US20150168072A1 - Parallel-flow type heat exchanger and air conditioner equipped with same - Google Patents

Parallel-flow type heat exchanger and air conditioner equipped with same Download PDF

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US20150168072A1
US20150168072A1 US14/418,467 US201314418467A US2015168072A1 US 20150168072 A1 US20150168072 A1 US 20150168072A1 US 201314418467 A US201314418467 A US 201314418467A US 2015168072 A1 US2015168072 A1 US 2015168072A1
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Prior art keywords
heat exchanger
refrigerant
flat tubes
parallel
flow
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US14/418,467
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Madoka Ueno
Kazuhisa Mishiro
Takeshi Yoshida
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Sharp Corp
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Sharp Corp
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Assigned to SHARP KABUSHIKI KAISHA reassignment SHARP KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MISHIRO, KAZUHISA, UENO, MADOKA, YOSHIDA, TAKESHI
Publication of US20150168072A1 publication Critical patent/US20150168072A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • 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
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/18—Heat exchangers specially adapted for separate outdoor units characterised by their shape
    • 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
    • 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
    • F28D1/0233—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 air flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a parallel-flow heat exchanger of a side-flow type, and to an air conditioner incorporating it.
  • a plurality of flat tubes are arranged between a plurality of header pipes such that a plurality of refrigerant passages inside the flat tubes communicate with the interior of the header pipes, with fins such as corrugated fins arranged between the flat tubes.
  • fins such as corrugated fins arranged between the flat tubes.
  • FIG. 1 An example of the structure of a parallel-flow heat exchanger is shown in FIG. 1 .
  • the top and bottom sides of FIG. 1 correspond respectively to the top and bottom sides of the heat exchanger.
  • the parallel-flow heat exchanger 1 is of a side-flow type, and comprises two header pipes 2 and 3 extending in the vertical direction and a plurality of flat tubes 4 arranged between them and extending in the horizontal direction.
  • the header pipes 2 and 3 are arranged parallel to each other, at an interval in the horizontal direction.
  • the flat tubes 4 are arranged at a predetermined pitch in the vertical direction.
  • the parallel-flow heat exchanger 1 can be installed at any angle to suit particular designs, and therefore, in the present description, the “vertical” and “horizontal” directions should not be interpreted strictly but be understood to merely give a rough notion of relevant directions.
  • the flat tubes 4 are elongate moldings of metal formed by extrusion and, as shown in FIG. 2 , have formed inside them refrigerant passages 5 through which refrigerant is circulated.
  • the flat tubes 4 are arranged with their longitudinal direction, i.e., the extrusion direction, aligned with the horizontal direction, and thus through the refrigerant passages 5 , the refrigerant circulate in the horizontal direction.
  • the refrigerant passages 4 comprise a plurality of refrigerant passages having the same cross-sectional shape and the same cross-sectional area arranged in the left-right direction in FIG. 2 .
  • the flat tubes 4 look like a harmonica.
  • the refrigerant passages 5 each communicate with the interior of the header pipes 2 and 3 .
  • the flat tubes 4 have fins 6 fitted on their flat faces. Used as the fins 6 here are corrugated fins, but plate fins may instead be used. Of the fins 6 arranged in the up-down direction, the topmost and bottom most ones have side plates 7 arranged on their respective outer sides.
  • the header pipes 2 and 3 , the flat tubes 4 , the fins 6 , and the side plates 7 are all made of metal with good thermal conductivity, such as aluminum.
  • the flat tubes 4 are brazed or welded to the header pipes 2 and 3 , so are the fins 6 to the flat tubes 4 , and so are the side plates 7 to the fins 6 .
  • the interior of the header pipe 2 is divided by two partitions P 1 and P 2 into three sections S 1 , S 2 , and S 3 .
  • the partitions P 1 and P 2 separate the plurality of flat tubes 4 into three flat tube groups, so that a plurality of flat tubes 4 are connected to each of the sections S 1 , S 2 , and S 3 .
  • the interior of the header pipe 3 is divided by a single partition P 3 into two sections S 4 and S 5 .
  • the partition P 3 separates the plurality of flat tubes 4 into two flat tube groups, so that a plurality of flat tubes 4 are connected to each of the sections S 4 and S 5 .
  • a refrigerant introduction/discharge pipe 8 is connected to the section S 1 , and another refrigerant introduction/discharge pipe 9 is connected to the section S 2 .
  • the parallel-flow heat exchanger 1 operates in the following manner.
  • refrigerant is fed into the section S 1 through the refrigerant introduction/discharge pipe 8 .
  • the refrigerant that has entered the section S 1 flows toward the section S 4 through the plurality of flat tubes 4 connecting the section S 1 to the section S 4 .
  • This group of a plurality of flat tubes 4 constitutes a refrigerant path A.
  • the refrigerant path A is indicated by a hollow arrow.
  • Other refrigerant paths will be indicated by a hollow arrow each.
  • the refrigerant that has entered the section S 4 turns back, then to flow toward the section S 2 through the plurality of flat tubes 4 connecting the section S 4 to the section S 2 .
  • This group of a plurality of flat tubes 4 constitutes a refrigerant path B.
  • the refrigerant that has entered the section S 2 turns back, then to flow toward the section S 5 through the plurality of flat tubes 4 connecting the section S 2 to the section S 5 .
  • This group of a plurality of flat tubes 4 constitutes a refrigerant path C.
  • the refrigerant that has entered the section S 5 turns back, then to flow toward the section S 3 through the plurality of flat tubes 4 connecting the section S 5 to the section S 3 .
  • This group of a plurality of flat tubes 4 constitutes a refrigerant path D.
  • the refrigerant that has entered the section S 3 is then discharged out of it through the refrigerant introduction/discharge pipe 9 .
  • each segment between the refrigerant introduction/discharge pipe 8 or 9 and the next turning-back and between one and the next turning-back is referred to as “one turn.”
  • the refrigerant paths A, B, C, and D each count as a one-turn refrigerant path.
  • refrigerant is fed into the section S 3 through the refrigerant introduction/discharge pipe 9 . Thereafter, the refrigerant travels in the reverse direction the route that it travels when the parallel-flow heat exchanger 1 is used as the condenser. Specifically, the refrigerant passes through the refrigerant path D, then the refrigerant path C, then the refrigerant path B, and then the refrigerant path A to enter the section S 1 , and is then discharged through the refrigerant introduction/discharge pipe 8 .
  • Patent Documents 1 to 3 identified below.
  • a plurality of refrigerant passages with a fluidic diameter of 0.015 inches (about 0.38 millimeters) to 0.07 inches (about 1.78 millimeters) are formed parallel to one another.
  • the outline of the cross section of those refrigerant passages is so designed as to have two or more comparatively straight portions that meet together and at least one dented portion formed where they meet. This design helps reduce the air-side front-face area obstructed by flat tubes, and thus makes it possible to increase the air-side heat transfer surface without increasing the air-side pressure drop.
  • refrigerant passages inside flat tubes are given a height of 0.35 millimeters to 0.8 millimeters. This helps reduce the sum of the drop in heat emission due to draft resistance and the drop in heat emission due to tube pressure loss, and thus helps improve heat emission performance.
  • a flow distribution parameter ⁇ i.e., the ratio of the resistance parameter ⁇ of flat tubes to the resistance parameter ⁇ of the refrigerant inlet-side header pipe is set at 0.5 or more. This helps prevent a concentrated flow of refrigerant through flat tubes connected to a refrigerant-inlet part of the header pipe where the pressure is higher. It is thus possible to make the pressure applied to the respective flat tubes even so that satisfactory flow distribution is achieved, and thereby to obtain satisfactory heat exchange performance.
  • Patent Document 1 JP-A-H5-87752
  • Patent Document 2 JP-A-2001-165532
  • Patent Document 3 JP-A-2000-111274
  • a parallel-flow heat exchanger In a case where a parallel-flow heat exchanger is used as an evaporator, with respect to refrigerant passing through a refrigerant path, it is preferable that no such condition arise where more liquid refrigerant passes through some flat tubes and more gaseous refrigerant passes through other flat tubes; that is, it is preferable that no “uneven flow” occur.
  • the present invention aims to provide a parallel-flow heat exchanger of a side-flow type that is designed optimally from the perspective of avoiding such an uneven flow with respect to the number of flat tubes constituting a refrigerant path. In particular, the present invention aims to optimize the number of flat tubes constituting a refrigerant path through which passes refrigerant with a large proportion of gaseous refrigerant.
  • a parallel-flow heat exchanger of a side-flow type is provided with two header pipes extending in the vertical direction, and a plurality of flat tubes extending in the horizontal direction and coupling together the header pipes with each other.
  • the plurality of flat tubes are grouped such that each group comprises a plurality of flat tubes, each group constituting a one-turn refrigerant path through which refrigerant is passed from one to the other of the two header pipes extending in the vertical direction.
  • the upper limit of the number of flat tubes constituting the one-turn refrigerant path is determined to be within a range of ⁇ 2 of a value calculated using, when the parallel-flow heat exchanger is used in an outdoor unit of an air conditioner, the formula
  • n the number of flat tubes constituting the one-turn refrigerant path
  • Q represents rated capacity, given in watts (W). Used as Q is, for an outdoor unit, rated heating capacity and, for an indoor unit, rated cooling capacity.
  • the lower limit of the number of flat tubes constituting the one-turn refrigerant path be determined using the formula
  • d represents the hydraulic diameter, given in meters (m).
  • A′ represents the refrigerant passage cross-sectional area of one flat tube, given in square meters (m 2 ).
  • the lower limit of the number of flat tubes constituting the one-turn refrigerant path is determined using the formula
  • d represents the hydraulic diameter, given in meters (m).
  • A′ represents the refrigerant passage cross-sectional area of one flat tube, given in square meters (m 2 ).
  • an air conditioner is provided with a parallel-flow heat exchanger configured as described above in an outdoor unit or in an indoor unit.
  • FIG. 1 An outline configuration diagrams of a parallel-flow heat exchanger of a side-flow type
  • FIG. 2 A sectional view along line II-II in FIG. 1 ;
  • FIG. 3 A table listing the specifications of flat tube samples
  • FIG. 4 A table showing the correlation between refrigerant circulation rate and the uneven-flow-free number of flat tubes
  • FIG. 5 A plot showing the correlation between refrigerant circulation rate and the number of flat tubes
  • FIG. 6 A plot showing the correlation between cooling capacity and refrigerant circulation rate
  • FIG. 7 A plot showing the correlation between heating capacity and refrigerant circulation rate
  • FIG. 8 A plot showing the optimal range of the number of flat tubes for an outdoor unit of an air conditioner
  • FIG. 9 A plot showing the optimal range of the number of flat tubes for an indoor unit of an air conditioner
  • FIG. 10 A plot showing the correlation between refrigerant circulation rate and suction pressure
  • FIG. 11 A plot showing the correlation between refrigerant circulation rate and the number of flat tubes
  • FIG. 12 A plot showing the correlation between the number of flat tubes in an outdoor-unit heat exchanger and rated heating capacity
  • FIG. 13 A plot showing the correlation between the number of flat tubes in an indoor-unit heat exchanger and rated cooling capacity
  • FIG. 14 An outline configuration diagram of an air conditioner incorporating a parallel-flow heat exchanger according to the present invention, in heating operation.
  • FIG. 15 An outline configuration diagram of an air conditioner incorporating a parallel-flow heat exchanger according to the present invention, in cooling operation.
  • the number of refrigerant paths is not limited to four; more than four or less than four refrigerant paths may be provided.
  • the upper limit of the number of flat tubes 4 constituting a one-turn refrigerant path is determined; it is calculated, in a case where the parallel-flow heat exchanger is used in an outdoor unit of an air conditioner, using the formula
  • n represents the number of flat tubes constituting a one-turn refrigerant path
  • Q represents the rated capacity, given in watts (W).
  • Formula (A) was derived through experiments.
  • the table in FIG. 3 lists the specifications of the flat tubes examined in the experiments.
  • Sample a had a width of 16.2 mm, a thickness of 1.9 mm, and a refrigerant passage cross-sectional area of 13 mm 2 .
  • Sample b had a width of 13.9 mm, a thickness of 1.9 mm, and a refrigerant passage cross-sectional area of 11 mm 2
  • Sample c had a width of 16.2 mm, a thickness of 1.6 mm, and a refrigerant passage cross-sectional area of 11 mm 2
  • Sample d had a width of 19.2 mm, a thickness of 1.9 mm, and a refrigerant passage cross-sectional area of 14 mm 2 .
  • Sample a was used in Experiment 1.
  • a refrigerant circulation rate of 27.3 kg/h gave a maximum uneven-flow-free number of 8.
  • a refrigerant circulation rate of 42.5 kg/h gave a maximum uneven-flow-free number of 9.
  • a refrigerant circulation rate of 64.3 kg/h gave a maximum uneven-flow-free number of 10.
  • a refrigerant circulation rate of 63.2 kg/h gave a maximum uneven-flow-free number of 10.
  • Sample b was used in Experiment 2.
  • a refrigerant circulation rate of 20.9 kg/h gave a maximum uneven-flow-free number of 9.
  • a refrigerant circulation rate of 22.1 kg/h gave a maximum uneven-flow-free number of 8.
  • Sample c was used in Experiment 3.
  • a refrigerant circulation rate of 59.2 kg/h gave a maximum uneven-flow-free number of 10.
  • a refrigerant circulation rate of 48.8 kg/h gave a maximum uneven-flow-free number of 9.
  • a refrigerant circulation rate of 26.4 kg/h gave a maximum uneven-flow-free number of 8.
  • Sample b was used in Experiment 4.
  • a refrigerant circulation rate of 54.8 kg/h gave a maximum uneven-flow-free number of 8.
  • a refrigerant circulation rate of 89.2 kg/h gave a maximum uneven-flow-free number of 8.
  • FIG. 5 is a plot of the results of the experiments shown in FIG. 4 .
  • An approximation straight line is drawn, and from the approximation formula, the number of flat tubes is determined to be within a range of ⁇ 2 of the value given by
  • the refrigerant circulation rate m (kg/h) is typically set as a value proportional to the rated capacity of a product. How the refrigerant circulation rate correlates with the rated capacity is shown in FIGS. 6 and 7 .
  • a parallel-flow heat exchanger when used as an outdoor-unit heat exchanger of an air conditioner, functions as an evaporator in heating operation and, when used as a an indoor-unit heat exchanger of an air conditioner, functions as an evaporator in cooling operation.
  • n 3.0 ⁇ 10 ⁇ 4 Q+ 8.0.
  • the upper limit of the number of flat tubes constituting a one-turn refrigerant path is determined to be within a range of ⁇ 2 of the value given by
  • n 4.2 ⁇ 10 ⁇ 4 Q+ 7.9.
  • the lower limit of the number of flat tubes constituting each refrigerant path is determined As shown in FIG. 10 , as the temperature at the outlet of the heat exchanger falls into the range
  • the suction pressure drops greatly; that is, the suction pressure drops sharply with respect to the refrigerant circulation rate. This is due to frost formation resulting from the outlet temperature falling below 0° C.
  • T Rin represents the inlet evaporation temperature of the refrigerant.
  • the pressure loss ⁇ P is given in pascals (Pa).
  • P Rin represents the inlet evaporation temperature
  • P lim represents the saturation pressure of the refrigerant at 0° C.
  • ⁇ represents the coefficient of friction between the inner wall of the flat tubes 4 and the refrigerant
  • L represents a tube path length, given in meters (m)
  • d represents the hydraulic diameter, given in meters (m)
  • ⁇ represents the refrigerant density, given in kilograms per cubic meter (kg/m 3 );
  • u represents the flow speed of the refrigerant, given in meters per second (m/s).
  • M represents the refrigerant circulation rate, given in kilograms per second (kg/s); and A represents the sum of the refrigerant passage cross-sectional areas of the plurality of flat tubes constituting a one-turn refrigerant path, given in square meters (m 2 ).
  • ⁇ P ⁇ / 2 ⁇ L/dA 2 ⁇ M 2 .
  • n represents the number of flat tubes 4 constituting a one-turn refrigerant path.
  • the refrigerant circulation rate m (kg/h), which is M as given in a different unit, is typically set as a value proportional to the rated capacity of a product; hence it can be expressed as
  • rated heating capacity can be used; for an indoor-unit heat exchanger, rated cooling capacity can be used.
  • the coefficient of friction ⁇ varies with refrigerant circulation rate, refrigerant pressure, the shape of flat tubes, etc.; it is typically in the range of about 0.5 to about 0.05 in air conditioners for household use.
  • the density p varies with refrigerant pressure and dryness; it is typically in the range of 20 to 70 kg/m 3 with a gaseous refrigerant.
  • the flat tubes be branched at the inlet or in the middle of the heat exchanger.
  • FIGS. 12 and 13 are plots of examples of the results of calculation using formula (B).
  • FIG. 12 shows how the number of flat tubes in an outdoor-unit heat exchanger correlates with rated heating capacity.
  • FIG. 13 shows how the number of flat tubes in an indoor-unit heat exchanger correlates with rated cooling capacity.
  • the parallel-flow heat exchanger 1 can be incorporated in a separate-type air conditioner.
  • a separate-type air conditioner is composed of an outdoor unit and an indoor unit.
  • the outdoor unit includes a compressor, a four-way value, an expansion value, an outdoor heat exchanger, an outdoor blower, etc.
  • the indoor unit includes an indoor heat exchanger, an indoor blower, etc.
  • the outdoor heat exchanger functions as an evaporator in heating operation, and functions as a condenser in cooling operation.
  • the indoor heat exchanger functions as a condenser in heating operation, and functions as an evaporator in cooling operation.
  • FIG. 14 shows a basic configuration of a separate-type air conditioner that employs a heat pump cycle as a refrigerating cycle.
  • the heat pump cycle 101 is composed of a compressor 102 , a four-way value 103 , an outdoor heat exchanger 104 , a decompression-expansion device 105 , and an indoor heat exchanger 106 connected in a loop.
  • the compressor 102 , the four-way value 103 , the heat exchanger 104 , and the decompression-expansion device 105 are housed in the cabinet of an outdoor unit.
  • the heat exchanger 106 is housed in the cabinet of an indoor unit.
  • the heat exchanger 104 is combined with an outdoor blower 107 .
  • the heat exchanger 106 is combined with an indoor blower 108 .
  • the blower 107 includes a propeller fan.
  • the blower 108 includes a cross-flow fan.
  • the parallel-flow heat exchanger 1 can be used as a component of the heat exchanger 106 in the indoor unit.
  • the heat exchanger 106 comprises three heat exchangers 106 A, 106 B, and 106 C combined together like a roof covering the blower 108 .
  • the parallel-flow heat exchanger 1 can be used as any of the heat exchangers 106 A, 106 B, and 106 C.
  • the parallel-flow heat exchanger 1 according to the present invention can also be used as the heat exchanger 104 in the outdoor unit.
  • FIG. 14 shows how heating operation proceeds.
  • high-temperature, high-pressure refrigerant is discharged from the compressor 102 , and enters the indoor heat exchanger 106 , where the refrigerant emits heat and condenses.
  • the refrigerant then exits from the indoor heat exchanger 106 , passes through the decompression-expansion device 105 , and enters the outdoor heat exchanger 104 , where the refrigerant expands as it absorbs heat from the outdoor air, before returning to the compressor 102 .
  • a current of air produced by the indoor blower 108 promotes heat emission by the indoor heat exchanger 106
  • a current of air produced by the outdoor blower 107 promotes heat absorption by the outdoor heat exchanger 104
  • FIG. 15 shows how cooling operation or frost removal operation proceeds.
  • the four-way value 103 is so switched that the refrigerant circulates in the opposite direction compared with in heating operation.
  • high-temperature, high-pressure refrigerant is discharged from the compressor 102 , and enters the outdoor heat exchanger 104 , where the refrigerant emits heat and condenses.
  • the refrigerant then exits from the outdoor heat exchanger 104 , passes through the decompression-expansion device 105 , and enters the indoor heat exchanger 106 , where the refrigerant expands as it absorbs heat from the indoor air, before returning to the compressor 102 .
  • a current of air produced by the outdoor blower 107 promotes heat emission by the outdoor heat exchanger 104
  • a current of air produced by the indoor blower 108 promotes heat absorption by the indoor heat exchanger 106 .
  • the present invention finds wide application in parallel-flow heat exchangers of a side-flow type.

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  • 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)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US14/418,467 2012-09-04 2013-08-07 Parallel-flow type heat exchanger and air conditioner equipped with same Abandoned US20150168072A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2012-194111 2012-09-04
JP2012194111A JP5858478B2 (ja) 2012-09-04 2012-09-04 パラレルフロー型熱交換器及びそれを搭載した空気調和機
PCT/JP2013/071301 WO2014038335A1 (ja) 2012-09-04 2013-08-07 パラレルフロー型熱交換器及びそれを搭載した空気調和機

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US20180274820A1 (en) * 2015-12-01 2018-09-27 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US10473401B2 (en) * 2015-07-28 2019-11-12 Sanden Holdings Corporation Heat exchanger
US11047625B2 (en) 2018-05-30 2021-06-29 Johnson Controls Technology Company Interlaced heat exchanger
US20230204297A1 (en) * 2021-12-23 2023-06-29 Goodman Manufacturing Company, L.P. Heat exchanger assembly and method for hvac system
US12098887B2 (en) 2018-05-30 2024-09-24 Tyco Fire & Security Gmbh Heat exchanger for HVAC unit

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JP2020165579A (ja) 2019-03-29 2020-10-08 パナソニックＩｐマネジメント株式会社 熱交換器分流器
JP2020165578A (ja) 2019-03-29 2020-10-08 パナソニックＩｐマネジメント株式会社 熱交換器分流器
JP7372777B2 (ja) * 2019-08-08 2023-11-01 株式会社Uacj 熱交換器および空気調和機
JP2021025746A (ja) * 2019-08-08 2021-02-22 株式会社Uacj 熱交換器および空気調和機
JP7372778B2 (ja) * 2019-08-08 2023-11-01 株式会社Uacj 熱交換器および空気調和機
JP7550573B2 (ja) 2020-09-02 2024-09-13 株式会社Uacj 空気調和機
KR102549339B1 (ko) 2023-01-17 2023-06-29 아세아열기 주식회사 히트파이프용 열교환기

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US20180038661A1 (en) * 2015-06-03 2018-02-08 Bayerische Motoren Werke Aktiengesellschaft Heat Exchanger for a Cooling System, Cooling System, and Assembly
US10473401B2 (en) * 2015-07-28 2019-11-12 Sanden Holdings Corporation Heat exchanger
US20180274820A1 (en) * 2015-12-01 2018-09-27 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US11105538B2 (en) * 2015-12-01 2021-08-31 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US11047625B2 (en) 2018-05-30 2021-06-29 Johnson Controls Technology Company Interlaced heat exchanger
US11614285B2 (en) 2018-05-30 2023-03-28 Johnson Controls Technology Company Interlaced heat exchanger
US12098887B2 (en) 2018-05-30 2024-09-24 Tyco Fire & Security Gmbh Heat exchanger for HVAC unit
US20230204297A1 (en) * 2021-12-23 2023-06-29 Goodman Manufacturing Company, L.P. Heat exchanger assembly and method for hvac system

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CN104620069B (zh) 2016-08-31
KR20150036570A (ko) 2015-04-07
CN104620069A (zh) 2015-05-13

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