US20250020409A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US20250020409A1
US20250020409A1 US18/712,526 US202218712526A US2025020409A1 US 20250020409 A1 US20250020409 A1 US 20250020409A1 US 202218712526 A US202218712526 A US 202218712526A US 2025020409 A1 US2025020409 A1 US 2025020409A1
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United States
Prior art keywords
heat exchanger
water guide
upper header
heat transfer
transfer tubes
Prior art date
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Pending
Application number
US18/712,526
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English (en)
Inventor
Atsushi Morita
Tsuyoshi Maeda
Akira YATSUYANAGI
Kosuke Sato
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: YATSUYANAGI, Akira, MAEDA, TSUYOSHI, MORITA, ATSUSHI, SATO, KOSUKE
Publication of US20250020409A1 publication Critical patent/US20250020409A1/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • 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
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/08—Fins with openings, e.g. louvers

Definitions

  • the present disclosure relates to a heat exchanger having a water guide.
  • This parallel-flow heat exchanger has been known as having such a configuration that a flat plate extending from the lowermost portion of an upper header to the flat tubes is provided to prevent condensate from scattering from the upper header (see, for example, Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2015-227754
  • the flat plate is simply attached to the upper header to cover the surface of the upper header. This may cause condensate to scatter from outside of the flat plate without being guided to the heat exchanger, and thus may cause dew dripping.
  • the present disclosure has been made in view of the above circumstances, and it is an object of the present disclosure to provide a heat exchanger that can prevent dew dripping of condensate from a header.
  • a heat exchanger includes: a plurality of heat transfer tubes, each of which extends in a first direction, arranged in a second direction orthogonal to the first direction; an upper header provided on an upper end of each of the plurality of heat transfer tubes and extending in the second direction; and a water guide covering a part of the upper header within a region of an angle formed by the first direction and a third direction orthogonal to the first direction and the second direction as viewed from a center of the upper header in the second direction, and guiding condensate generated on a surface of the upper header toward a position between the plurality of heat transfer tubes.
  • the water guide covers a part of a lower portion of the upper header within the region of the angle formed by the first direction and the third direction, and can therefore guide condensate generated on the surface of the upper header toward the position between the plurality of heat transfer tubes.
  • FIG. 1 is a refrigerant circuit diagram schematically illustrating the refrigerant circuit configuration of a refrigeration cycle apparatus according to Embodiment 1.
  • FIG. 2 is a cross-sectional schematic diagram illustrating a second heat exchanger in the refrigeration cycle apparatus according to Embodiment 1 viewed in cross-section from the front.
  • FIG. 3 is a side cross-sectional schematic diagram illustrating the second heat exchanger according to Embodiment 1 viewed in cross-section from the side.
  • FIG. 4 is a cross-sectional schematic diagram illustrating the second heat exchanger in the refrigeration cycle apparatus according to a modification of Embodiment 1 viewed in cross-section from the front.
  • FIG. 5 is a side cross-sectional schematic diagram illustrating the second heat exchanger according to the modification of Embodiment 1 viewed in cross-section from the side.
  • FIG. 6 is a side cross-sectional schematic diagram illustrating the second heat exchanger according to Embodiment 2 viewed in cross-section from the side.
  • FIG. 7 illustrates the second heat exchanger according to Embodiment 2 with a first water guide provided to an upper header of a flat tube inclined forward.
  • FIG. 8 is a side cross-sectional schematic diagram illustrating the second heat exchanger according to Embodiment 3 viewed in cross-section from the side.
  • FIG. 9 illustrates the first water guide of the second heat exchanger according to Embodiment 3.
  • FIG. 10 illustrates the first water guide of the second heat exchanger according to a modification of Embodiment 3.
  • FIG. 11 is an explanatory diagram describing a contact angle.
  • FIG. 12 illustrates the first water guide provided to a first-row heat exchanger and a second-row heat exchanger arranged next to each other in a third direction of the second heat exchanger according to Embodiment 5.
  • FIG. 13 is a top cross-sectional schematic diagram illustrating the A-A′ cross-section of FIG. 12 .
  • FIG. 14 is a side cross-sectional schematic diagram illustrating the second heat exchanger according to Embodiment 6 viewed in cross-section from the side.
  • FIG. 1 is a refrigerant circuit diagram schematically illustrating the refrigerant circuit configuration of a refrigeration cycle apparatus 200 according to Embodiment 1.
  • the refrigeration cycle apparatus 200 according to Embodiment 1 includes, as elements of the refrigerant circuit, a first heat exchanger 152 and a second heat exchanger 154 .
  • the first heat exchanger 152 is provided with a first refrigerant distributer 152 a .
  • the second heat exchanger 154 is provided with a second refrigerant distributer 154 a.
  • the refrigeration cycle apparatus 200 has an outdoor unit 101 and an indoor unit 102 .
  • the outdoor unit 101 has a compressor 100 , a flow switching device 151 , the first heat exchanger 152 , and an expansion device 153 .
  • An accumulator 300 is located upstream of the compressor 100 .
  • the first heat exchanger 152 is provided with the first refrigerant distributer 152 a .
  • the first refrigerant distributer 152 a distributes refrigerant to heat transfer tubes of the first heat exchanger 152 .
  • An outdoor fan 156 is provided in the vicinity of the first heat exchanger 152 .
  • the outdoor unit 101 has a controller 160 .
  • the indoor unit 102 has the second heat exchanger 154 .
  • the second heat exchanger 154 is provided with the second refrigerant distributer 154 a .
  • the second refrigerant distributer 154 a distributes refrigerant to heat transfer tubes (not illustrated) of the second heat exchanger 154 .
  • An indoor fan 157 is provided in the vicinity of the second heat exchanger 154 .
  • the compressor 100 , the first heat exchanger 152 , and the expansion device 153 are connected by a pipe 155 a , while the expansion device 153 , the second heat exchanger 154 , and the compressor 100 are connected by a pipe 155 b , thereby forming the refrigerant circuit.
  • the compressor 100 is configured to compress suctioned refrigerant into a high-temperature and high-pressure state.
  • the refrigerant compressed by the compressor 100 is discharged from the compressor 100 and delivered to the first heat exchanger 152 or the second heat exchanger 154 .
  • the flow switching device 151 is configured to switch a flow of refrigerant between flow directions for heating operation and cooling operation.
  • the flow switching device 151 switches the flow of refrigerant to a flow direction to connect the compressor 100 and the second heat exchanger 154 during heating operation, and switches the flow of refrigerant to a flow direction to connect the compressor 100 and the first heat exchanger 152 during cooling operation.
  • the flow switching device 151 is preferably a four-way valve. However, a combination of two-way valves or three-way valves may be employed as the flow switching device 151 .
  • the first heat exchanger 152 serves as an evaporator during heating operation, and serves as a condenser during cooling operation.
  • low-temperature and low-pressure refrigerant flowing out from the expansion device 153 exchanges heat with air supplied by the outdoor fan 156 , and liquid refrigerant of low-temperature and low-pressure two-phase gas-liquid refrigerant evaporates.
  • the first heat exchanger 152 when the first heat exchanger 152 serves as a condenser, high-temperature and high-pressure refrigerant discharged from the compressor 100 exchanges heat with air supplied by the outdoor fan 156 , and high-temperature and high-pressure gas refrigerant condenses.
  • the first heat exchanger 152 may be a refrigerant-water heat exchanger. In this case, in the first heat exchanger 152 , refrigerant exchanges heat with a heat medium such as water.
  • the expansion device 153 is configured to expand refrigerant flowing out from the first heat exchanger 152 or the second heat exchanger 154 , and to reduce the pressure of the refrigerant.
  • the expansion device 153 is preferably an electrically operated expansion valve or another component that is capable of adjusting, for example, the flow rate of refrigerant. Note that as the expansion device 153 , not only the electrically operated expansion valve, but a mechanical expansion valve or a capillary tube are also applicable.
  • the mechanical expansion valve employs a diaphragm on its pressure receiving portion.
  • the second heat exchanger 154 serves as a condenser during heating operation, and serves as an evaporator during cooling operation.
  • high-temperature and high-pressure refrigerant discharged from the compressor 100 exchanges heat with air supplied by the indoor fan 157 , and high-temperature and high-pressure gas refrigerant condenses.
  • the second heat exchanger 154 when the second heat exchanger 154 serves as an evaporator, low-temperature and low-pressure refrigerant flowing out from the expansion device 153 exchanges heat with air supplied by the indoor fan 157 , and low-temperature and low-pressure liquid refrigerant of two-phase gas-liquid refrigerant evaporates.
  • the second heat exchanger 154 may be a refrigerant-water heat exchanger. In this case, in the second heat exchanger 154 , refrigerant exchanges heat with a heat medium such as water.
  • the first refrigerant distributer 152 a distributes refrigerant to a plurality of heat transfer tubes of the first heat exchanger 152 .
  • the outdoor fan 156 sends air to be used for exchanging heat to the first heat exchanger 152 .
  • the second refrigerant distributer 154 a distributes refrigerant to heat transfer tubes (not illustrated) of the second heat exchanger 154 .
  • the indoor fan 157 sends air to be used for exchanging heat to the second heat exchanger 154 .
  • the controller 160 controls the refrigeration cycle apparatus 200 in its entirety. Specifically, the controller 160 controls the driving frequency of the compressor 100 in response to the cooling capacity or heating capacity required. The controller 160 also controls the opening degree of the expansion device 153 in response to the operating condition and operating mode. The controller 160 further controls the flow switching device 151 in response to the operating mode.
  • the controller 160 uses information transmitted from each temperature sensor (not illustrated) and each pressure sensor (not illustrated) to control, for example, respective actuators of the compressor 100 , the expansion device 153 , and the flow switching device 151 .
  • controller 160 may be hardware such as a circuit device that implements the functions of the controller 160 , or may be made up of a computation device such as a microcomputer and a CPU, and software to be executed by the computation device.
  • the controller 160 is dedicated hardware or a central processing unit (CPU, also referred to as “central processor,” “processing device,” “computation device,” “microprocessor,” “microcomputer,” or “processor”) configured to execute programs stored in a memory.
  • CPU central processing unit
  • processing device processing device
  • computation device computational device
  • microprocessor microcomputer
  • processor processor
  • the controller 160 is equivalent to, for example, a single circuit, a combined circuit, an application specific integrated circuit (ASIC), a field programmable gate array (FPGA), or a combination of any of the foregoing.
  • ASIC application specific integrated circuit
  • FPGA field programmable gate array
  • the functional units of the controller 160 may be individually implemented by separate units of hardware, or the functional units of the controller 160 may be implemented together by a single unit of hardware.
  • the functions to be executed by the controller 160 are implemented by software, firmware, or a combination of the software and the firmware.
  • the software and the firmware are described as programs and stored in the memory.
  • the CPU reads and executes the programs stored in the memory, thereby to implement the functions of the controller 160 .
  • the memory is a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, and an EEPROM.
  • the functions of the controller 160 may be partially implemented by dedicated hardware, while being partially implemented by software or firmware.
  • FIG. 1 illustrates an example in which the first heat exchanger 152 is provided with the first refrigerant distributer 152 a
  • the second heat exchanger 154 is provided with the second refrigerant distributer 154 a
  • either the first heat exchanger 152 or the second heat exchanger 154 may only be provided with a refrigerant distributer.
  • high-temperature and high-pressure refrigerant in gas form is discharged from the compressor 100 .
  • the high-temperature and high-pressure gas refrigerant (single phase) discharged from the compressor 100 flows into the first heat exchanger 152 .
  • the high-temperature and high-pressure gas refrigerant flowing in the first heat exchanger 152 exchanges heat with air supplied by the outdoor fan 156 .
  • This high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant (single phase).
  • the high-pressure liquid refrigerant delivered from the first heat exchanger 152 is brought into a state of low-pressure two-phase gas-liquid refrigerant by the expansion device 153 .
  • the two-phase gas-liquid refrigerant is collected by the second refrigerant distributer 154 a , and the collected two-phase gas-liquid refrigerant flows into the second heat exchanger 154 .
  • the two-phase gas-liquid refrigerant distributed by the second refrigerant distributer 154 a and flowing into the second heat exchanger 154 exchanges heat with air supplied by the indoor fan 157 .
  • Liquid refrigerant of the two-phase gas-liquid refrigerant then evaporates into low-pressure single-phase gas refrigerant.
  • the low-pressure gas refrigerant delivered from the second heat exchanger 154 flows into the compressor 100 through the accumulator 300 , and is then compressed into high-temperature and high-pressure gas refrigerant to be discharged from the compressor 100 again. This cycle is repeated afterwards.
  • operation of the refrigeration cycle apparatus 200 in heating mode is performed by switching the flow of refrigerant to the flow direction shown by the solid arrows in FIG. 1 by the flow switching device 151 .
  • the refrigerant flows in a fixed direction, instead of providing the flow switching device 151 on the discharge side of the compressor 100 .
  • the flow switching device 151 is not provided.
  • refrigeration cycle apparatus 200 include, in addition to the air-conditioning apparatus, a hot-water supply device, a refrigerating machine, and an air-conditioning hot-water supply combination system.
  • FIG. 2 is a cross-sectional schematic diagram illustrating the second heat exchanger 154 in the refrigeration cycle apparatus 200 according to Embodiment 1 viewed in cross-section from the front.
  • FIG. 3 is a side cross-sectional schematic diagram illustrating the second heat exchanger 154 according to Embodiment 1 viewed in cross-section from the side.
  • FIGS. 2 and 3 illustrate the second heat exchanger 154
  • the first heat exchanger 152 may also employ the same configuration as the second heat exchanger 154 .
  • the second heat exchanger 154 includes an upper header 1 , a lower header 2 , flat tubes 3 , corrugated fins 4 , a drain pan 5 , and a water guide 12 .
  • the flat tubes 3 extend in a first direction, which is the vertical direction (gravity direction).
  • the first direction is the vertical direction.
  • a direction pointed by the arrow of the first direction corresponds to its positive direction.
  • the upper header 1 and the lower header 2 are located to extend in a second direction orthogonal to the first direction.
  • the flat tubes 3 are spaced apart from each other in the second direction with their ends inserted into the upper header 1 , and with their other ends inserted into the lower header 2 .
  • the flow direction of refrigerant is not particularly specified, the refrigerant flows from the lower header 2 toward the upper header 1 during evaporation operation in FIG. 2 .
  • the upper header 1 serving as a gas header has an outer diameter larger than the outer diameter of the lower header 2 to reduce a pressure loss of the refrigerant flowing inside the upper header 1 . Therefore, dew dripping from the upper header 1 is more likely to occur.
  • the upper header 1 and the lower header 2 may each have a circular-cylindrical shape or a cylindrical shape with a D-shape in cross section.
  • the corrugated fins 4 are attached to the flat tubes 3 such that the corrugated fins 4 are each positioned between the corresponding adjacent ones of the flat tubes 3 .
  • the corrugated fins 4 extend in the second direction orthogonal to the first direction.
  • the corrugated fins 4 transfer heat to the flat tubes 3 .
  • the corrugated fins 4 each have a louvered structure through which water can be discharged in the first direction. Note that the form of a fin to be attached to the flat tubes 3 is not limited to the corrugated fin.
  • the drain pan 5 When the second heat exchanger 154 is located in place, the drain pan 5 is located below the lower header 2 .
  • the drain pan 5 receives, on its upper surface, condensate that adheres to the surface of the upper header 1 and drops onto the drain pan 5 through the water guide 12 .
  • the water guide 12 is provided to the upper header 1 , and has a first water guide 11 a and a second water guide 11 b .
  • the first water guide 11 a and the second water guide 11 b are formed as separate components of, for example, resin.
  • the first water guide 11 a covers a part of the upper header 1 within a region of an angle formed by the first direction and a third direction orthogonal to the first direction and the second direction as viewed from a center C of the upper header 1 in the second direction.
  • a direction pointed by the arrow of the third direction corresponds to its positive direction.
  • the center C of the upper header 1 refers to the center of the cross-section of the flow passage of the upper header 1 .
  • the first water guide 11 a guides condensate generated on the surface of the upper header 1 to the corrugated fins 4 .
  • the first water guide 11 a is provided in front of the upper header 1 in the direction of airflow passing through the corrugated fins 4 . While not being in contact with the corrugated fins 4 , the first water guide 11 a is located in the vicinity of the corrugated fins 4 such that the first water guide 11 a guides the condensate to the corrugated fins 4 .
  • the first water guide 11 a covers the upper header 1 over the entire region of the angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 in the second direction.
  • One end portion of the first water guide 11 a positioned closer to the heat transfer tubes than is the other end portion is positioned on an imaginary line extending in the positive direction of the first direction, or in an area between the imaginary line and an imaginary line extending in the negative direction of the third direction as viewed from the center C of the upper header 1 in the second direction (see, for example, FIG. 8 ).
  • the second water guide 11 b covers a part of the upper header 1 within a region of an angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 in the second direction.
  • the second water guide 11 b guides condensate generated on the surface of the upper header 1 to the corrugated fins 4 .
  • the second water guide 11 b is provided behind the upper header 1 in the direction of airflow passing through the corrugated fins 4 . While not being in contact with the corrugated fins 4 , the second water guide 11 b is located in the vicinity of the corrugated fins 4 such that the second water guide 11 b guides the condensate to the corrugated fins 4 .
  • FIG. 4 is a cross-sectional schematic diagram illustrating the second heat exchanger 154 in the refrigeration cycle apparatus 200 according to a modification of Embodiment 1 viewed in cross-section from the front.
  • FIG. 5 is a side cross-sectional schematic diagram illustrating the second heat exchanger 154 according to the modification of Embodiment 1 viewed in cross-section from the side.
  • the first water guide 11 a and the second water guide 11 b are in contact with the corrugated fins 4 as illustrated in FIGS. 4 and 5 .
  • the first water guide 11 a and the second water guide 11 b are in contact with the uppermost part of the corrugated fins 4 .
  • first water guide 11 a and the second water guide 11 b each have a substantially L-shape as illustrated in FIG. 5 when the second heat exchanger 154 is viewed from the side
  • first water guide 11 a and the second water guide 11 b may each have other shape such as a semi-circular shape.
  • Condensate generated on the surface of the upper header 1 is guided to the corrugated fins 4 by the first water guide 11 a and the second water guide 11 b .
  • the condensate guided to the corrugated fins 4 exchanges heat with airflow passing through the corrugated fins 4 , while being partially discharged in the first direction.
  • the condensate discharged from the corrugated fins 4 runs down the surface of the flat tubes 3 and drops from the lower header 2 onto the drain pan 5 .
  • the water guide 12 allows condensate generated on the surface of the upper header 1 to be guided to the corrugated fins 4 , so that it is possible to prevent the condensate from flowing out from the upper header 1 to an airflow path. As a result, it is possible to prevent drew dripping of condensate generated on the surface of the upper header 1 .
  • the first water guide 11 a and the second water guide 11 b are in contact with the corrugated fins 4 as illustrated in FIG. 5 .
  • a gap between the corrugated fins 4 and the upper header 1 is closed by the first water guide 11 a and the second water guide 11 b , so that it is possible to prevent airflow from passing through the gap between the corrugated fins 4 and the upper header 1 .
  • it is possible to prevent condensation on an airflow path downstream of the second heat exchanger 154 which can be caused by moist air flowing through the second heat exchanger 154 to the downstream airflow path.
  • the second heat exchanger 154 has been described as being provided vertically. In Embodiment 2, the second heat exchanger 154 is located with an inclination to the vertical direction.
  • FIG. 6 is a side cross-sectional schematic diagram illustrating the second heat exchanger 154 according to Embodiment 2 viewed in cross-section from the side. Note that the same components as those in FIGS. 2 and 3 are denoted by the same reference signs, and different parts are described below.
  • the flat tube 3 is located with an inclination to the vertical direction.
  • the first direction is an inclination direction of the flat tube 3 .
  • the third direction is orthogonal to the first direction and the second direction.
  • the water guide 12 is provided to the upper header 1 and has the first water guide 11 a .
  • the first water guide 11 a covers a part of the upper header 1 that faces in the direction in which the flat tube 3 is inclined, within a region of an angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 in the second direction.
  • the first water guide 11 a guides condensate generated on the surface of the upper header 1 to the corrugated fins 4 .
  • the first water guide 11 a is provided in front of the upper header 1 in the direction of airflow passing through the corrugated fins 4 . While not being in contact with the corrugated fins 4 , the first water guide 11 a is located in the vicinity of the corrugated fins 4 such that the first water guide 11 a guides the condensate to the corrugated fins 4 .
  • the first water guide 11 a may be in contact with the corrugated fins 4 .
  • the first water guide 11 a is in contact with the uppermost part of the corrugated fins 4 .
  • the first direction which is the inclination direction of the flat tube 3 to the vertical direction, may be either inclined forward or inclined rearward with reference to the airflow direction.
  • the flat tube 3 may be inclined at any angle.
  • FIG. 6 illustrates a state in which the first water guide 11 a is provided to the upper header 1 , to which the flat tube 3 inclined rearward is inserted.
  • FIG. 7 illustrates the second heat exchanger 154 according to Embodiment 2 with the first water guide 11 a provided to the upper header 1 , to which the flat tube 3 inclined forward is inserted.
  • the first water guide 11 a covers a part of the lower portion of the upper header 1 to prevent the occurrence of dew dipping from the upper header 1 due to gravity.
  • the first water guide 11 a is in contact with the corrugated fins 4 .
  • the first water guide 11 a is in contact with the uppermost part of the corrugated fins 4 .
  • the first water guide 11 a still covers a lower part of the upper header 1 , which is inclined. It is therefore possible to prevent condensate generated on the surface of the upper header 1 from dropping onto the airflow path passing through the corrugated fins 4 .
  • FIG. 8 is a side cross-sectional schematic diagram illustrating the second heat exchanger 154 according to Embodiment 3 viewed in cross-section from the side.
  • FIG. 9 illustrates the first water guide 11 a of the second heat exchanger 154 according to Embodiment 3.
  • the water guide 12 has an L-shape in side view, and has a comb-like shape at its lower end.
  • the flat tubes 3 are inserted between teeth of this comb-like shape and fixed to the teeth.
  • the lower end of the water guide 12 is in contact with the corrugated fins 4 .
  • the first water guide 11 a covers the upper header 1 over the entire region of the angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 in the second direction.
  • One end portion of the first water guide 11 a positioned closer to the heat transfer tubes than is the other end portion is positioned on an imaginary line extending in the positive direction of the first direction, or in an area between the imaginary line and an imaginary line extending in the negative direction of the third direction as viewed from the center C of the upper header 1 in the second direction.
  • the first water guide 11 a has such a comb-like shape that the contact position between the first water guide 11 a and the corrugated fins 4 is located upstream of the center of the upper header 1 in the airflow direction.
  • the first water guide 11 a having such a comb-like shape as described above is used, so that condensate flowing on the water guide 12 is less likely to flow out to the downstream side of the airflow.
  • FIG. 10 illustrates the first water guide 11 a of the second heat exchanger 154 according to a modification of Embodiment 3. As illustrated in FIG. 10 , the first water guide 11 a is located to extend across heat exchangers 21 a and 21 b.
  • the first water guide 11 a is provided to the upper header 1 of the heat exchanger 21 a .
  • the first water guide 11 a covers a part of the upper header 1 of the heat exchanger 21 a , that faces in the direction in which the flat tube 3 is inclined, within a region of an angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 of the heat exchanger 21 a in the second direction.
  • the first water guide 11 a guides condensate generated on the surface of the upper header 1 of the heat exchanger 21 a to the corrugated fins 4 .
  • the first water guide 11 a also covers a part of the upper header 1 of the heat exchanger 21 b , that faces in the direction in which the flat tube 3 is inclined, within a region of an angle formed by the first direction and the third direction orthogonal to the first direction and the second direction as viewed from the center C of the upper header 1 of the heat exchanger 21 b in the second direction.
  • the first water guide 11 a guides condensate generated on the surface of the upper header 1 of the heat exchanger 21 b to the corrugated fins 4 .
  • the first water guide 11 a is in contact with the corrugated fins 4 , and thus allows condensate generated on the upper header 1 to be guided to the surface of the corrugated fins 4 more reliably.
  • the first water guide 11 a has an L-shape in side view, and thus can close the airflow path passing through between the upper header 1 and the corrugated fins 4 . As a result, it is possible to prevent formation of frost on the airflow path caused by moist air bypassing the corrugated fins 4 .
  • the surfaces of the first water guide 11 a and the second water guide 11 b in Embodiment 1 are water-repellent surfaces.
  • the surfaces of the first water guide 11 a and the second water guide 11 b in Embodiments 2 and 3 are water-repellent surfaces.
  • the surfaces of the corrugated fins 4 in Embodiments 1, 2, and 3 are hydrophilic surfaces.
  • FIG. 11 is an explanatory diagram describing the contact angle ⁇ .
  • the contact angle ⁇ is formed by a solid surface rSL and a droplet surface rLV.
  • the contact angle ⁇ is larger than or equal to 90°.
  • the contact angle ⁇ is smaller than or equal to 40°, and preferably smaller than or equal to 10°.
  • a droplet has such properties that when a surface has a wettability gradient with which the contact angle ⁇ changes, a driving force is generated, which causes the droplet to move from a water-repellent surface toward a hydrophilic surface. Therefore, according to Embodiment 4, condensate is more easily guided from the first water guide 11 a or the second water guide 11 b toward the corrugated fins 4 .
  • FIG. 12 illustrates the first water guide 11 a provided to a first-row heat exchanger 22 a and a second-row heat exchanger 22 b arranged next to each other in the third direction of the second heat exchanger 154 according to Embodiment 5.
  • FIG. 13 is a top cross-sectional schematic diagram illustrating the A-A′ cross-section of FIG. 12 .
  • FIG. 13 illustrates the area where the first water guide 11 a is located by use of hatched lines. Note that the same components as those in FIGS. 2 and 3 are denoted by the same reference signs, and different parts are described below.
  • FIG. 12 illustrates a single unit of first-row heat exchanger 22 a located with an inclination, and the second-row heat exchanger 22 b located in parallel to the first-row heat exchanger 22 a in the third direction.
  • FIG. 13 illustrates a two-row second heat exchanger 154 .
  • inter-row water guide holes 31 are provided between the flat tubes 3 of the first-row heat exchanger 22 a and the flat tubes 3 of the second-row heat exchanger 22 b .
  • the flat tubes 3 of the first-row heat exchanger 22 a are also referred to as “first-row heat transfer tubes,” while the flat tubes 3 of the second-row heat exchanger 22 b are also referred to as “second-row heat transfer tubes.”
  • the first water guide 11 a extends toward the inter-row water guide holes 31 .
  • the corrugated fins 4 are provided integrally between the flat tubes 3 of the first-row heat exchanger 22 a and the flat tubes 3 of the second-row heat exchanger 22 b .
  • the corrugated fins 4 may be provided between the flat tubes 3 of the first-row heat exchanger 22 a separately from the corrugated fins 4 provided between the flat tubes 3 of the second-row heat exchanger 22 b .
  • the inter-row water guide holes 31 may be provided to the corrugated fins 4 .
  • the first water guide 11 a is provided to extend toward the inter-row water guide holes 31 . Therefore, in the second heat exchanger 154 according to Embodiment 5, it is possible to more efficiently discharge condensate, compared to when the condensate is discharged through a discharge path on the corrugated fins 4 .
  • FIG. 14 is a side cross-sectional schematic diagram illustrating the second heat exchanger 154 according to Embodiment 6 viewed in cross-section from the side. Note that the same components as those in FIGS. 2 and 3 are denoted by the same reference signs, and different parts are described below.
  • a thermal-insulation treatment portion 41 is provided between the upper header 1 and the first water guide 11 a of the second heat exchanger 154 according to Embodiment 6.
  • the thermal-insulation treatment portion 41 is additionally provided between the upper header 1 and the second water guide 11 b .
  • the thermal-insulation treatment portion 41 employs either one or both of thermal insulation sheet and hollow structure.
  • the thermal-insulation treatment portion 41 is provided between the first water guide 11 a and the upper header 1 .
  • the thermal-insulation treatment portions 41 are provided, so that when moist air touches the first water guide 11 a and the second water guide 11 b , the thermal-insulation treatment portions 41 can further prevent the moist air from being cooled by and condensed on the surface of the upper header 1 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
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US20240200838A1 (en) * 2022-12-20 2024-06-20 Kyungdong Navien Co., Ltd. Evaporative condenser

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CN216694564U (zh) * 2021-11-29 2022-06-07 丹佛斯有限公司 换热组件和具有该换热组件的空调系统
WO2026069556A1 (ja) * 2024-09-27 2026-04-02 三菱電機株式会社 熱交換器、および、空気調和機

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JPH0612425Y2 (ja) * 1990-01-18 1994-03-30 ピーエス工業株式会社 冷房用熱交換器
JP3287100B2 (ja) * 1993-05-19 2002-05-27 株式会社デンソー 空気調和装置のクーリングユニットおよび排水ケース
JP3797109B2 (ja) * 2001-01-19 2006-07-12 株式会社デンソー 蒸発器
JP2004316976A (ja) * 2003-04-14 2004-11-11 Japan Climate Systems Corp 熱交換器
KR101543655B1 (ko) * 2009-02-26 2015-08-11 한온시스템 주식회사 배수성 향상된 자동차용 공조장치
JP2015222146A (ja) * 2014-05-23 2015-12-10 パナソニックＩｐマネジメント株式会社 熱交換器
JP6471345B2 (ja) * 2014-05-29 2019-02-20 パナソニックＩｐマネジメント株式会社 熱交換器
JP2015227754A (ja) * 2014-06-02 2015-12-17 パナソニックＩｐマネジメント株式会社 熱交換器
JP2016020759A (ja) * 2014-07-14 2016-02-04 カルソニックカンセイ株式会社 熱交換器

Cited By (1)

* Cited by examiner, † Cited by third party
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US20240200838A1 (en) * 2022-12-20 2024-06-20 Kyungdong Navien Co., Ltd. Evaporative condenser

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