WO2021245986A1 - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
WO2021245986A1
WO2021245986A1 PCT/JP2021/004504 JP2021004504W WO2021245986A1 WO 2021245986 A1 WO2021245986 A1 WO 2021245986A1 JP 2021004504 W JP2021004504 W JP 2021004504W WO 2021245986 A1 WO2021245986 A1 WO 2021245986A1
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WO
WIPO (PCT)
Prior art keywords
flow path
heat exchanger
plate fins
header
plate
Prior art date
Application number
PCT/JP2021/004504
Other languages
French (fr)
Japanese (ja)
Inventor
拓也 奥村
健二 名越
憲昭 山本
Original Assignee
パナソニックＩｐマネジメント株式会社
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 パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Priority to EP21817911.7A priority Critical patent/EP4160130A4/en
Priority to CN202180038894.1A priority patent/CN115885150A/en
Publication of WO2021245986A1 publication Critical patent/WO2021245986A1/en

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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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F28D1/03—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 plate-like or laminated conduits
    • F28D1/0308—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other
    • F28D1/0325—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
    • F28D1/0333—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
    • F28D1/0341—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 plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members with U-flow or serpentine-flow inside the conduits
    • 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
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each 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
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2225/00—Reinforcing means
    • F28F2225/04—Reinforcing means for conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/26—Safety or protection arrangements; Arrangements for preventing malfunction for allowing differential expansion between elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • This disclosure relates to a plate fin laminated heat exchanger.
  • Patent Document 1 discloses a conventional plate fin laminated heat exchanger. As shown in FIGS. 7 and 8, this plate fin laminated heat exchanger has a plate fin laminated body 102 in which plate fins 101 having a flow path through which a first fluid such as a refrigerant flows flows, and a plate fin laminated body 102.
  • the end plates 103 are laminated and arranged on both sides of the body 102, and the inflow / outflow pipes 104 and 105 through which the first fluid flowing through the flow path of the plate fin laminated body 102 flows in and out.
  • the second fluid flows between the stacks of the plate fins 101 of the plate fin laminate 102, so that heat exchange is performed between the first fluid and the second fluid.
  • Through holes 107 are provided at appropriate positions on the peripheral edge of the header region 106, which is the entrance / exit portion of the flow path of the first fluid of the plate fin laminated body 102.
  • the header region portion of each plate fin 101 is connected and fixed by passing the bolt 109 through the through hole 107 via the reinforcing plate 108.
  • the present disclosure provides a plate fin laminated heat exchanger that suppresses deformation of the plate fin due to insufficient strength of the connection and fixing while simplifying the configuration of the connection and fixing of the header region portion of the plate fin.
  • the plate fin laminated heat exchanger in the present disclosure has a tubular portion provided at an appropriate position on the peripheral edge of the header region portion of the plate fin.
  • the header areas of the plate fins are connected and fixed by fitting the tubular portions of the adjacent plate fins to each other.
  • FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment.
  • FIG. 2 is an enlarged perspective view showing a header region of the heat exchanger.
  • FIG. 3 is an enlarged cross-sectional view showing a header region of the heat exchanger.
  • FIG. 4 is an enlarged cross-sectional view showing a main part of the header region of the heat exchanger.
  • FIG. 5 is an enlarged cross-sectional view of the portion shown by A in FIG.
  • FIG. 6 is an exploded perspective view of the plate fins of the heat exchanger according to the first embodiment.
  • FIG. 7 is a perspective view of a conventional plate fin laminated heat exchanger.
  • FIG. 8 is a perspective view showing a state of the conventional plate fin laminated heat exchanger before connecting and fixing the header region.
  • the plate fin laminated heat exchanger described in Patent Document 1 is a heat exchanger proposed by the present inventors.
  • the header region 106 in which the first fluid such as the refrigerant flowing in the flow path gathers is deformed by the pressure of the first fluid. Since it is easy, the reinforcing plate 108 is applied to the outer surface of the header region 106, and the header region 106 portion is connected and fixed by the bolt 109.
  • the reinforcing plate 108 and the bolt 109 and the like are required in the conventional configuration, so that the configuration is complicated and the weight of the entire heat exchanger increases, and the reinforcing plate 108 and the bolt 109 are required. It was found that there is a problem that productivity is reduced due to the need for assembly work.
  • the present disclosure provides a heat exchanger with improved reliability by suppressing deformation of the header region portion of the plate fin while simplifying the configuration of connecting and fixing the header region portion of the plate fin.
  • the heat exchanger of the present disclosure is not limited to the configuration of the plate fin laminated heat exchanger described in the following embodiments, and has the same heat as the technical idea described in the following embodiments. It includes the configuration of the exchanger.
  • FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger (hereinafter, simply referred to as a heat exchanger) 1 of the first embodiment
  • FIG. 2 is an enlarged view showing a header region of the plate fin laminated heat exchanger.
  • a perspective view FIG. 3 is an enlarged sectional view showing a header region of the plate fin laminated heat exchanger
  • FIG. 4 is an enlarged sectional view of a main part of the header region of the plate fin laminated heat exchanger
  • FIG. 5 is FIG.
  • FIG. 6 is an enlarged cross-sectional view of the portion shown by A
  • FIG. 6 is an exploded perspective view of the plate fins of the plate fin laminated heat exchanger according to the first embodiment.
  • the heat exchanger 1 of the present embodiment includes an inflow pipe (inlet header) 2, a plate fin laminate 4 formed by laminating a plurality of plate fins 3, and a plate. It has an outflow pipe (outlet header) 5 for discharging the refrigerant flowing through the flow path in the fin 3.
  • the refrigerant which is the first fluid, flows into the inflow pipe (inlet header) 2.
  • the plurality of plate fins 3 have a rectangular plate shape.
  • End plates 6a and 6b are provided on both sides (upper side and lower side in FIG. 1) of the plate fin laminated body 4 in the laminating direction.
  • the shapes of the end plates 6a and 6b and the shapes of the plate fins 3 are substantially the same in plan view.
  • the end plates 6a and 6b are made of a rigid plate material, and are formed by grinding a metal material such as aluminum, an aluminum alloy, or stainless steel.
  • the end plates 6a and 6b and the plurality of plate fins 3 are joined and integrated by brazing in a laminated state.
  • the end plates 6a, 6b and the plurality of plate fins 3 may be joined by another heat-resistant fixing method, or may be joined by using, for example, a chemical joining member.
  • the plate fins 3 are connected and fixed at both ends in the longitudinal direction of the plate fin laminated body 4.
  • the configuration of connecting and fixing the plate fin laminated body 4 will be described later.
  • the plate fin 3 is configured by joining a pair of long plates 3a and 3b by brazing.
  • the pair of plates 3a and 3b have a concave groove serving as a flow path 7.
  • an inflow header flow path 9 and an outflow header flow path 10 connected to the flow path 7 via the connecting path 8 are formed.
  • the flow paths 7 provided in the plates 3a and 3b are arranged along the longitudinal direction of the plates 3a and 3b.
  • the flow path 7 is configured to make a U-turn at the ends of the plates 3a and 3b.
  • an inflow header flow path 9 connected to the outward flow path 7a and an outflow header flow path 10 connected to the return flow path 7b are collectively arranged.
  • a slit 11 is formed between the forward flow path 7a and the return flow path 7b to suppress heat transfer between the first fluid flowing through the forward flow path 7a and the first fluid flowing through the return flow path 7b.
  • the plate fin laminated body 4 is formed by laminating and brazing the plate fins 3 together with the end plates 6a and 6b.
  • the inflow pipe 2 and the outflow pipe 5 are connected to the inflow header flow path 9 and the outflow header flow path 10 of the plate fin laminated body 4, respectively.
  • a through hole 12 is provided at the peripheral edge of the header region X where the inflow header flow path 9 and the outflow header flow path 10 of the plate fin 3 are located (for example, FIG. 3 and FIG. 6).
  • the tubular portion 13 is erected and arranged in the portions of the pair of plates 3a and 3b provided with the through holes 12.
  • the through hole 12 is arranged inside the wall surface constituting the tubular portion 13.
  • the tubular portion 13 is arranged so as to project outward from each of the pair of plates 3a and 3b.
  • the tubular portion 13 is fitted with the tubular portion 13 of another plate fin 3 adjacent in the stacking direction.
  • the header regions X (see FIG. 1 and the like) of the adjacent plate fins 3 are connected and fixed to each other.
  • the tubular portion 13 is formed so as to project on a surface opposite to the brazed surface of the plates 3a and 3b to which the brazing material is previously applied.
  • the tubular portions 13 of the adjacent plate fins 3 are fitted to each other, and the brazed material on the brazed surface of the inner peripheral surface of one of the tubular portions 13 is melted and solidified to integrate the tubular portions 13 with each other.
  • the header region X of the plate fin laminated body 4 formed by laminating the plate fins 3 of the above is connected and fixed.
  • a similar through hole 12 is provided at the end of each plate fin 3 on the opposite side of the header region X, and a tubular portion 13 is formed. By fitting and brazing the tubular portions 13, the end portions of the plate fin laminated body 4 formed by laminating the plate fins 3 are connected and fixed.
  • the tubular portion 13 erected in the through hole 12 is arranged so as to surround the inflow header flow path 9 or the outflow header flow path 10.
  • each tubular portion 13 is provided on a line connecting substantially the centers of the inflow header flow path 9 and the outflow header flow path 10.
  • the tubular portion 13 is provided so that at least a part of the outer periphery of the tubular portion 13 overlaps on a line connecting substantially the centers of the outflow header flow path 10 and the outflow header flow path 10.
  • the fitting clearance between the tubular portions 13 of the adjacent plate fins 3 is 0.2 mm or less, preferably 0.2 mm to 0.1 mm.
  • At least one of the tubular portions 13 to be fitted is the tubular portion 13, and in the example shown in FIG. 6, the tubular portion 13 of the upper plate 3a of the pair of plates 3a and 3b. Is formed in the shape of a tapered tip.
  • a gas-liquid two-phase state refrigerant which is the first fluid is introduced from the inflow pipe 2 to the plate fin laminated body 4.
  • Inflow into the inflow header flow path 9 The refrigerant that has flowed into the inflow header flow path 9 flows to the outbound flow path 7a group via the connecting path 8 of each plate fin 3.
  • the refrigerant flowing through the forward flow path 7a group of each plate fin 3 makes a U-turn and flows out from the outflow pipe 5 to the refrigerant circuit of the refrigeration system in the gas phase state through the return flow path 7b.
  • the refrigerant exchanges heat with the air (second fluid) that passes between the stacks of the plate fins 3 of the plate fin laminate 4 when flowing through the outbound flow path 7a.
  • the heat transfer between the refrigerant flowing in the forward flow path 7a group and the refrigerant flowing in the return flow path 7b is suppressed by the slit 11, so that high heat exchange efficiency is exhibited.
  • the heat exchanger 1 is used as a condenser, the flow of the first fluid is in the opposite direction to that when it is used as an evaporator. That is, the inflow pipe 2 and the inflow header flow path 9 are the outflow pipe and the outflow header flow path, respectively, and the outflow pipe 5 and the outflow header flow path 10 are the inflow pipe and the inflow header flow path, respectively.
  • the heat exchanger 1 of the present embodiment can be a highly reliable heat exchanger because the header region X portion is firmly connected and fixed to suppress the deformation of the header region X portion. ..
  • the cylinder portion 13 is provided in the header region X portion of each of the plates 3a and 3b forming the plate fins 3, respectively.
  • the tubular portions 13 of the adjacent plate fins 3 are fitted and brazed to each other.
  • the header region X portions of the adjacent plate fins 3 are connected and fixed to each other.
  • the tubular portions 13 of the adjacent plate fins 3 are fitted to each other, and the tubular portions 13 are connected in a columnar shape in the stacking direction. Further, since the cylinder portions 13 are joined to each other with a brazing material, the joining strength is further increased by the solidified brazing material, and a more robust fixing structure is obtained. Therefore, the connection strength of the header region portion can be greatly improved, the rigidity of the plate fin laminate can be improved, and a highly reliable heat exchanger can be obtained.
  • the configuration should be simplified as compared with the conventional heat exchanger using the reinforcing plate and bolts or the like. Can be done.
  • the header region X is connected only by inserting the guide pin jig into the through hole 12, laminating the plates 3a and 3b, putting them in the melting furnace as they are, and brazing them. Can be fixed. The man-hours required for assembling using reinforcing plates and bolts separately from the brazing work, which is required in the conventional configuration, can be reduced, and the workability at the time of manufacturing is greatly improved. Therefore, the productivity of the heat exchanger is greatly improved.
  • the tubular portion 13 is arranged so as to surround each of the inflow header flow path 9 and the outflow header flow path 10. Therefore, even if a high pressure is applied around the inflow header flow path 9 and the outflow header flow path 10 of each of the plates 3a and 3b, that is, in the header region X portion due to the concentrated flow of many first fluids, the inflow occurs.
  • the pressure resistance around the header flow path 9 and the pressure resistance around the outflow header flow path 10 can be improved substantially evenly to increase the pressure resistance of the entire header region X portion.
  • each cylinder portion 13 is provided so that at least the outer periphery of the cylinder portion 13 overlaps on a line connecting substantially the centers of the inflow header flow path 9 and the outflow header flow path 10. ing. Therefore, the header region X portion is connected by the tubular portion 13 in the vicinity of the line connecting the substantially centers of the inflow header flow path 9 and the outflow header flow path 10, and the pressure resistance of the header region X portion is more evenly distributed. Moreover, it can be surely improved and the deformation of the plate fin 3 can be prevented.
  • At least one of the tubular portions 13 provided on the pair of plates 3a and 3b is tapered.
  • the cylinders 13 are surely in contact with each other at least in a part thereof, so that the cylinders 13 can be surely fixed with the brazing material. Therefore, the connection strength of the header region X portion becomes strong, and the pressure resistance can be improved more reliably.
  • the fitting clearance between the tubular portions 13 to be fitted is set to 0.2 mm or less, and in the example of this embodiment, it is set to be in the range of 0.2 mm to 0.1 mm.
  • the molten wax material wraps around the entire circumference of the cylinders 13 substantially uniformly between the cylinders 13 and solidifies. Therefore, the strength of the joint portion between the tubular portions 13 including the brazing material is surely improved, and the pressure resistance of the header region X portion can be more reliably improved.
  • the first embodiment has been described as an example of the technique in the present disclosure.
  • the technique in the present disclosure is not limited to this, and can be applied to embodiments in which changes, replacements, additions, omissions, etc. have been made. Further, it is also possible to combine the components described in the first embodiment to form a new embodiment.
  • the flow path 7 through which the first fluid flows is made a U-turn
  • the inflow header flow path 9 connected to the outward flow path 7a and the outflow flow path 7b connected to the return flow path 7b are on one end side of the plate fin 3.
  • An example is a heat exchanger having a configuration in which the header flow paths 10 are collectively provided.
  • the flow path 7 is arranged in a straight line without making a U-turn
  • the inflow header flow path 9 is provided on one end side of the plate fin 3
  • the outflow header flow path 10 is provided on the other end side of the plate fin 3. It may be provided.
  • a tubular portion 13 may be provided so as to surround the inflow header flow path 9 and the outflow header flow path 10, respectively, so that the plate fins 3 may be connected and fixed to each other.
  • the tubular portion 13 provided on the pair of plates 3a and 3b constituting the plate fin 3 has been described as a tubular portion having a circular cross section.
  • the cross-sectional shape of the tubular portion is not limited to a circle, and may be any shape such as a polygon such as a hexagon or an ellipse.
  • the tubular portion may be a tubular portion having a discontinuous wall surface with a cut, such as the tubular portion 13a provided in the middle of the slit 11 shown in FIG.
  • At least one of the tubular portions 13 of the adjacent plate fins 3 has a tapered shape.
  • the tubular portions 13 of the adjacent plate fins 3 may not be tapered.
  • both of the tubular portions 13 of the adjacent plate fins 3 may be tapered.
  • the taper angles of the two tubular portions 13 to be fitted are slightly different from each other.
  • the tip portion of one of the tubular portions 13 of the adjacent plate fins 3 may be nested.
  • the heat exchanger of the present disclosure is arranged so as to be laminated on both sides of the plate fin laminated body in which the plate fins having the flow path through which the first fluid such as the refrigerant flows are laminated and the plate fin laminated body.
  • the end plate is provided with an inflow header flow path and an outflow header flow path through which the first fluid flowing through the flow path of the plate fin laminate passes.
  • the second fluid flows between the stacks of the plate fins of the plate fin laminate, so that heat exchange is performed between the first fluid and the second fluid.
  • the plate fins are formed by joining a pair of plates by brazing, and a flow path is formed between the pair of plates.
  • a tubular portion is provided at an appropriate position on the peripheral edge of the header region portion of the plate fin provided with the inflow header flow path and the outflow header flow path connected to the flow path.
  • the tubular portions of adjacent plate fins are fitted to each other.
  • the tubular portions of the adjacent plate fins are brazed to each other, and the header region is connected and fixed.
  • connection strength of the header region portion can be improved with a simple configuration without using a reinforcing plate, bolts, etc., and the rigidity of the plate fin laminate can be improved, and a highly reliable heat exchanger can be obtained. be able to.
  • the cylinder portion is provided so as to surround the inflow header flow path and the outflow header flow path. This makes it possible to more reliably improve the pressure resistance of the header region portion.
  • At least one of the cylinders provided on the pair of plates has a tapered or nesting shape. As a result, the bonding between the cylinder portions becomes more reliable, and the pressure resistance of the header region portion can be improved more reliably.
  • the fitting clearance between the tubular portions arranged on the adjacent plate fins and mating with each other is 0.2 mm or less. As a result, the bonding between the cylinder portions becomes more reliable, and the pressure resistance of the header region portion can be further reliably improved.
  • the heat exchanger of the present disclosure can be a highly reliable heat exchanger by improving the connection strength of the header region portion of the plate fins and improving the rigidity of the plate fin laminate with a simple configuration. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and has great industrial value.

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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)

Abstract

This heat exchanger comprises a plate fin stack (4) configured by stacking plate fins (3) each of which has a flow path for the flow of a first fluid such as a refrigerant. Each plate fin (3) comprises a pair of brazed plates, and the flow path is formed between the pair of plates. A cylindrical part (13) which projects toward the outside of each pair of plates is provided at a header region X portion that is connected to the flow path of the plate fin (3). Cylindrical parts (13) of adjacent plate fins (3) are engaged and brazed to connect and fix header region X portions of the adjacent plate fins (3) together.

Description

熱交換器Heat exchanger
　本開示は、プレートフィン積層型の熱交換器に関する。 This disclosure relates to a plate fin laminated heat exchanger.
　特許文献１は、従来のプレートフィン積層型の熱交換器を開示する。このプレートフィン積層型の熱交換器は、図７及び図８に示すように、冷媒等の第１流体が流れる流路を有するプレートフィン１０１が積層されたプレートフィン積層体１０２と、プレートフィン積層体１０２の両側部に積層して配置されたエンドプレート１０３と、プレートフィン積層体１０２の流路を流れる第１流体が流入し又は流出する流入出管１０４，１０５と、を備える。プレートフィン積層体１０２の各プレートフィン１０１の積層間に第２流体が流れることで、第１流体と第２流体との間で熱交換が行われる。プレートフィン積層体１０２の第１流体の流路の出入り口部分となるヘッダ領域１０６の周縁の適所に貫通孔１０７が設けられている。補強プレート１０８を介して貫通孔１０７にボルト１０９を通すことで、各プレートフィン１０１のヘッダ領域部分が連結固定されている。 Patent Document 1 discloses a conventional plate fin laminated heat exchanger. As shown in FIGS. 7 and 8, this plate fin laminated heat exchanger has a plate fin laminated body 102 in which plate fins 101 having a flow path through which a first fluid such as a refrigerant flows flows, and a plate fin laminated body 102. The end plates 103 are laminated and arranged on both sides of the body 102, and the inflow / outflow pipes 104 and 105 through which the first fluid flowing through the flow path of the plate fin laminated body 102 flows in and out. The second fluid flows between the stacks of the plate fins 101 of the plate fin laminate 102, so that heat exchange is performed between the first fluid and the second fluid. Through holes 107 are provided at appropriate positions on the peripheral edge of the header region 106, which is the entrance / exit portion of the flow path of the first fluid of the plate fin laminated body 102. The header region portion of each plate fin 101 is connected and fixed by passing the bolt 109 through the through hole 107 via the reinforcing plate 108.
国際公開第２０１８／０７４３４２号International Publication No. 2018/074342
　本開示は、プレートフィンのヘッダ領域部分の連結固定の構成を簡素化しつつ、連結固定の強度不足によるプレートフィンの変形を抑制したプレートフィン積層型の熱交換器を提供する。 The present disclosure provides a plate fin laminated heat exchanger that suppresses deformation of the plate fin due to insufficient strength of the connection and fixing while simplifying the configuration of the connection and fixing of the header region portion of the plate fin.
　本開示におけるプレートフィン積層型の熱交換器は、プレートフィンのヘッダ領域部分の周縁の適所に設けられた筒部を有する。隣接するプレートフィンの筒部同士が嵌合されることでプレートフィンのヘッダ領域が連結固定される。 The plate fin laminated heat exchanger in the present disclosure has a tubular portion provided at an appropriate position on the peripheral edge of the header region portion of the plate fin. The header areas of the plate fins are connected and fixed by fitting the tubular portions of the adjacent plate fins to each other.
図１は、実施の形態１におけるプレートフィン積層型の熱交換器の外観を示す斜視図である。FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger according to the first embodiment. 図２は、同熱交換器のヘッダ領域を示す拡大斜視図である。FIG. 2 is an enlarged perspective view showing a header region of the heat exchanger. 図３は、同熱交換器のヘッダ領域を示す拡大断面図である。FIG. 3 is an enlarged cross-sectional view showing a header region of the heat exchanger. 図４は、同熱交換器のヘッダ領域の要部を示す拡大断面図である。FIG. 4 is an enlarged cross-sectional view showing a main part of the header region of the heat exchanger. 図５は、図４のＡで示す部分の拡大断面図である。FIG. 5 is an enlarged cross-sectional view of the portion shown by A in FIG. 図６は、実施の形態１における熱交換器のプレートフィンの分解斜視図である。FIG. 6 is an exploded perspective view of the plate fins of the heat exchanger according to the first embodiment. 図７は、従来のプレートフィン積層型熱交換器の斜視図である。FIG. 7 is a perspective view of a conventional plate fin laminated heat exchanger. 図８は、従来のプレートフィン積層型熱交換器について、ヘッダ領域を連結固定する前の状態を示す斜視図である。FIG. 8 is a perspective view showing a state of the conventional plate fin laminated heat exchanger before connecting and fixing the header region.
　（本開示の基礎となった知見等）
　特許文献１に記載されたプレートフィン積層型熱交換器は、本発明者らが提案した熱交換器である。発明者らが本開示に想到するに至った当時、特許文献１に記載の熱交換器においては、流路を流れる冷媒等の第１流体が集まるヘッダ領域１０６が第１流体の圧力で変形しやすいことから、当該ヘッダ領域１０６の外面に補強プレート１０８をあてがってボルト１０９によりヘッダ領域１０６部分を連結固定している。発明者らの鋭意検討の結果、当該従来の構成においては、補強プレート１０８及びボルト１０９等が必要であるため、構成が複雑で熱交換器全体の重量が増加するとともに、補強プレート１０８及びボルト１０９についての組み立て作業が必要となって生産性が低下する、という課題があることを見出した。 (Knowledge, etc. that became the basis of this disclosure)
The plate fin laminated heat exchanger described in Patent Document 1 is a heat exchanger proposed by the present inventors. At the time when the inventors came to the present disclosure, in the heat exchanger described in Patent Document 1, the header region 106 in which the first fluid such as the refrigerant flowing in the flow path gathers is deformed by the pressure of the first fluid. Since it is easy, the reinforcing plate 108 is applied to the outer surface of the header region 106, and the header region 106 portion is connected and fixed by the bolt 109. As a result of diligent studies by the inventors, the reinforcing plate 108 and the bolt 109 and the like are required in the conventional configuration, so that the configuration is complicated and the weight of the entire heat exchanger increases, and the reinforcing plate 108 and the bolt 109 are required. It was found that there is a problem that productivity is reduced due to the need for assembly work.
　発明者らはこのような課題に鑑み、本開示の主題を構成するに至った。 In view of these issues, the inventors have come to construct the subject matter of the present disclosure.
　本開示は、プレートフィンのヘッダ領域部分の連結固定の構成を簡素化しつつ、プレートフィンのヘッダ領域部分の変形を抑制して信頼性を高めた熱交換器を提供する。 The present disclosure provides a heat exchanger with improved reliability by suppressing deformation of the header region portion of the plate fin while simplifying the configuration of connecting and fixing the header region portion of the plate fin.
　以下、図面を参照しながら、実施の形態を詳細に説明する。但し、必要以上に詳細な説明は省略する場合がある。例えば、既によく知られた事項の詳細説明、または、変形例においても実質的に同一の構成に対しては同じ符号を付して、重複説明を省略する場合がある。これは、以下の説明が必要以上に冗長になるのを避け、当業者の理解を容易にするためである。 Hereinafter, embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanations of already well-known matters, or even in modified examples, the same reference numerals may be given to substantially the same configuration, and duplicate explanations may be omitted. This is to prevent the following explanation from becoming unnecessarily redundant and to facilitate the understanding of those skilled in the art.
　なお、本開示の熱交換器は、以下の実施の形態に記載したプレートフィン積層型熱交換器の構成に限定されるものではなく、以下の実施の形態において説明する技術的思想と同等の熱交換器の構成を含むものである。 The heat exchanger of the present disclosure is not limited to the configuration of the plate fin laminated heat exchanger described in the following embodiments, and has the same heat as the technical idea described in the following embodiments. It includes the configuration of the exchanger.
　また、以下で説明する実施の形態は、本開示の一例を示すものであって、実施の形態において示される構成、機能及び動作などは例示であり、本開示を限定するものではない。 Further, the embodiments described below are examples of the present disclosure, and the configurations, functions, operations, and the like shown in the embodiments are examples, and the present disclosure is not limited.
　（実施の形態１）
　以下、本開示の熱交換器に係る実施の形態１について、図１～図６を用いて説明する。 (Embodiment 1)
Hereinafter, the first embodiment of the heat exchanger of the present disclosure will be described with reference to FIGS. 1 to 6.
　［１－１．構成］
　図１は実施の形態１のプレートフィン積層型熱交換器（以下、単に熱交換器と称する）１の外観を示す斜視図、図２は同プレートフィン積層型熱交換器のヘッダ領域を示す拡大斜視図、図３は同プレートフィン積層型熱交換器のヘッダ領域を示す拡大断面図、図４は同プレートフィン積層型熱交換器のヘッダ領域の要部の拡大断面図、図５は図４のＡで示す部分の拡大断面図、及び図６は同実施の形態１におけるプレートフィン積層型熱交換器のプレートフィンの分解斜視図である。 [1-1. composition]
FIG. 1 is a perspective view showing the appearance of the plate fin laminated heat exchanger (hereinafter, simply referred to as a heat exchanger) 1 of the first embodiment, and FIG. 2 is an enlarged view showing a header region of the plate fin laminated heat exchanger. A perspective view, FIG. 3 is an enlarged sectional view showing a header region of the plate fin laminated heat exchanger, FIG. 4 is an enlarged sectional view of a main part of the header region of the plate fin laminated heat exchanger, and FIG. 5 is FIG. FIG. 6 is an enlarged cross-sectional view of the portion shown by A, and FIG. 6 is an exploded perspective view of the plate fins of the plate fin laminated heat exchanger according to the first embodiment.
　図１～図６に示すように、本実施の形態の熱交換器１は、流入管（入口ヘッダ）２と、複数のプレートフィン３が積層されて構成されたプレートフィン積層体４と、プレートフィン３の中の流路を流れた冷媒を排出する流出管（出口ヘッダ）５と、を有する。流入管（入口ヘッダ）２には、第１流体である冷媒が流入する。本実施の形態の例では、複数のプレートフィン３は長方形の板状である。 As shown in FIGS. 1 to 6, the heat exchanger 1 of the present embodiment includes an inflow pipe (inlet header) 2, a plate fin laminate 4 formed by laminating a plurality of plate fins 3, and a plate. It has an outflow pipe (outlet header) 5 for discharging the refrigerant flowing through the flow path in the fin 3. The refrigerant, which is the first fluid, flows into the inflow pipe (inlet header) 2. In the example of this embodiment, the plurality of plate fins 3 have a rectangular plate shape.
　プレートフィン積層体４の積層方向の両側（図１では上側及び下側）には、エンドプレート６ａ，６ｂが設けられている。エンドプレート６ａ，６ｂの形状とプレートフィン３の形状とは、平面視において略同一形状である。エンドプレート６ａ，６ｂは、剛性を有する板材で形成されており、例えばアルミニウム、アルミニウム合金又はステンレスなどの金属材を研削により加工することで形成されている。 End plates 6a and 6b are provided on both sides (upper side and lower side in FIG. 1) of the plate fin laminated body 4 in the laminating direction. The shapes of the end plates 6a and 6b and the shapes of the plate fins 3 are substantially the same in plan view. The end plates 6a and 6b are made of a rigid plate material, and are formed by grinding a metal material such as aluminum, an aluminum alloy, or stainless steel.
　なお、上記エンドプレート６ａ，６ｂ及び複数のプレートフィン３は、積層された状態でロウ付けにより接合されて一体化されている。エンドプレート６ａ，６ｂ及び複数のプレートフィン３は、他の耐熱性のある固定方法によって接合されていてもよく、例えば化学的な接合部材を用いて接合されていてもよい。 The end plates 6a and 6b and the plurality of plate fins 3 are joined and integrated by brazing in a laminated state. The end plates 6a, 6b and the plurality of plate fins 3 may be joined by another heat-resistant fixing method, or may be joined by using, for example, a chemical joining member.
　また、本実施の形態では、プレートフィン３を積層することで構成されたプレートフィン積層体４は、プレートフィン積層体４の長手方向の両端部においてプレートフィン３が連結固定されている。プレートフィン積層体４の連結固定の構成は後述する。 Further, in the present embodiment, in the plate fin laminated body 4 configured by laminating the plate fins 3, the plate fins 3 are connected and fixed at both ends in the longitudinal direction of the plate fin laminated body 4. The configuration of connecting and fixing the plate fin laminated body 4 will be described later.
　なお、プレートフィン３は、図６に示すように一対の長尺状のプレート３ａ，３ｂがロウ付けにより接合されて構成されている。一対のプレート３ａ，３ｂは、流路７となる凹溝を有する。一対のプレート３ａ，３ｂが接合されることによって、連絡路８を介して流路７に繋がる流入用ヘッダ流路９、及び流出用ヘッダ流路１０が形成される。プレート３ａ，３ｂに設けられた流路７は、プレート３ａ，３ｂの長手方向に沿って配置されている。流路７は、プレート３ａ，３ｂの端部でＵターンするように構成されている。プレート３ａ，３ｂの一端側には、往き流路７ａに繋がる流入用ヘッダ流路９及びに戻り流路７ｂに繋がる流出用ヘッダ流路１０が纏めて配置されている。往き流路７ａと戻り流路７ｂとの間には、往き流路７ａを流れる第１流体と戻り流路７ｂを流れる第１流体との間の熱移動を抑制するスリット１１が形成されている。既述したように、プレートフィン３がエンドプレート６ａ，６ｂとともに積層されてロウ付けされることでプレートフィン積層体４が構成されている。プレートフィン積層体４の流入用ヘッダ流路９及び流出用ヘッダ流路１０に流入管２及び流出管５が各々接続されている。 As shown in FIG. 6, the plate fin 3 is configured by joining a pair of long plates 3a and 3b by brazing. The pair of plates 3a and 3b have a concave groove serving as a flow path 7. By joining the pair of plates 3a and 3b, an inflow header flow path 9 and an outflow header flow path 10 connected to the flow path 7 via the connecting path 8 are formed. The flow paths 7 provided in the plates 3a and 3b are arranged along the longitudinal direction of the plates 3a and 3b. The flow path 7 is configured to make a U-turn at the ends of the plates 3a and 3b. On one end side of the plates 3a and 3b, an inflow header flow path 9 connected to the outward flow path 7a and an outflow header flow path 10 connected to the return flow path 7b are collectively arranged. A slit 11 is formed between the forward flow path 7a and the return flow path 7b to suppress heat transfer between the first fluid flowing through the forward flow path 7a and the first fluid flowing through the return flow path 7b. .. As described above, the plate fin laminated body 4 is formed by laminating and brazing the plate fins 3 together with the end plates 6a and 6b. The inflow pipe 2 and the outflow pipe 5 are connected to the inflow header flow path 9 and the outflow header flow path 10 of the plate fin laminated body 4, respectively.
　次に、プレートフィン積層体４の両端部の連結固定の構成について説明する。本実施の形態のプレートフィン３においては、プレートフィン３の流入用ヘッダ流路９及び流出用ヘッダ流路１０が位置するヘッダ領域Ｘの周縁部に貫通孔１２が設けてられている（例えば図３及び図６参照）。図６に示すように、貫通孔１２の設けられた一対のプレート３ａ，３ｂの部分に筒部１３が立設して配置されている。言い換えると、筒部１３を構成する壁面の内側に貫通孔１２が配置されている。筒部１３は、一対のプレート３ａ，３ｂ各々の外側へ突出して配置されている。この筒部１３が図４及び図５に示すように、積層方向に隣接する他のプレートフィン３の筒部１３と嵌合される。隣接するプレートフィン３の筒部１３同士がロウ付けされることにより、隣接するプレートフィン３のヘッダ領域Ｘ（図１等参照）が互いに連結されて固定されている。筒部１３は、あらかじめロウ材が塗布されているプレート３ａ，３ｂのロウ付け面とは反対側の面に、突出して形成されている。隣接するプレートフィン３の筒部１３同士が嵌合され、いずれか一方の筒部１３の内周面のロウ付け面のロウ材が溶融固化して筒部１３同士が一体化することで、複数のプレートフィン３が積層されて構成したプレートフィン積層体４のヘッダ領域Ｘが連結固定される。 Next, the configuration of connecting and fixing both ends of the plate fin laminate 4 will be described. In the plate fin 3 of the present embodiment, a through hole 12 is provided at the peripheral edge of the header region X where the inflow header flow path 9 and the outflow header flow path 10 of the plate fin 3 are located (for example, FIG. 3 and FIG. 6). As shown in FIG. 6, the tubular portion 13 is erected and arranged in the portions of the pair of plates 3a and 3b provided with the through holes 12. In other words, the through hole 12 is arranged inside the wall surface constituting the tubular portion 13. The tubular portion 13 is arranged so as to project outward from each of the pair of plates 3a and 3b. As shown in FIGS. 4 and 5, the tubular portion 13 is fitted with the tubular portion 13 of another plate fin 3 adjacent in the stacking direction. By brazing the tubular portions 13 of the adjacent plate fins 3, the header regions X (see FIG. 1 and the like) of the adjacent plate fins 3 are connected and fixed to each other. The tubular portion 13 is formed so as to project on a surface opposite to the brazed surface of the plates 3a and 3b to which the brazing material is previously applied. The tubular portions 13 of the adjacent plate fins 3 are fitted to each other, and the brazed material on the brazed surface of the inner peripheral surface of one of the tubular portions 13 is melted and solidified to integrate the tubular portions 13 with each other. The header region X of the plate fin laminated body 4 formed by laminating the plate fins 3 of the above is connected and fixed.
　なお、各プレートフィン３のヘッダ領域Ｘとは反対側の端部にも、図示はしないが同様の貫通孔１２が設けられているとともに、筒部１３が形成されている。この筒部１３同士が嵌合されてロウ付けされることで、各プレートフィン３が積層されて構成されたプレートフィン積層体４の端部が連結固定されている。 Although not shown, a similar through hole 12 is provided at the end of each plate fin 3 on the opposite side of the header region X, and a tubular portion 13 is formed. By fitting and brazing the tubular portions 13, the end portions of the plate fin laminated body 4 formed by laminating the plate fins 3 are connected and fixed.
　貫通孔１２に立設された筒部１３は、図６に示すように、流入用ヘッダ流路９又は流出用ヘッダ流路１０を取り囲むように配置されている。図６に示す例では、各筒部１３は流入用ヘッダ流路９及び流出用ヘッダ流路１０の各々の略中心を結ぶ線上に設けられている。具体的には、筒部１３は、流出用ヘッダ流路１０及び流出用ヘッダ流路１０のそれぞれの略中心を結ぶ線上に筒部１３の外周の少なくとも一部がオーバーラップするように設けられている。隣接するプレートフィン３の筒部１３同士の嵌合クリアランスは、０．２ｍｍ以下、好ましくは０．２ｍｍ～０．１ｍｍである。 As shown in FIG. 6, the tubular portion 13 erected in the through hole 12 is arranged so as to surround the inflow header flow path 9 or the outflow header flow path 10. In the example shown in FIG. 6, each tubular portion 13 is provided on a line connecting substantially the centers of the inflow header flow path 9 and the outflow header flow path 10. Specifically, the tubular portion 13 is provided so that at least a part of the outer periphery of the tubular portion 13 overlaps on a line connecting substantially the centers of the outflow header flow path 10 and the outflow header flow path 10. There is. The fitting clearance between the tubular portions 13 of the adjacent plate fins 3 is 0.2 mm or less, preferably 0.2 mm to 0.1 mm.
　なお、本実施の形態の例では、嵌合させる筒部１３同士の少なくともいずれか一方の筒部１３、図６に示す例では一対のプレート３ａ，３ｂのうちの上側のプレート３ａの筒部１３は、先すぼまりのテーパ状に形成されている。 In the example of the present embodiment, at least one of the tubular portions 13 to be fitted is the tubular portion 13, and in the example shown in FIG. 6, the tubular portion 13 of the upper plate 3a of the pair of plates 3a and 3b. Is formed in the shape of a tapered tip.
　［１－２．動作］
　以上のように構成された熱交換器１について、以下その動作、作用について説明する。 [1-2. motion]
The operation and operation of the heat exchanger 1 configured as described above will be described below.
　本実施の形態の熱交換器１は、例えば冷凍システムに組み込まれて蒸発条件で使用される際には、第１流体である気液二相状態の冷媒が流入管２からプレートフィン積層体４の流入用ヘッダ流路９内に流入する。流入用ヘッダ流路９内に流入した冷媒は、各プレートフィン３の連絡路８を介して往き流路７ａ群へ流れる。各プレートフィン３の往き流路７ａ群を流れた冷媒はＵターンし、戻り流路７ｂを介して気相状態で流出管５より冷凍システムの冷媒回路へと流出する。冷媒は、往き流路７ａを流れる際に、プレートフィン積層体４のプレートフィン３の積層間を通り抜ける空気（第２流体）と熱交換する。 When the heat exchanger 1 of the present embodiment is incorporated into a refrigeration system and used under evaporation conditions, for example, a gas-liquid two-phase state refrigerant which is the first fluid is introduced from the inflow pipe 2 to the plate fin laminated body 4. Inflow into the inflow header flow path 9. The refrigerant that has flowed into the inflow header flow path 9 flows to the outbound flow path 7a group via the connecting path 8 of each plate fin 3. The refrigerant flowing through the forward flow path 7a group of each plate fin 3 makes a U-turn and flows out from the outflow pipe 5 to the refrigerant circuit of the refrigeration system in the gas phase state through the return flow path 7b. The refrigerant exchanges heat with the air (second fluid) that passes between the stacks of the plate fins 3 of the plate fin laminate 4 when flowing through the outbound flow path 7a.
　この時、上記往き流路７ａ群を流れる冷媒と戻り流路７ｂを流れる冷媒との間の熱移動は、スリット１１によって抑制されるので、高い熱交換効率が発揮される。なお、熱交換器１が凝縮器として使用される場合、第１流体の流れは蒸発器として使用される場合とは逆向きになる。すなわち、流入管２及び流入用ヘッダ流路９はそれぞれ流出管及び流出用ヘッダ流路となり、流出管５及び流出用ヘッダ流路１０はそれぞれ流入管及び流入用ヘッダ流路となる。 At this time, the heat transfer between the refrigerant flowing in the forward flow path 7a group and the refrigerant flowing in the return flow path 7b is suppressed by the slit 11, so that high heat exchange efficiency is exhibited. When the heat exchanger 1 is used as a condenser, the flow of the first fluid is in the opposite direction to that when it is used as an evaporator. That is, the inflow pipe 2 and the inflow header flow path 9 are the outflow pipe and the outflow header flow path, respectively, and the outflow pipe 5 and the outflow header flow path 10 are the inflow pipe and the inflow header flow path, respectively.
　熱交換器１においては、流入用ヘッダ流路９の開口面積が他の流路の開口面積に比べて大きいため、流入用ヘッダ流路９の配置されるヘッダ領域Ｘ部分に応力が集中してヘッダ領域Ｘ部分が積層方向に大きく変形しようとする。しかしながら、本実施の形態の熱交換器１はヘッダ領域Ｘ部分が強固に連結固定されていることでヘッダ領域Ｘ部分の変形が抑制されるため、信頼性の高い熱交換器とすることができる。 In the heat exchanger 1, since the opening area of the inflow header flow path 9 is larger than the opening area of the other flow paths, stress is concentrated on the header region X portion where the inflow header flow path 9 is arranged. The header area X portion tends to be greatly deformed in the stacking direction. However, the heat exchanger 1 of the present embodiment can be a highly reliable heat exchanger because the header region X portion is firmly connected and fixed to suppress the deformation of the header region X portion. ..
　詳述すると、本実施の形態の熱交換器１は、プレートフィン３を形成する各プレート３ａ，３ｂのヘッダ領域Ｘ部分に筒部１３がそれぞれ設けられている。隣接するプレートフィン３の筒部１３同士が嵌合されてロウ付けされている。これにより、隣接するプレートフィン３のヘッダ領域Ｘ部分同士が連結固定されている。 More specifically, in the heat exchanger 1 of the present embodiment, the cylinder portion 13 is provided in the header region X portion of each of the plates 3a and 3b forming the plate fins 3, respectively. The tubular portions 13 of the adjacent plate fins 3 are fitted and brazed to each other. As a result, the header region X portions of the adjacent plate fins 3 are connected and fixed to each other.
　従って、隣接する各プレートフィン３の筒部１３同士が嵌合して、筒部１３が積層方向に円柱状に繋がった状態になる。さらに、筒部１３同士がロウ材で接合されることで、固形化したロウ材により接合強度がさらに高まり、より堅牢な固定構造となる。よって、ヘッダ領域部分の連結強度を大きく向上させて、プレートフィン積層体の剛性を向上させ、信頼性の高い熱交換器とすることができる。 Therefore, the tubular portions 13 of the adjacent plate fins 3 are fitted to each other, and the tubular portions 13 are connected in a columnar shape in the stacking direction. Further, since the cylinder portions 13 are joined to each other with a brazing material, the joining strength is further increased by the solidified brazing material, and a more robust fixing structure is obtained. Therefore, the connection strength of the header region portion can be greatly improved, the rigidity of the plate fin laminate can be improved, and a highly reliable heat exchanger can be obtained.
　また、従来のようなヘッダ領域部分の連結強度を確保するための補強プレート及びボルト等を必要としないため、補強プレート及びボルト等を用いた従来の熱交換器と比べて構成を簡素化することができる。 In addition, since a reinforcing plate and bolts or the like for ensuring the connection strength of the header region portion as in the conventional case are not required, the configuration should be simplified as compared with the conventional heat exchanger using the reinforcing plate and bolts or the like. Can be done.
　しかも、熱交換器の製造時の作業性も向上するため、生産性を高めることができる。すなわち、本実施の形態の構成によれば、ガイドピン治具を貫通孔１２に挿入して各プレート３ａ，３ｂを積層し、そのまま溶融炉に入れてロウ付けするだけで、ヘッダ領域Ｘを連結固定することができる。従来の構成において必要であった、ロウ付け作業とは別に補強プレート及びボルトを用いて組み立てるという工数が削減でき、製造時の作業性が大幅に向上する。従って、熱交換器の生産性が大きく向上する。 Moreover, the workability at the time of manufacturing the heat exchanger is also improved, so that the productivity can be improved. That is, according to the configuration of the present embodiment, the header region X is connected only by inserting the guide pin jig into the through hole 12, laminating the plates 3a and 3b, putting them in the melting furnace as they are, and brazing them. Can be fixed. The man-hours required for assembling using reinforcing plates and bolts separately from the brazing work, which is required in the conventional configuration, can be reduced, and the workability at the time of manufacturing is greatly improved. Therefore, the productivity of the heat exchanger is greatly improved.
　本実施の形態の熱交換器では、筒部１３は流入用ヘッダ流路９及び流出用ヘッダ流路１０のそれぞれを取り囲むように配置されている。従って、多くの第１流体が集中して流れることで各プレート３ａ，３ｂの流入用ヘッダ流路９及び流出用ヘッダ流路１０の周り、すなわちヘッダ領域Ｘ部分に高い圧力が加わっても、流入用ヘッダ流路９の周りの耐圧性及び流出用ヘッダ流路１０の周りの耐圧性をそれぞれ略均等に向上させてヘッダ領域Ｘ部分全体の耐圧性を高めることができる。本実施の形態の例では、流入用ヘッダ流路９及び流出用ヘッダ流路１０それぞれの略中心を互いに結んだ線上に筒部１３の少なくとも外周がオーバーラップするように各筒部１３が設けられている。従って、流入用ヘッダ流路９及び流出用ヘッダ流路１０それぞれの略中心を結ぶ線上付近においてヘッダ領域Ｘ部分が筒部１３により連結されることになり、ヘッダ領域Ｘ部分の耐圧性をより均等かつ確実に向上させてプレートフィン３の変形を防止することができる。 In the heat exchanger of the present embodiment, the tubular portion 13 is arranged so as to surround each of the inflow header flow path 9 and the outflow header flow path 10. Therefore, even if a high pressure is applied around the inflow header flow path 9 and the outflow header flow path 10 of each of the plates 3a and 3b, that is, in the header region X portion due to the concentrated flow of many first fluids, the inflow occurs. The pressure resistance around the header flow path 9 and the pressure resistance around the outflow header flow path 10 can be improved substantially evenly to increase the pressure resistance of the entire header region X portion. In the example of the present embodiment, each cylinder portion 13 is provided so that at least the outer periphery of the cylinder portion 13 overlaps on a line connecting substantially the centers of the inflow header flow path 9 and the outflow header flow path 10. ing. Therefore, the header region X portion is connected by the tubular portion 13 in the vicinity of the line connecting the substantially centers of the inflow header flow path 9 and the outflow header flow path 10, and the pressure resistance of the header region X portion is more evenly distributed. Moreover, it can be surely improved and the deformation of the plate fin 3 can be prevented.
　なお、本実施の形態の例では、一対のプレート３ａ，３ｂに設けられた筒部１３の少なくともいずれか一方は、テーパ状としている。これにより、嵌合し合った筒部１３に寸法公差があっても筒部１３同士は少なくともそれらの一部分において確実に接触するため、ロウ材で筒部１３同士を確実に固定することができる。したがって、ヘッダ領域Ｘ部分の連結強度が強固なものとなり、耐圧性をより確実に向上させることができる。 In the example of this embodiment, at least one of the tubular portions 13 provided on the pair of plates 3a and 3b is tapered. As a result, even if the fitted cylinders 13 have dimensional tolerances, the cylinders 13 are surely in contact with each other at least in a part thereof, so that the cylinders 13 can be surely fixed with the brazing material. Therefore, the connection strength of the header region X portion becomes strong, and the pressure resistance can be improved more reliably.
　また、嵌合される筒部１３同士の嵌合クリアランスは０．２ｍｍ以下、本実施の形態の例では０．２ｍｍ～０．１ｍｍの範囲になるようにしている。これにより、筒部１３同士の間において、溶融したロウ材が筒部１３の全周に略均一に廻り込んで固化する。したがって、ロウ材を含む筒部１３同士の接合部の強度が確実に向上し、ヘッダ領域Ｘ部分の耐圧性をさらに確実に向上させることができる。 Further, the fitting clearance between the tubular portions 13 to be fitted is set to 0.2 mm or less, and in the example of this embodiment, it is set to be in the range of 0.2 mm to 0.1 mm. As a result, the molten wax material wraps around the entire circumference of the cylinders 13 substantially uniformly between the cylinders 13 and solidifies. Therefore, the strength of the joint portion between the tubular portions 13 including the brazing material is surely improved, and the pressure resistance of the header region X portion can be more reliably improved.
　［他の実施の形態］
　以上のように、本開示における技術の一例として、実施の形態１を用いて説明した。しかしながら、本開示における技術は、これに限定されず、変更、置き換え、付加及び省略などを行った実施の形態にも適用できる。また、上記実施の形態１で説明した各構成要素を組み合わせて、新たな実施の形態とすることも可能である。 [Other embodiments]
As described above, the first embodiment has been described as an example of the technique in the present disclosure. However, the technique in the present disclosure is not limited to this, and can be applied to embodiments in which changes, replacements, additions, omissions, etc. have been made. Further, it is also possible to combine the components described in the first embodiment to form a new embodiment.
　そこで、以下、他の実施の形態を例示する。 Therefore, other embodiments will be exemplified below.
　実施の形態１では、第１流体が流れる流路７をＵターンさせており、プレートフィン３の一端側に、往き流路７ａに繋がる流入用ヘッダ流路９及び戻り流路７ｂに繋がる流出用ヘッダ流路１０を纏めて設けた構成の熱交換器を例示した。しかしながら、流路７をＵターンさせずに直線状に配置して、プレートフィン３の一端側に流入用ヘッダ流路９を設けるとともに、プレートフィン３の他端側に流出用ヘッダ流路１０を設けてもよい。そして、流入用ヘッダ流路９及び流出用ヘッダ流路１０をそれぞれ取り囲むように筒部１３を設けて、プレートフィン３同士を連結固定する構成としてもよい。 In the first embodiment, the flow path 7 through which the first fluid flows is made a U-turn, and the inflow header flow path 9 connected to the outward flow path 7a and the outflow flow path 7b connected to the return flow path 7b are on one end side of the plate fin 3. An example is a heat exchanger having a configuration in which the header flow paths 10 are collectively provided. However, the flow path 7 is arranged in a straight line without making a U-turn, the inflow header flow path 9 is provided on one end side of the plate fin 3, and the outflow header flow path 10 is provided on the other end side of the plate fin 3. It may be provided. Then, a tubular portion 13 may be provided so as to surround the inflow header flow path 9 and the outflow header flow path 10, respectively, so that the plate fins 3 may be connected and fixed to each other.
　なお、実施の形態１においては、プレートフィン３を構成する一対のプレート３ａ，３ｂに設けられた筒部１３は、断面が円形の筒部として説明した。しかしながら、筒部の断面形状は円形に限られず、六角形等の多角形又は楕円形等、どのような形状としてもよい。なお、筒部は、図６において示す、スリット１１の途中に設けられた筒部１３ａのように、切れ目のある非連続な壁面を有する筒部であってもよい。 In the first embodiment, the tubular portion 13 provided on the pair of plates 3a and 3b constituting the plate fin 3 has been described as a tubular portion having a circular cross section. However, the cross-sectional shape of the tubular portion is not limited to a circle, and may be any shape such as a polygon such as a hexagon or an ellipse. The tubular portion may be a tubular portion having a discontinuous wall surface with a cut, such as the tubular portion 13a provided in the middle of the slit 11 shown in FIG.
　なお、実施の形態１においては、隣接するプレートフィン３の筒部１３のうち少なくとも一方の筒部がテーパ状であるものを例示した。しかしながら、隣接するプレートフィン３の筒部１３はともにテーパ状でない構成であってもよい。または、隣接するプレートフィン３の筒部１３の両方がテーパ状であってもよい。この場合は、嵌合する二つの筒部１３のテーパ角を互いに若干異なるものとしておくのが好ましい。或いは、図示しないが、隣接するプレートフィン３の筒部１３のうちの一方の筒部１３の先端部は、ネスティング加工されていてもよい。 In the first embodiment, at least one of the tubular portions 13 of the adjacent plate fins 3 has a tapered shape. However, the tubular portions 13 of the adjacent plate fins 3 may not be tapered. Alternatively, both of the tubular portions 13 of the adjacent plate fins 3 may be tapered. In this case, it is preferable that the taper angles of the two tubular portions 13 to be fitted are slightly different from each other. Alternatively, although not shown, the tip portion of one of the tubular portions 13 of the adjacent plate fins 3 may be nested.
　［１－３．効果等］
　以上のように、本開示の熱交換器は、冷媒等の第１流体が流れる流路を有するプレートフィンが積層されたプレートフィン積層体と、プレートフィン積層体の両側部に積層して配置されたエンドプレートと、プレートフィン積層体の流路を流れる第１流体が通過する流入用ヘッダ流路及び流出用ヘッダ流路と、を備える。プレートフィン積層体の各プレートフィンの積層間に第２流体が流れることで、第１流体と第２流体との間で熱交換が行われる。プレートフィンは一対のプレートがロウ付けにより接合されて構成されており、一対のプレートの間に流路が形成されている。流路に繋がる流入用ヘッダ流路及び流出用ヘッダ流路の設けられたプレートフィンのヘッダ領域部分の周縁の適所には、筒部が設けられている。隣接するプレートフィンの筒部同士が嵌合される。本実施の形態では、隣接するプレートフィンの筒部同士がロウ付けされ、ヘッダ領域が連結固定されている。 [1-3. Effect, etc.]
As described above, the heat exchanger of the present disclosure is arranged so as to be laminated on both sides of the plate fin laminated body in which the plate fins having the flow path through which the first fluid such as the refrigerant flows are laminated and the plate fin laminated body. The end plate is provided with an inflow header flow path and an outflow header flow path through which the first fluid flowing through the flow path of the plate fin laminate passes. The second fluid flows between the stacks of the plate fins of the plate fin laminate, so that heat exchange is performed between the first fluid and the second fluid. The plate fins are formed by joining a pair of plates by brazing, and a flow path is formed between the pair of plates. A tubular portion is provided at an appropriate position on the peripheral edge of the header region portion of the plate fin provided with the inflow header flow path and the outflow header flow path connected to the flow path. The tubular portions of adjacent plate fins are fitted to each other. In the present embodiment, the tubular portions of the adjacent plate fins are brazed to each other, and the header region is connected and fixed.
　これにより、補強プレート及びボルト等を使用することなく簡素な構成でヘッダ領域部分の連結強度を向上させて、プレートフィン積層体の剛性を向上させることができ、信頼性の高い熱交換器を得ることができる。 As a result, the connection strength of the header region portion can be improved with a simple configuration without using a reinforcing plate, bolts, etc., and the rigidity of the plate fin laminate can be improved, and a highly reliable heat exchanger can be obtained. be able to.
　なお、筒部は、流入用ヘッダ流路及び流出用ヘッダ流路を取り囲むように設けるのが好ましい。これによりヘッダ領域部分の耐圧性をより確実に向上させることができる。 It is preferable that the cylinder portion is provided so as to surround the inflow header flow path and the outflow header flow path. This makes it possible to more reliably improve the pressure resistance of the header region portion.
　なお、一対のプレートに設けられた各筒部のうちの少なくとも一方の筒部は、テーパ状或いはネスティング加工した形状としておくのが好ましい。これにより筒部同士の接合がより確実なものとなって、ヘッダ領域部分の耐圧性をより確実に向上させることができる。 It is preferable that at least one of the cylinders provided on the pair of plates has a tapered or nesting shape. As a result, the bonding between the cylinder portions becomes more reliable, and the pressure resistance of the header region portion can be improved more reliably.
　なお、隣接するプレートフィンに配置されて互いに嵌合する筒部同士の嵌合クリアランスは、０．２ｍｍ以下としておくのが好ましい。これにより、筒部同士の接合がより確実なものとなって、ヘッダ領域部分の耐圧性をさらに確実に向上させることができる。 It is preferable that the fitting clearance between the tubular portions arranged on the adjacent plate fins and mating with each other is 0.2 mm or less. As a result, the bonding between the cylinder portions becomes more reliable, and the pressure resistance of the header region portion can be further reliably improved.
　以上、本開示に係るプレートフィン積層型の熱交換器について、上記実施の形態を用いて説明したが、本開示はこれらに限定されるものではない。つまり、今回開示した実施の形態はすべての点で例示であって制限的なものではなく、本開示の範囲は請求の範囲によって示され、請求の範囲と均等の意味及び範囲内でのすべての変更が含まれるものである。 The plate fin laminated heat exchanger according to the present disclosure has been described above using the above-described embodiment, but the present disclosure is not limited thereto. That is, the embodiments disclosed this time are exemplary and not restrictive in all respects, and the scope of the present disclosure is indicated by the scope of claims, meaning and all within the meaning and scope equivalent to the scope of claims. Changes are included.
　本開示の熱交換器は、簡素な構成でプレートフィンのヘッダ領域部分の連結強度を向上させて、プレートフィン積層体の剛性を向上させ、信頼性の高い熱交換器とすることができる。よって、家庭用及び業務用エアコン等に用いる熱交換器や各種冷凍機器等に幅広く利用でき、その産業的価値は大なるものがある。 The heat exchanger of the present disclosure can be a highly reliable heat exchanger by improving the connection strength of the header region portion of the plate fins and improving the rigidity of the plate fin laminate with a simple configuration. Therefore, it can be widely used in heat exchangers and various refrigeration equipment used for home and commercial air conditioners, and has great industrial value.
　１　熱交換器
　２　流入管
　３　プレートフィン
　３ａ，３ｂ　プレート
　４　プレートフィン積層体
　５　流出管
　６ａ，６ｂ　エンドプレート
　７　流路
　７ａ　往き流路
　７ｂ　戻り流路
　８　連絡路
　９　流入用ヘッダ流路
　１０　流出用ヘッダ流路
　１１　スリット
　１２　貫通孔
　１３，１３ａ　筒部 1 Heat exchanger 2 Inflow pipe 3 Plate fin 3a, 3b Plate 4 Plate fin laminate 5 Outflow pipe 6a, 6b End plate 7 Flow path 7a Outward flow path 7b Return flow path 8 Connection path 9 Inflow header flow path 10 Outflow Header flow path 11 Slit 12 Through hole 13, 13a Cylinder

Claims (7)

  1. 　複数のプレートフィンであって第１流体が流れる流路を各々有する複数のプレートフィンが積層されて構成されたプレートフィン積層体と、
    　前記プレートフィン積層体の積層方向における両側部に配置されたエンドプレートと、
    　前記第１流体が前記流路への流入の際に通過する流入用ヘッダ流路、及び前記第１流体が前記流路への流出の際に通過する流出用ヘッダ流路と、を備え、
    　前記複数のプレートフィンの各々は、
    　　一対のプレートがロウ付けされて構成されて、前記一対のプレートの間に前記流路が形成されており、
    　　前記流入用ヘッダ流路及び前記流出用ヘッダ流路の配置されたヘッダ領域部分に配置され、前記一対のプレートの各々の外側へ突出した筒部を有し、
    　前記複数のプレートフィンのうち隣接するプレートフィンの筒部同士が嵌合されている、
    熱交換器。     A plate fin laminate composed of a plurality of plate fins having a flow path through which the first fluid flows, each of which is a plurality of plate fins.
    The end plates arranged on both sides in the stacking direction of the plate fin laminate and
    It includes an inflow header flow path through which the first fluid passes when flowing into the flow path, and an outflow header flow path through which the first fluid passes when flowing out into the flow path.
    Each of the plurality of plate fins
    A pair of plates are brazed to form the flow path between the pair of plates.
    It is arranged in the header region portion where the inflow header flow path and the outflow header flow path are arranged, and has a tubular portion protruding outward from each of the pair of plates.
    Of the plurality of plate fins, the tubular portions of adjacent plate fins are fitted to each other.
    Heat exchanger.
  2. 　前記複数のプレートフィンの各々の前記筒部は、前記複数のプレートフィンの各々の平面視において、前記流入用ヘッダ流路又は前記流出用ヘッダ流路を取り囲むように配置されている、
    請求項１に記載の熱交換器。     The tubular portion of each of the plurality of plate fins is arranged so as to surround the inflow header flow path or the outflow header flow path in the plan view of each of the plurality of plate fins.
    The heat exchanger according to claim 1.
  3. 　前記複数のプレートフィンの各々の前記筒部のうち少なくとも一方の筒部は、テーパ状又はネスティング加工した形状を有する、
    請求項１又は請求項２に記載の熱交換器。     At least one of the tubular portions of each of the plurality of plate fins has a tapered or nesting shape.
    The heat exchanger according to claim 1 or 2.
  4. 　前記複数のプレートフィンのうち隣接する前記プレートフィンの前記筒部同士の嵌合クリアランスが０．２ｍｍ以下である、
    請求項１から請求項３のいずれか１項に記載の熱交換器。     Among the plurality of plate fins, the fitting clearance between the tubular portions of the adjacent plate fins is 0.2 mm or less.
    The heat exchanger according to any one of claims 1 to 3.
  5. 　前記複数のプレートフィンのうち隣接する前記プレートフィンの前記筒部同士がロウ付けされて、隣接する前記プレートフィンのヘッダ領域部分が互いに連結されている、
    請求項１から請求項４のいずれか１項に記載の熱交換器。     Among the plurality of plate fins, the tubular portions of the adjacent plate fins are brazed to each other, and the header region portions of the adjacent plate fins are connected to each other.
    The heat exchanger according to any one of claims 1 to 4.
  6. 　前記一対のプレートの各々の外側へ突出した前記筒部は、前記プレートフィンの平面視において同じ位置に配置されている、
    請求項１から請求項５のいずれか１項に記載の熱交換器。     The tubular portions protruding outward from each of the pair of plates are arranged at the same position in the plan view of the plate fins.
    The heat exchanger according to any one of claims 1 to 5.
  7. 　積層された前記複数のプレートフィンの間に第２流体が流れて、前記第１流体と前記第２流体との間で熱交換する、
    請求項１から請求項６のいずれか１項に記載の熱交換器。     A second fluid flows between the plurality of stacked plate fins, and heat is exchanged between the first fluid and the second fluid.
    The heat exchanger according to any one of claims 1 to 6.
PCT/JP2021/004504 2020-06-02 2021-02-08 Heat exchanger WO2021245986A1 (en)

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CN115885150A (en) 2023-03-31
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JP7538991B2 (en) 2024-08-23

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