • (1) General Configuration of Air Conditioner
  • The present embodiment is directed to an air conditioner (10) that includes a heat exchanger unit. The air conditioner (10) adjusts the temperature of air in an indoor space (I) as a target space.
  • As shown in FIG. 1, the air conditioner (10) is an example of a refrigeration cycle apparatus that includes a refrigerant circuit (11). The refrigerant circuit (11) is filled with a refrigerant. The refrigerant circuit (11) circulates a refrigerant to perform a refrigeration cycle.
  • The air conditioner (10) includes an air-conditioning outdoor unit (20), an air-conditioning indoor unit (30), a first connection pipe (12), and a second connection pipe (13). The air conditioner (10) is a pair-type air conditioner that includes one air-conditioning outdoor unit (20) and one air-conditioning indoor unit (30). The first connection pipe (12) is a gas connection pipe, and the second connection pipe (13) is a liquid connection pipe.
  • The air-conditioning outdoor unit (20) is placed outside. The air-conditioning outdoor unit (20) includes an outdoor casing (20a); and a compressor (21), an outdoor heat exchanger (22), an outdoor expansion valve (23), a four-way switching valve (24), and an outdoor fan (25) which are housed in the outdoor casing (20a).
  • The compressor (21) is a rotary compressor such as an oscillating-piston-type compressor, a rotary-type compressor, and a scroll-type compressor. The outdoor heat exchanger (22) exchanges heat between a refrigerant and outdoor air. The outdoor heat exchanger (22) is a fin-and-tube heat exchanger. The outdoor expansion valve (23) decompresses a refrigerant. The outdoor expansion valve (23) is an electronic expansion valve. The four-way switching valve (24) switches between a first state (the state indicated by the solid lines in FIG. 1) and a second state (the state indicated by the broken lines in FIG. 1). The four-way switching valve (24) in the first state allows a discharge portion of the compressor (21) and a gas end portion of the outdoor heat exchanger (22) to communicate with each other, and allows an inlet portion of the compressor (21) and the first connection pipe (12) to communicate with each other. The four-way switching valve (24) in the second state allows the discharge portion of the compressor (21) and the first connection pipe (12) to communicate with each other, and allows the inlet portion of the compressor (21) and the gas end portion of the outdoor heat exchanger (22) to communicate with each other. The outdoor fan (25) transfers air flowing through the outdoor heat exchanger (22). The outdoor fan (25) is a propeller fan.
  • The air-conditioning indoor unit (30) includes a casing (31); and an indoor heat exchanger (40), an indoor fan (32), and an indoor expansion valve (37) which are housed in the casing (31).
    • (2) Air-Conditioning Indoor Unit
  • The air-conditioning indoor unit (30) as an indoor air conditioner will be described in detail with reference to FIGS. 2 to 4. The air-conditioning indoor unit (30) of this embodiment is a wall-mounted unit provided on a wall of the indoor space (I). The terms "upper", "lower", "right", "left", "front", and "rear" described below correspond to the directions of the arrows shown in FIGS. 2 and 3, and the left-right direction refers to the direction in which the casing (31) is viewed from the front.
    • (2-1) Casing
  • As shown in FIG. 2 and FIG. 3, the casing (31) is formed in a box shape that extends in the left-right direction. The casing (31) includes a front panel (31a), a rear panel (31b), an upper panel (31c), a lower panel (31d), a first side panel (31e), and a second side panel (31f).
  • The front panel (31a) is on the front side of the casing (31) and constitutes a front surface of the casing (31). The rear panel (31b) is on the rear side of the casing (31) and constitutes a rear surface of the casing (31). The upper panel (31c) is on the upper side of the casing (31) and constitutes an upper surface of the casing (31). The lower panel (31d) is on the lower side of the casing (31) and constitutes a lower surface of the casing (31). The first side panel (31e) is on the right side of the casing (31) and constitutes a right surface of the casing (31). The second side panel (31f) is on the left side of the casing (31) and constitutes a left surface of the casing (31).
  • An inlet port (33) is formed in the upper panel (31c), and an outlet port (34) is formed in the lower panel (31d). In the casing (31), an air passage (P) is formed from the inlet port (33) to the outlet port (34). The inlet port (33) extends in the longitudinal direction of the casing (31). The inlet port (33) is an opening for sucking the air in the indoor space (I) into the air passage (P). The outlet port (34) is formed in the lower panel (31d). The outlet port (34) extends in the longitudinal direction of the casing (31). The outlet port (34) is an opening for discharging the air in the air passage (P) to the indoor space (I).
    • (2-2) Filter
  • The air-conditioning indoor unit (30) includes a filter (35). The filter (35) is disposed behind the inlet port (33) and upstream of the indoor heat exchanger (40). The filter (35) collects dust in the air sent from the inlet port (33) to the indoor heat exchanger (40). The air-conditioning indoor unit (30) may include a dust removal mechanism for removing the dust collected by the filter (35).
    • (2-3) Heat Exchanger Unit
  • The heat exchanger unit (U) includes one indoor heat exchanger (40) and one indoor expansion valve (37). The indoor heat exchanger (40) includes one heat exchanger body (B) and two plate stacks (50, 60). The heat exchanger body (B) of the indoor heat exchanger (40) is disposed to cross the air passage (P). The air passage (P) is divided into an upstream side and a downstream side of the heat exchanger body (B).
    • (2-4) Indoor Fan
  • The indoor fan (32) is disposed in the air passage (P). In the air passage (P), the indoor fan (32) is disposed downstream of the indoor heat exchanger (40). The indoor fan (32) is a cross-flow fan. The indoor fan (32) has a fan rotor that extends in the longitudinal direction of the casing (31).
    • (2-5) Flap
  • The air-conditioning indoor unit (30) has a flap (36) that adjusts the direction of the air discharged from the outlet port (34). The flap (36) adjusts the airflow direction in the top-bottom direction. The air-conditioning indoor unit (30) may have a plurality of flaps (36). The flap (36) may adjust the airflow direction in the left-right direction.
    • (3) Heat Exchanger Unit
  • As described above, the heat exchanger unit (U) includes the indoor heat exchanger (40), the indoor expansion valve (37), a gas relay pipe (12a), and a liquid relay pipe (13a).
    • (3-1) Indoor Heat Exchanger
  • The indoor heat exchanger (40) shown in FIGS. 3 to 5 includes the heat exchanger body (B) and the plate stacks (50, 60) connected with the heat exchanger body (B). The indoor heat exchanger (40) is a fin-and-tube heat exchanger having fins (41) and heat transfer tubes (42). The indoor heat exchanger (40) exchanges heat between air and a refrigerant.
  • The heat exchanger body (B) is an example of the heat exchange portion (B). The heat exchanger body (B) includes the plurality of fins (41) and the plurality of heat transfer tubes (42) penetrating the plurality of fins (41). The plurality of fins (41) are arranged in the longitudinal direction of the casing (31). The plurality of heat transfer tubes (42) extend in the direction in which the fins (41) are arranged. The plate stack (50, 60) contains a refrigerant flow path (51, 61) that communicates with the heat transfer tubes (42). The refrigerant flow path (51, 61) is an example of the flow path (51, 61).
  • The fin (41) has a rectangular plate shape having long sides and short sides. The thickness direction of the fins (41) corresponds to the arrangement direction of the fins (41). The plurality of fins (41) are arranged at predetermined intervals in the thickness direction. These intervals form air flow paths. The fin (41) is made of an aluminum alloy.
  • The heat transfer tubes (42) are straight tubes. The heat transfer tubes (42) are made of an aluminum alloy. Refrigerant flow paths are formed inside the heat transfer tubes (42). The plurality of heat transfer tubes (42) extend parallel to each other to penetrate the fins (41). A right end portion, which is one of the end portions, of the heat transfer tubes (42) protrudes to the right of the rightmost one of the fins (41). The end portion of the heat transfer tube that protrudes to the right is connected to the plate stack (50, 60).
  • Among the left end portions of the plurality of heat transfer tubes (42), the end portions of the heat transfer tubes (42) adjacent to each other are connected to each other by a U-shaped pipe (48). The two heat transfer tubes (42) adjacent to each other and the U-shaped pipe (48) connecting them are integrated together seamlessly.
  • The indoor heat exchanger (40) of this embodiment includes a front heat exchange portion (40A) and a rear heat exchange portion (40B). The front heat exchange portion (40A) is located close to the front side of the casing (31), and the rear heat exchange portion (40B) is located close to the rear side of the casing (31). The front heat exchange portion (40A) and the rear heat exchange portion (40B) are arranged to sandwich the indoor fan (32) in the direction orthogonal to both the top-bottom direction and the axial direction of the heat transfer tube (42), or in other words, in the front-rear direction.
  • The front heat exchange portion (40A) includes a front main heat exchange portion (43), a first auxiliary heat exchange portion (44), and a second auxiliary heat exchange portion (45).
  • The front main heat exchange portion (43) is disposed in part of the front heat exchange portion (40A) that is close to the indoor fan (32). The outer shape of the front main heat exchange portion (43) is formed in a V shape when viewed in the longitudinal direction of the heat transfer tube (42). The tip of the V shape is directed to the front side.
  • The front main heat exchange portion (43) includes a first front main heat exchange portion (43a) and a second front main heat exchange portion (43b). The first front main heat exchange portion (43a) is located in an upper part of the front main heat exchange portion (43), and the second front main heat exchange portion (43b) is located in a lower part of the front main heat exchange portion (43). The lower end of the first front main heat exchange portion (43a), or in other words, the lower short side of the fin (41), is in contact with the long side of the fin (41) of the second front main heat exchange portion (43b) (more precisely, the upper end portion of the long side of the fin (41)).
  • The first auxiliary heat exchange portion (44) is provided on the inlet side (the front side) of the first front main heat exchange portion (43a). The number of the heat transfer tubes (42) in the first auxiliary heat exchange portion (44) that is along the long side (hereinafter referred to as the number of rows) is smaller than the number of the heat transfer tubes (42) in the first front main heat exchange portion (43a). The number of the heat transfer tubes (42) in the first auxiliary heat exchange portion (44) that is along the short side (hereinafter referred to as the number of columns) is smaller than the number of the heat transfer tubes (42) in the first front main heat exchange portion (43a).
  • The second auxiliary heat exchange portion (45) is provided on the inlet side (the front side) of the second front main heat exchange portion (43b). The number of rows and the number of columns of the heat transfer tubes (42) in the second auxiliary heat exchange portion (45) are smaller than the number of rows and the number of columns of the heat transfer tubes (42) in the second front main heat exchange portion (43b).
  • The rear heat exchange portion (40B) includes a rear main heat exchange portion (46) and a third auxiliary heat exchange portion (47). The rear main heat exchange portion (46) is disposed in part of the rear heat exchange portion (40B) that is close to the indoor fan (32). The third auxiliary heat exchange portion (47) is provided on the inlet side (the rear side) of the rear main heat exchange portion (46). The lengths of the long side and the short side of the fin (41) of the third auxiliary heat exchange portion (47) are shorter than the lengths of the long side and the short side of the fin (41) of the rear main heat exchange portion (46). The number of rows and the number of columns of the heat transfer tubes (42) in the third auxiliary heat exchange portion (47) are smaller than the number of rows and the number of columns of the heat transfer tubes (42) in the rear main heat exchange portion (46).
  • The plate stack (50, 60) is disposed to the right side of the heat exchanger body (B) and is adjacent to the heat exchanger body (B). The right side is an example of the first direction. Specifically, the plate stack (50, 60) is disposed to the right side of the rightmost one of the plurality of fins (41) as well as being parallel to the fin (41). The plate stack (50, 60) is connected to end portion of the heat transfer tube (42). As shown in FIG. 5, the plate stack (50, 60) includes a front plate stack (50) connected with the heat transfer tubes (42) of the front heat exchange portion (40A) and a rear plate stack (60) connected with the heat transfer tubes (42) of the rear heat exchange portion (40B). The front plate stack (50) is disposed to overlap with the front heat exchange portion (40A) in the axial direction of the heat transfer tube (42). The rear plate stack (60) is disposed to overlap with the rear heat exchange portion (40B) in the axial direction of the heat transfer tube (42). The front plate stack (50) and the rear plate stack (60) will be described in detail later.
    • (3-2) Indoor Expansion Valve, Gas Relay Pipe, and Liquid Relay Pipe
  • The indoor expansion valve (37) is an electronic expansion valve of which the opening degree is variable. The indoor expansion valve (37) is disposed to the right of the plate stack (50, 60). The indoor expansion valve (37) is connected to the front plate stack (50) through a first internal pipe (38), and is connected to the rear plate stack (60) through a second internal pipe (39). The first internal pipe (38) and the second internal pipe (39) are examples of the refrigerant pipes that connect the front refrigerant flow path (51) of the front plate stack (50) and the rear refrigerant flow path (61) of the rear plate stack (60) together.
    • (4) Plate Stack
  • The gas relay pipe (12a) transfers the refrigerant gas compressed by the compressor (21) to the indoor heat exchanger (40). The gas relay pipe (12a) is an example of the gas pipe (12a). One end of the gas relay pipe (12a) is connected to the rear plate stack (60). The other end of the gas relay pipe (12a) is connected to the first connection pipe (12) via a joint. One end of the liquid relay pipe (13a) is connected to the front plate stack (50). The other end of the liquid relay pipe (13a) is connected to the second connection pipe (13) via a joint.
  • The plate stack (50, 60) contains the flow path (51, 61) that communicates with the heat transfer tubes (42). The plate stack (50, 60) includes a plurality of plates (52, 62) stacked in the right direction. The plate stack (50, 60) of this embodiment will be described in detail with reference to FIGS. 5 to 14.
    • (4-1) Front Plate Stack
  • The front plate stack (50) includes the front refrigerant flow path (51), a front connection pipe (53), a front relay portion (54), and a liquid end portion (55). The front refrigerant flow path (51) is formed in the front plate stack (50). The front connection pipe (53) connects the plurality of heat transfer tubes (42) of the front heat exchange portion (40A) and the front refrigerant flow path (51). The front relay portion (54) is connected with the first internal pipe (38). The liquid end portion (55) communicates with the second connection pipe (13) via the liquid relay pipe (13a). The front plate stack (50) will be described below as the plate stack (50, 60) of the present disclosure.
    • (4-1-1) First Plate Portion and Second Plate Portion
  • As shown in FIGS. 5, 6, and 8, the front plate stack (50) includes a front first plate portion (50A) and a front second plate portion (50B). The front first plate portion (50A) is an example of the first plate portion (50A, 60A) of the present disclosure. The front second plate portion (50B) is an example of the second plate portion (50B, 60B) of the present disclosure. The front first plate portion (50A) includes two front plates (52) stacked together. The front second plate portion (50B) includes three front plates (52) stacked together.
  • The shape of the outer edge of each front plate (52) of the front first plate portion (50A) is the same. The three front plates (52) of the front first plate portion (50A) are defined as a first plate (521) and a second plate (522) in order from the left. The first plate (521) is connected with the front connection pipes (53) extending toward the right end portion of the heat transfer tubes (42). The inside of the front connection pipes (53) forms the front refrigerant flow path (51) described later.
  • The shape of the outer edge of each front plate (52) of the front second plate portion (50B) is the same. The three front plates (52) of the front second plate portion (50B) are defined as a third plate (523), a fourth plate (524) and a fifth plate (525) in order from the left.
  • The shape of each front plate (521, 522) of the front first plate portion (50A) is different from the shape of each front plate (523, 524, 525) of the front second plate portion (50B). Specifically, the shape of the outer edge of the front first plate portion (50A) is different from the shape of the outer edge of the front second plate portion (50B).
  • The front second plate portion (50B) is disposed on the surface of the front first plate portion (50A) that is opposite to the surface facing the heat exchanger body (B). Specifically, the front second plate portion (50B) is disposed on the right surface of the front first plate portion (50A).
  • Each of the front plates (521 to 525) is made of the same material as those of the heat transfer tube (42) and the front connection pipe (53). In this embodiment, the front plates (521 to 525) of the front first plate portion (50A) and the front second plate portion (50B) are made of an aluminum alloy.
  • When the front plate stack (50) is viewed from the left direction, the area of the left surface of the front first plate portion (50A) is smaller than the area of left surface of the front second plate portion (50B). In other words, when viewed from the left direction, the front plate stack (50) has a first region (S1) in which the front first plate portion (50A) and the front second plate portion (50B) do not overlap with each other and a second region (S2) in which the front first plate portion (50A) and the front second plate portion (50B) overlap with each other.
  • When the front plate stack (50) is viewed from the opposite direction of the right direction, or in other words, from the left direction, the area of part of the front second plate portion (50B) that does not overlap with the front first plate portion (50A) is smaller than the area of part of the front second plate portion (50B) that overlaps with the front first plate portion (50A). In other words, the area of the first region (S1) is smaller than the area of the second region (S2).
  • As shown in FIG. 8, the front plate stack (50) has a step portion (X). The step portion (X) is formed by the front first plate portion (50A) and the front second plate portion (50B). The step portion (X) is formed in a peripheral portion of the left surface (501) of the front plate stack (50) that faces the heat exchanger body (B). The left surface (501) of the front plate stack (50) is an example of the first surface (501). In other words, the step portion (X) is formed in the peripheral portion of the left surface of the front plate stack (50). Further, in other words, the step portion (X) is a portion in which the first region (S1) is formed when the front plate stack (50) is viewed from the left direction. Specifically, the step portion (X) is formed by the first region (S1) and a first circumferential surface (P1) of the front second plate portion (50B). The first circumferential surface (P1) is part of a circumferential surface sandwiched between the right surface and the left surface of the front first plate portion (50A) that is in contact with the first region (S1).
  • The step portion (X) is formed in a lower portion of the front plate stack (50) when the front plate stack (50) is viewed from the right. Specifically, the step portion (X) is formed in part of the front plate stack (50) that is below the height position of the center of the front plate stack (50). In other words, in the air-conditioning indoor unit (30) of this embodiment, the inlet port (33), the front heat exchange portion (40A), and the outlet port (34) are disposed in order from the top (see FIG. 3), and therefore the step portion (X) is located close to the outlet port (34) in the front plate stack (50).
  • In this manner, the first region (S1) is formed in a lower portion of the front second plate portion (50B). Part of the circumferential surface of the front plate stack (50) in which the front first plate portion (50A) and the front second plate portion (50B) overlap with each other is a flush surface. In other words, when the front plate stack (50) is viewed from the left direction, there is no region in which the front first plate portion (50A) and the front second plate portion (50B) do not overlap with each other.
  • The first region (S1) only needs to be formed in a lower portion of the front first plate portion (50A) when the front plate stack (50) is viewed from the left direction, and the shape of the first region (S1) is not limited.
  • The front plate stack (50) is subjected to anti-corrosion treatment. Specifically, in the front plate stack (50), the entire surface of the left surface (501) and the second region (S2) of the right surface (502) are subjected to anti-corrosion treatment. For the anti-corrosion treatment of this embodiment, alloy plates with a sacrificial anti-corrosion effect are provided on the entire surface of the left surface (501) and the second region (S2) of the right surface (502) of the front plate stack (50). The alloy plates are made of, for example, a clad material with a relatively high amount of metal in which a core material is aluminum and a skin material is zinc. The first region (S1) and the first circumferential surface (P1) do not require the anti-corrosion treatment. This is because the third plate (523) forming the first region (S1) is one of intermediate plates (522 to 524) each having a large thickness. Similarly, this is because the fourth plate (524) forming part of the first circumferential surface (P1) is also one of the intermediate plates (522 to 524) each having a large thickness.
  • Next, the thicknesses of each front plate (521 to 525) of the front plate stack (50) will be described. In the front plate stack (50), the front plate (52) of the front first plate portion (50A) that is closest to the heat exchanger body (B) is defined as a first end plate, and the front plate (52) of the front second plate portion (50B) that is most distant from the heat exchanger body (B) is defined as a second end plate. In this embodiment, the first end plate (521) is the first plate (521) located at the left end of the front first plate portion (50A), and the second end plate (525) is the fifth plate (525) located at the right end of the front second plate portion (50B).
  • In the front plate stack (50), the plates between the first end plate (521) and the second end plate (525) are defined as the intermediate plates (522 to 524). In this embodiment, the intermediate plates (522 to 524) include the second plate (522), the third plate (523), and the fourth plate (524).
  • The thickness of each of the intermediate plates (522 to 524) is greater than the thickness of each of the first end plate (521) and the second end plate (525). In this embodiment, the thickness of each of the intermediate plates (522 to 524) is 3.0 mm, and the thickness of each of the first end plate (521) and the second end plate (525) is 1.5 mm.
    • (4-1-2) Configuration of Refrigerant Flow Path
  • A configuration of the front refrigerant flow path (51) of the plate stack (50) of this embodiment will be described. The front refrigerant flow path (51) is included in the refrigerant flow path (51, 61) of the present disclosure. An example of the front refrigerant flow path (51) will be described below.
  • As shown in FIGS. 9 and 10, the front refrigerant flow path (51) has first flow paths (51A) provided in the front first plate portion (50A), and second flow paths (51B) provided between the front first plate portion (50A) and the front second plate portion (50B). The first flow paths (51A) and the second flow paths (51B) are provided in portions that overlap with the front first plate portion (50A) and the front second plate portion (50B).
  • The first flow path (51A) is formed by two first through holes (71) penetrating the first plate (521) in the thickness direction located at the left end of the front first plate portion (50A); a first groove portion (81) formed in the second plate (522) located in the middle; and the third plate (523) located at the right end. One end of the first through hole (71) communicates with one end of the heat transfer tube (42). The other end of the first through hole (71) is connected to the first groove portion (81).
  • The first groove portion (81) is a long hole formed along the surface of the first plate (521). One end of the first groove portion (81) is connected to one of the first through holes (71), and the other end of the first groove portion (81) is connected to the other one of the first through holes (71). The first groove portion (81) is closed in the left-right direction by the first plate (521) located at the left end and the third plate (523) located at the right end.
  • The second flow path (51B) is formed by second through holes (72) penetrating the front first plate portion (50A) in the thickness direction; a second groove portion (82) formed in the fourth plate (524) located at the left end of the front second plate portion (50B); and the fifth plate (525) located at the right end of the front second plate portion (50B). One end of the second through hole (72) communicates with one end of the heat transfer tube (42). The other end of the second through hole (72) is connected to the second groove portion (82). The second groove portion (82) is a long hole formed along the surface of the second plate (522). One end of the second groove portion (82) is connected to one of the second through holes (72), and the other end of the second groove portion (82) is connected to the other one of the second through holes (72). The second groove portion (82) is closed in the left-right direction by the third plate (523) and the fifth plate (525).
  • In FIG. 11, the first groove portion (81) is illustrated by a one-dot chain line, and the second groove portion (82) is illustrated by a two-dot chain line. As shown in FIG. 11, the first groove portion (81) and the second groove portion (82) are disposed to intersect each other when the front plate stack (50) is viewed from the left. Accordingly, the second flow path (51B) intersects the first flow path (51A). Specifically, the second flow path (51B) is formed to cross the first flow path (51A) in the right direction.
    • (4-2) Rear Plate Stack
  • As shown in FIGS. 5 to 6, the rear plate stack (60) includes the rear refrigerant flow path (61) formed inside the rear plate stack (60); a plurality of rear connection pipes (not shown) connecting the plurality of heat transfer tubes (42) of the rear heat exchange portion (40B) and the rear refrigerant flow path (61); a rear relay portion (64) connected with the second internal pipe (39); and a gas end portion (65) communicating with the first connection pipe (12) via the gas relay pipe (12a). The rear refrigerant flow path (61) is included the refrigerant flow path (51, 61) of the present disclosure.
  • The rear plate stack (60) is different from the front plate stack (50) in terms of the shape of the outer edge of the plate when viewed from the right direction and in terms of the rear refrigerant flow path (61) in the rear plate stack (60). The rear plate stack (60) is a thick plate member that includes five rear plates (62) each formed in the same shape and stacked together. The rear plates (62) are stacked in the right direction.
  • The five rear plates (62) forming the rear plate stack (60) include a sixth plate (621), a seventh plate (622), an eighth plate (623), a ninth plate (624), and a tenth plate (625) arranged in order from the left (see FIG. 5).
  • As in the front plate stack (50), the sixth plate (621) closest to the heat exchange portion (B) is defined as a first end plate (621), the tenth plate (625) most distant from the heat exchange portion (B) is defined as a second end plate (625), and the seventh to ninth plates (622 to 624) disposed between the sixth plate (621) and the tenth plate (625) are defined as intermediate plates (622 to 624). In this case, the thickness of each of the intermediate plates (622 to 624) is greater than the thickness of each of the sixth plate (621) and the tenth plate (625).
  • The rear plate stack (60) is subjected to anti-corrosion treatment in the same way the front plate stack (50) is. Specifically, the alloy plates are attached to the left surface (601) and the right surface (602) of the rear plate stack (60). The left surface (601) and the right surface (602) of the rear plate stack (60) correspond to the first surface (601) and the second surface (602) of the present disclosure, respectively.
  • The rear relay portion (64) is a circular pipe. As shown in FIG. 5, the rear relay portion (64) is disposed on the right surface of the rear plate stack (60). In other words, in the rear plate stack (60), the second internal pipe (39) that connects the front refrigerant flow path (51) of the front plate stack (50) and the rear refrigerant flow path (61) of the rear plate stack (60) are connected to the right surface of the rear plate stack (60). The gas end portion (65) is a circular pipe. The gas end portion (65) is located on the right surface of the rear plate stack (60).
    • (4-3) U-Shaped Connection Pipe
  • As shown in FIG. 8, in the indoor heat exchanger (40), the connection pipe (400) having a U-shape is disposed between the heat exchanger body (B) and the front plate stack (50). The connection pipe (400) having a U-shape is hereinafter referred to as a U-shaped connection pipe (400).
  • The U-shaped connection pipe (400) is provided in the heat exchanger body (B). The U-shaped connection pipe (400) connects the heat transfer tubes (42) adjacent to each other. The refrigerant flowing from the heat transfer tube (42) of the heat exchanger body (B) into the U-shaped connection pipe (400) is discharged to the adjacent one of the heat transfer tubes (42) without passing through the plate stack (50, 60), and then flows into the heat exchanger body (B).
  • The U-shaped connection pipe (400) is disposed at a position facing the step portion (X) when viewed from the opposite direction of the right direction, or in other words, from the left direction. Specifically, the position of the right end of the U-shaped pipe is disposed inside the space formed by the step portion (X). More specifically, the position of the right end of the U-shaped connection pipe (400) is disposed to the right side of the left surface of the front plate stack (50). In other words, in the left-right direction, the position of the right end of the U-shaped connection pipe (400) is disposed at the same position as the position of the left surface of the first plate (521) or disposed to the right side of the same.
  • The air-conditioning indoor unit (30) includes a temperature sensor (70) that detects a refrigerant temperature. The temperature sensor (70) detects a temperature of a refrigerant flowing through the heat transfer tube (42). The temperature sensor (70) is an example of the detecting unit (70).
  • As shown in FIGS. 12A and 12B, the temperature sensor (70) is provided on the U-shaped connection pipe (400), and the indoor heat exchanger (40) includes an attachment unit (90). The attachment unit (90) is a member for attaching the temperature sensor (70) to the U-shaped connection pipe. The attachment unit (90) includes an attachment member (91) for housing the temperature sensor (70), and a brazed portion (92) for attaching the attachment member (91) to the surface of the U-shaped connection pipe (400). The attachment member (91) is attached to the U-shaped connection pipe (400) via the brazed portion (92).
  • The attachment member (91) has a substantially cylindrical shape, for example, and is configured to be able to house part of the temperature sensor (70). The attachment member (91) is attached to a curved portion of the U-shaped connection pipe (400), for example. The brazed portion (92) is configured to extend linearly, for example. The brazed portion (92) is formed by, for example, supplying a brazing material between the U-shaped connection pipe (400) and the attachment member (91) and then heating the brazing material with the flame of a burner.
  • A sacrificial layer of which the potential is lower than the potential of the surface of the attachment member (91) is formed on part of the surface of the attachment member (91). The sacrificial layer is made of Zn, Zn alloy, Al alloy containing Zn, or the like, and is formed on the surface of a heat transfer tube (42) by thermal spraying, for example. The sacrificial layer is sacrificially corroded to protect the attachment member (91), and retards corrosion of the surface of the attachment member (91) for a long period of time.
  • The attachment member (91) and the piping portion such as the U-shaped connection pipe (400) are made of the same type of metal, such as aluminum of A3003. Accordingly, it is possible to retard electrolytic corrosion of the attachment member (91) and the piping portion.
    • (5) Features (5-1) First Feature
  • Among the plate stacks (50, 60) of the indoor heat exchanger (40) of this embodiment, the front plate stack (50) is adjacent to the indoor heat exchanger body (B) in the right direction (the first direction). The front plate stack (50) includes: the front first plate portion (50A) having two front plates (52); and the front second plate portion (50B) which includes three front plates (52) different in shape from the front plates (52) of the front first plate portion (50A) and which is disposed on the surface of the front first plate portion (50A) that is opposite to the surface facing the heat exchanger body (B). The step portion (X) is formed in a peripheral portion of the surface of the front plate stack (50) that faces the heat exchanger body (B), and the step portion (X) is formed by the front first plate portion (50A) and the front second plate portion (50B).
  • By providing the step portion (X) in the front plate stack (50) in this manner, it is possible to form a space at a position facing the step portion (X). By using this space effectively, such as disposing a predetermined component in this space, it is possible to downsize the air-conditioning indoor unit (30).
    • (5-2) Second Feature
  • In this embodiment, the second to fourth plates (522 to 524) of the front plate stack (50) are thicker than the first plate (521) and the fifth plate (525), and the seventh to ninth plates (622 to 624) of the rear plate stack (60) are thicker than the sixth plate (621) and the tenth plate (625).
  • Accordingly, by increasing the thickness of the intermediate plates (522 to 524), it is possible to increase the area or the inner diameter of the cross section of the refrigerant flow path (51, 61) formed in the plate stack (50, 60). Accordingly, it is possible to reduce an increase in pressure loss of the refrigerant flowing through the refrigerant flow path (51, 61).
    • (5-3) Third Feature
  • The surface of the plate stack (50,60) of this embodiment that is opposite to the surface facing the heat exchanger body (B) is subjected to anti-corrosion treatment. Accordingly, it is possible to reduce electrolytic corrosion of the right surface of the plate stack (50, 60) caused by dew condensation or others, and then it is possible to increase the durability of the indoor heat exchanger (40).
    • (5-4) Fourth Feature
  • When the front plate stack (50) is viewed from the left direction, the area of part of the front second plate portion (50B) that does not overlap with the front first plate portion (50A) is smaller than the area of part of the front second plate portion (50B) that overlaps with the front first plate portion (50A).
  • Part of the front plate stack (50) in which the front first plate portion (50A) and the front second plate portion (50B) overlap each other is thicker than part of the front plate stack (50) in which only the front first plate portion (50A) is present, and therefore a larger number of the flow paths (51, 61) can be formed therein. Accordingly, it is possible to increase the flow rate of the refrigerant flowing through the heat transfer tubes (42) of the heat exchange portion (B), and as a result, the heat exchange is promoted. In this embodiment, when the region of the portion in which the front first plate portion (50A) and the front second plate portion (50B) overlap with each other is larger than the region of the portion in which only the front first plate portion (50A) is present, it is possible to secure a sufficient number of flow paths in the front plate stack (50), and therefore it is possible to promote the indoor heat exchanger (40) exchanging heat between air and a refrigerant.
    • (5-5) Fifth Feature
  • The front refrigerant flow path (51) has first flow paths (51A) provided in the front first plate portion (50A), and second flow paths (51B) provided between the front first plate portion (50A) and the front second plate portion (50B). The second flow path (51B) is formed to intersect the first flow path (51A).
  • By designing the front refrigerant flow path (51) so that the first flow path (51A) and the second flow path (51B) intersect each other, it is possible to create more patterns of the front refrigerant flow path (51) in the front plate stack (50). On the other hand, by designing the front plate stack (50) where the portion in which only the first flow path (51A) is provided and the first flow path (51A) and the second flow path (51B) do not intersect with each other is formed as the step portion (X), it is possible to form a space that can be used effectively. In other words, by providing the step portion (X), it is possible to reduce an unnecessary part of one front plate (52) in which the front refrigerant flow path (51) cannot be provided.
    • (5-6) Sixth Feature
  • The heat exchanger body (B) of this embodiment includes the U-shaped connection pipe (400) disposed between the heat exchanger body (B) and the front plate stack (50) and connecting two heat transfer tubes (42) with each other. The U-shaped connection pipe (400) is disposed at a position facing the step portion (X) when viewed from the left direction (the opposite direction of the first direction).
  • It is necessary to form a gap between the heat exchanger body (B) and the front plate stack (50) into an enough size to dispose the U-shaped connection pipe (400), and in this embodiment, since the connection pipe (400) is disposed in the space formed by the step portion (X), the gap between the heat exchanger body (B) and the front plate stack (50) can be relatively small. Accordingly, it is possible to make the indoor heat exchanger (40) compact.
    • (5-7) Seventh Feature
  • In this embodiment, the inner heat exchanger further includes the temperature sensor (70) configured to detect a temperature of a refrigerant flowing through the heat transfer tubes (42), and the temperature sensor (70) is provided in the U-shaped connection pipe (400). It is possible to provide the detecting unit (70) by effectively using the space formed by the step portion (X).
    • (6) Variations
  • An air-conditioning indoor unit (30) of a variation will be described. The configurations different from those of the air-conditioning indoor unit (30) of the embodiment will be described below.
    • (6-1) First Variation
  • As shown in FIG. 13, in an indoor heat exchanger (40) of a first variation, the U-shaped connection pipe (400) is connected to the front plate stack (50). Specifically, the U-shaped connection pipe (400) is disposed in the first region (S1) of the front plate stack (50). Both end portions of the U-shaped connection pipe (400) extend to the right, and they are connected to the refrigerant flow path (51, 61) formed in the front second plate portion (50B). In this manner, the refrigerant flowing through the refrigerant flow path (51, 61) in the front plate stack (50) flows through the U-shaped connection pipe (400) of the first variation. The temperature sensor (70) provided in the U-shaped connection pipe (400) can detect the temperature of the refrigerant flowing in the front plate stack (50).
    • (6-2) Second Variation
  • A rear plate stack (60) of a second variation has the same configuration as the front plate stack (50) of the embodiment. In other words, the rear plate stack (60) has a rear first plate portion (60A) and a rear second plate portion (60B). The rear first plate portion (60A) and the rear second plate portion (60B) are examples of the first plate portion (50A, 60A) and the second plate portion (50B, 60B) of the present disclosure.
  • The rear plate stack (60) is an example of the plate stack (50, 60) of the present disclosure. The rear first plate portion (60A) and the rear second plate portion (60B) have the same configurations as those of the front first plate portion (50A) and the front second plate portion (50B) of the front plate stack (50) of the embodiment, respectively, and thus the description thereof will be omitted. When viewed from the left direction, the rear plate stack (60) has a first region (S1) in which the rear second plate portion (60B) and the rear first plate portion (60A) do not overlap with each other and a second region (S2) in which the rear second plate portion (60B) and the rear first plate portion (60A) overlap with each other.
  • In the indoor heat exchanger (40) of the second variation, the first internal pipe (38) and the second internal pipe (39) are disposed between the heat exchanger body (B) and the plate stack (50, 60). Specifically, the first internal pipe (38) is connected to the left surface of the front plate stack (50). The second internal pipe (39) is connected to the left surface of the rear plate stack (60). The front relay portion (54) of this variation is disposed in the first region (S1) of the front plate stack (50), and the rear relay portion (64) is disposed in the first region (S1) of the rear plate stack (60). The first internal pipe (38) extends from the rear relay portion (64) to the left (to the heat exchanger body (B)), and then extends to the rear plate stack (60). The second internal pipe (39) extends from the rear relay portion (64) to the left (the heat exchanger body (B)), and then extends to the front plate stack (50). In this manner, in this variation, even if the space between the heat exchanger body (B) and the plate stack (50, 60) is relatively small, it is possible to dispose the first internal pipe (38) and the second internal pipe (39) by using the space formed by the step portion (X).
    • (7) Other Embodiments
  • The following configurations may be applied to the air-conditioning indoor units (30) of the above-described embodiment and variations.
  • In the embodiment, the indoor heat exchanger (40) may be configured so that if the indoor heat exchanger (40) functions a radiator, a refrigerant in a supercooled region flows in the U-shaped connection pipe (400). Since the U-shaped connection pipe (400) is disposed away from the front plate stack (50), it is possible to reduce heat exchange between the refrigerant in the supercooled region and the refrigerant flowing through the front plate stack (50).
  • If as in the second variation the rear plate stack (60) has the rear first plate portion (60A) and the second rear plate unit, the U-shaped connection pipe (400) may be disposed at a position facing the step portion (X) of the rear plate stack (60). In this case, the U-shaped connection pipe (400) may be connected to the heat exchanger body (B) provided on the rear side or may be connected to the rear plate stack (60). This indoor heat exchanger (40) may be configured so that if the indoor heat exchanger (40) functions as an evaporator, a refrigerant in a superheated region flows therein. For example, the U-shaped connection pipe (400) communicates with the first connection pipe (12) via the gas end portion (65). In this manner, the refrigerant in the superheated region flows into the U-shaped connection pipe (400) located outside the plate stack (50, 60), whereby it is possible to reduce heat exchange between the refrigerant flowing through the refrigerant flow path (51, 61) in the plate stack (50, 60) and the refrigerant in the superheated region.
  • If as in the second variation the rear plate stack (60) has the rear first plate portion (60A) and the rear second plate portion (60B), the gas end portion (65) may be connected to the rear refrigerant flow path (61) formed in the portion in which the rear first plate portion (60A) and the rear second plate portion (60B) overlap with each other. Specifically, the gas end portion (65) may be disposed in the second region (S2). Accordingly, the refrigerant flowing from the first connection pipe (12) to the rear plate stack (60) through the gas relay pipe (12a) passes through the refrigerant flow path (51, 61) that is relatively long and that extends in the stacking direction of the rear first plate portion (60A) and the rear second plate portion (60B), and therefore it is possible to reduce the pressure loss of the compressed gas refrigerant.
  • The indoor heat exchanger (40) may be disposed in the air passage (P) communicating with the inlet port (33) and the outlet port (34) each provided in the casing (31), and the step portion (X) may be formed on part of the plate stack (50, 60) that is on a downstream side of the air flow when viewed from the right direction.
  • For example, in summer, if the indoor heat exchanger (40) functions as an evaporator, the air passage (P) has a temperature gradient in which the temperature decreases from the inlet port (33) to the outlet port (34). In this air passage (P), the air temperature is higher on the upstream side, and therefore the load of heat exchange is greater in part of the indoor heat exchanger (40) that is located on an upstream side of the air flow than on a downstream side of the same. Therefore, by providing the step portion (X) on a downstream part of the plate stack (50, 60) and increasing the thickness of an upstream part of the plate stack (50, 60), it is possible to secure a sufficient number of refrigerant flow paths (51, 61) on the upstream part of the plate stack (50, 60). Accordingly, it is possible to increase the flow rate of the refrigerant flowing through the upper part of the heat exchanger body (B), and then it is possible to promote heat exchange between the refrigerant and the air in the upper part of the indoor heat exchanger (40). As a result, it is possible to reduce the load of heat exchange in the upper part of the indoor heat exchanger (40), and also it is possible to increase the efficiency of heat exchange with the air flowing through the air passage (P), and therefore, it is possible to adjust the air temperature in the indoor space to the target temperature more immediately.
  • In the variation, the rear plate stack (60) may include rear refrigerant flow paths (61) that correspond to the first flow path (51A) and the second flow path (51B) of the front plate stack (50) of the embodiment. In other words, the rear plate stack (50, 60) may have the plurality of rear refrigerant flow paths (61) that intersect each other.
  • In the embodiment and variation, instead of the alloy plates with the sacrificial anti-corrosion effect, an anti-corrosion or anti-rust coating material may be applied to the plate stack (50, 60). In this case, the coating material is an epoxy resin coating material. The coating material only needs to be applied to form a coating film on a front surface including the right surface (502) and the left surface (501) of the plate stack (50, 60).
  • In the embodiment and variations, the heat transfer tubes (42), the plate stack (50, 60), the refrigerant pipe (the connection pipe (53), the U-shaped connection pipe (400), or the like), the attachment member (91), and the detecting unit of the temperature sensor (70) may be made of a copper alloy or stainless steel. The heat transfer tube (42), the U-shaped connection pipe (400), the attachment member (91), and the temperature sensor (70) are made of the same metal in one preferred embodiment. In addition, if the heat transfer tube (42) is made of a copper alloy, the plate stack (50, 60) and the refrigerant pipe is also made of a copper alloy in one preferred embodiment.
  • While the embodiment and variations thereof have been described above, it will be understood that various changes in form and details may be made without departing from the spirit and scope of the claims. The foregoing embodiment and variations thereof may be combined and replaced with each other without deteriorating the intended functions of the present disclosure. The expressions of "first," "second," ... described above are used to distinguish the terms to which these expressions are given, and do not limit the number and order of the terms.
    • INDUSTRIAL APPLICABILITY
  • As described above, the present disclosure is useful for an indoor heat exchanger and an air-conditioning indoor unit.
    • DESCRIPTION OF REFERENCE CHARACTERS
    • 12a Gas Relay Pipe (Gas Pipe)
    • 30 Air-Conditioning Indoor Unit
    • 40 Indoor Heat Exchanger
    • 41 Fin
    • 42 Heat Transfer Tube
    • 50, 60 Plate Stack
    • 50A, 60A First Plate Portion
    • 50B, 60B Second Plate Portion
    • 51, 61 Refrigerant Flow Path (Flow Path)
    • 51A First Flow Path
    • 51B Second Flow Path
    • 52, 62 Plate
    • 70 Temperature Sensor (Detecting Unit)
    • 400 U-Shaped Connection Pipe (Connection Pipe)
    • 521 First Plate (First End Plate)
    • 522 to 524 Intermediate Plate
    • 525 Second End Plate (Fifth Plate)
    • B Heat Exchanger Body (Heat Exchange Portion)
    • X Step Portion

Claims (9)

  1. An indoor heat exchanger comprising:
    a heat exchange portion (B) including a plurality of fins (41) and a plurality of heat transfer tubes (42) penetrating the plurality of fins (41); and
    a plate stack (50, 60) in which a flow path (51, 61) communicating with the heat transfer tube (42) is provided and in which a plurality of plates (52, 62) are stacked in a first direction in which the heat transfer tube (42) extends,
    wherein
    the plate stack (50, 60)
    is adjacent to the heat exchange portion (B) in the first direction, and includes
    a first plate portion (50A, 60A) having one or more of the plates (52, 62), and
    a second plate portion (50B, 60B) which has one or more of the plates (52, 62) that is different in shape from the plates (52, 62) of the first plate portion (50A, 60A) and which is disposed on a surface of the first plate portion (50A, 60A) that is opposite to a surface facing the heat exchange portion (B),
    the plate stack (50, 60) has a step portion (X) in a peripheral portion of a first surface (501, 601) facing the heat exchange portion (B), and
    the step portion (X) is formed by the first plate portion (50A, 60A) and the second plate portion (50B, 60B).
  2. The indoor heat exchanger of claim 1, wherein
    the plate stack (50, 60) has the plates (52, 62) including three or more plates (52, 62), and
    in the plate stack (50, 60),
    one of the plates (52, 62) of the first plate portion (50A, 60A) that is closest to the heat exchange portion (B) is defined as a first end plate (521),
    one of the plates (52, 62) of the second plate portion (50B, 60B) that is most distant from the heat exchange portion (B) is defined as a second end plate (525), and
    the plate (52, 62) disposed between the first end plate (521) and the second end plate (525) is defined as an intermediate plate (522 to 524),
    the flow path (51, 61) runs through the intermediate plate (522 to 524, 622 to 624), and
    a thickness of the intermediate plate (522 to 524) is greater than a thickness of the first end plate (521) and the second end plate (525).
  3. The indoor heat exchanger of claim 1 or 2, wherein
    in the plate stack (50, 60), at least part of the first surface (501, 601) and a second surface (502, 602) that is opposite to the first surface (501, 601) is subjected to anti-corrosion treatment.
  4. The indoor heat exchanger of any one of claims 1 to 3, wherein
    when the plate stack (50, 60) is viewed from an opposite direction of the first direction, an area of part of the second plate portion (50B, 60B) that does not overlap with the first plate portion (50A, 60A) is smaller than an area of part of the second plate portion (50B, 60B) that overlaps with the first plate portion (50A, 60A).
  5. The indoor heat exchanger of any one of claims 1 to 4, wherein
    the flow path (51, 61) includes
    a first flow path (51A) provided in the first plate portion (50A, 60A), and
    a second flow path (51B) provided between the first plate portion (50A, 60A) and the second plate portion (50B, 60B), and
    the second flow path (51B) is formed to intersect the first flow path (51A).
  6. The indoor heat exchanger of any one of claims 1 to 5, wherein
    the heat exchange portion (B) includes a connection pipe (400) having a U-shape, disposed between the heat exchange portion (B) and the plate stack (50, 60), and connecting two of the heat transfer tubes (42), and
    the connection pipe (400) is disposed at a position facing the step portion (X) when viewed from the first direction.
  7. The indoor heat exchanger of claim 6, further comprising:
    a detecting unit (70) configured to detect a temperature of a refrigerant flowing through the heat transfer tube (42),
    wherein
    the detecting unit (70) is provided in the connection pipe (400).
  8. The indoor heat exchanger of claim 6 or 7, wherein
    in the connection pipe (400),
    a refrigerant in a superheated region flows if the indoor heat exchanger functions as an evaporator, and
    a refrigerant in a supercooled region flows if the indoor heat exchanger functions as a radiator.
  9. An air-conditioning indoor unit comprising:
    the indoor heat exchanger of any one of claims 1 to 8; and
    a gas pipe (12a) configured to transfer compressed refrigerant gas to the indoor heat exchanger (40),
    wherein
    the gas pipe (12a) is connected to the flow path (51, 61) formed in part of the plate stack (50, 60) in which the first plate portion (50A, 60A) and the second plate portion (50B, 60B) overlap with each other.
EP24871397.6A 2023-09-29 2024-06-14 Indoor heat exchanger and air-conditioning indoor machine Pending EP4775920A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2023169548A JP7602165B1 (en) 2023-09-29 2023-09-29 Indoor heat exchanger
PCT/JP2024/021704 WO2025069592A1 (en) 2023-09-29 2024-06-14 Indoor heat exchanger and air-conditioning indoor machine

Publications (1)

Publication Number Publication Date
EP4775920A1 true EP4775920A1 (en) 2026-07-15

Family

ID=93850384

Family Applications (1)

Application Number Title Priority Date Filing Date
EP24871397.6A Pending EP4775920A1 (en) 2023-09-29 2024-06-14 Indoor heat exchanger and air-conditioning indoor machine

Country Status (4)

Country Link
EP (1) EP4775920A1 (en)
JP (1) JP7602165B1 (en)
CN (1) CN121925536A (en)
WO (1) WO2025069592A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN120799699A (en) * 2025-08-29 2025-10-17 合肥美的暖通设备有限公司 Heat pump water heater

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006125652A (en) * 2004-10-26 2006-05-18 Mitsubishi Electric Corp Heat exchanger
FR2916835B1 (en) * 2007-05-31 2010-07-30 Valeo Systemes Thermiques HEAT EXCHANGE MODULE FOR AN AIR CONDITIONING CIRCUIT
EP2998682B1 (en) 2013-05-15 2019-11-06 Mitsubishi Electric Corporation Laminated header, heat exchanger, and air conditioner
JP6005266B2 (en) * 2013-05-15 2016-10-12 三菱電機株式会社 Laminated header, heat exchanger, and air conditioner
WO2016071953A1 (en) * 2014-11-04 2016-05-12 三菱電機株式会社 Indoor unit for air conditioning device
CN109154460B (en) * 2016-05-23 2021-05-18 三菱电机株式会社 Stacked headers, heat exchangers and air conditioners
CN110476036B (en) * 2017-03-31 2021-05-18 三菱电机株式会社 Heat exchanger and refrigeration cycle apparatus provided with the same
JP6906149B2 (en) * 2019-05-17 2021-07-21 パナソニックＩｐマネジメント株式会社 Plate fin laminated heat exchanger and refrigeration system using it
JP6930557B2 (en) * 2019-06-28 2021-09-01 ダイキン工業株式会社 Heat exchanger and heat pump equipment
DE112020007772T5 (en) * 2020-11-12 2023-09-21 Mitsubishi Electric Corporation Indoor heat exchanger and indoor unit of an air conditioning system

Also Published As

Publication number Publication date
CN121925536A (en) 2026-04-24
WO2025069592A1 (en) 2025-04-03
JP2025059459A (en) 2025-04-10
JP7602165B1 (en) 2024-12-18

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20260408

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC ME MK MT NL NO PL PT RO RS SE SI SK SM TR