US20110094258A1 - Heat exchanger and air conditioner provided with heat exchanger - Google Patents

Heat exchanger and air conditioner provided with heat exchanger Download PDF

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Publication number
US20110094258A1
US20110094258A1 US12/994,193 US99419309A US2011094258A1 US 20110094258 A1 US20110094258 A1 US 20110094258A1 US 99419309 A US99419309 A US 99419309A US 2011094258 A1 US2011094258 A1 US 2011094258A1
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United States
Prior art keywords
refrigerant
heat transfer
heat exchanger
pipe
refrigerant flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US12/994,193
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English (en)
Inventor
Sangmu Lee
Akira Ishibashi
Takuya Matsuda
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Filing date
Publication date
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Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ISHIBASHI, AKIRA, LEE, SANGMU, MATSUDA, TAKUYA
Publication of US20110094258A1 publication Critical patent/US20110094258A1/en
Priority to US14/515,994 priority Critical patent/US9322602B2/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/005—Compression machines, plants or systems with non-reversible cycle of the single unit type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F28F1/405—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element and being formed of wires
    • 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
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/125—Fastening; Joining by methods involving deformation of the elements by bringing elements together and expanding
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49373—Tube joint and tube plate structure

Definitions

  • the present invention relates to a heat exchanger and an air conditioner provided with this heat exchanger.
  • a prior-art heat exchanger constituting an air conditioner includes a heat exchanger called fin-tube heat exchanger.
  • This heat exchanger is constituted by plate-like fins arranged with a certain interval and through which gas (air) flows and a flat-shaped heat transfer pipe inserted orthogonally into the plate-like fins and through which a refrigerant flows, and a plurality of protruding strips are provided in the axial direction on an inner face of the heat transfer pipe (See Patent Document 1, for example).
  • a heat exchanger having a flat-shaped heat transfer pipe in a multi-hole structure or a heat exchanger having a plurality of slits provided in a plate-like fin by cutting are included.
  • the slit group is provided so that a side end portion of the slit opposes a flow direction of air, and it is described that by thinning a speed boundary layer and a temperature boundary layer of the air flow at the side end portion of the slit, heat transfer is promoted and heat exchange capacity is increased (See Patent Document 2, for example).
  • Patent Document 1 Japanese Unexamined Patent Application Publication No. 11-94481 ( FIGS. 1 to 3 )
  • Patent Document 2 Japanese Unexamined Patent Application Publication No 2003-262485 ( FIGS. 1 to 4 )
  • the heat transfer pipe can be made into a multi-hole structure and its size and diameter can be reduced as in Patent Document 2.
  • the size and diameter of the heat transfer pipe heat transfer rate in the pipe is increased while pressure loss is increased, and they need to be optimized.
  • the heat transfer pipe whose size and diameter are reduced is advantageous in heat transfer performance, but there is a problem that a cost for assembling or the like is increased since manufacture of the heat transfer pipe and mounting between the heat transfer pipe and the plate-like fin are carried out by brazing.
  • the present invention was made in order to solve the above problems and has an object to provide a heat exchanger and an air conditioner provided with this heat exchanger in which ventilation resistance is reduced and heat exchange capacity is increased by using a heat transfer pipe in which deformation of the heat transfer pipe caused by a pressure inside the heat transfer pipe does not occur even if the heat transfer pipe is made flat, close contact with the plate-like fin is favorable, assembling performance is good, and heat transfer performance is excellent.
  • a heat exchanger is provided with a plurality of plate-like fins arranged in parallel with a predetermined interval and a plurality of flat-shaped heat transfer pipes inserted in a direction orthogonal to the plate-like fins and through which a refrigerant flows, and the heat transfer pipe has an outside shape with a flat outer face arranged along an air flow direction and a section substantially in an oval shape and first and second refrigerant flow passages made of two symmetric and substantially D-shaped through holes having a bulkhead between the two passages inside, which is bonded to the plate-like fin by expanding diameters of the first and second refrigerant flow passages by a pipe-expanding burette ball.
  • the bulkhead partitioning the two refrigerant flow passages are provided inside the flat-shaped heat transfer pipe, deformation of the heat transfer pipe is not caused by a pressure inside the heat transfer pipe even if the heat transfer pipe is made flat, and a heat transfer pipe in which close contact with the plate-like fin is favorable, assembling performance is good and heat transfer performance is excellent can be obtained. Also, by using the flat-shaped heat transfer pipe with excellent heat transfer performance with reduced size and diameter, such a heat exchanger can be obtained in which ventilation resistance is reduced and heat exchange capacity is increased.
  • FIG. 1 is a front view illustrating an outline of a heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is a front view of a heat transfer pipe of the first embodiment.
  • FIG. 3 is an explanatory diagram of pipe-expanding means for the heat transfer pipe in FIG. 2 .
  • FIG. 4 is A-A sectional view of the pipe-expanding means in FIG. 3 .
  • FIG. 5 is a front view of a heat transfer pipe of a second embodiment.
  • FIG. 6 is a diagram illustrating a relation between a height of a protruding strip and a heat exchange rate after pipe expansion.
  • FIG. 7 is a front view of a heat transfer pipe of a third embodiment.
  • FIG. 8 is an explanatory diagram of pipe-expanding means for the heat transfer pipe in FIG. 7 .
  • FIG. 9 is B-B sectional view f the pipe-expanding means in FIG. 8 .
  • FIG. 10 is a front view of a heat transfer pipe of a fourth embodiment.
  • FIGS. 11 are explanatory views of a prior-art fin-tube heat exchanger.
  • FIG. 12 is a front view illustrating an outline of a heat exchanger according to a fifth embodiment.
  • FIG. 13 is a front view illustrating an outline of a heat exchanger according to a sixth embodiment.
  • FIG. 1 is a front view illustrating an outline of a heat exchanger according to a first embodiment of the present invention.
  • reference numeral 1 denotes a heat exchanger constituted by a plurality of plate-like fins 2 arranged in parallel with a predetermined interval and a plurality of flat-shaped heat transfer pipes 3 inserted in a direction orthogonal to the plate-like fins 2 and bonded to the plate-like fins 2 by pipe expansion (also called diameter expansion).
  • the plate-like fins 2 are made of a metal plate such as copper or copper alloy or aluminum or aluminum alloy (similarly in the other embodiments) and provided in parallel with an air flow direction A and with a predetermined interval in a perpendicular direction (depth direction) in the figure.
  • the flat-shaped heat transfer pipes 2 which will be described later, are provided in plural stages and in one row or more in a direction (vertical direction in the figure) perpendicular to the air flow direction A. Moreover, a plurality of slits 4 are provided in the plate-like fin 2 by cutting between each stage of the flat-shaped heat transfer pipes 3 .
  • the slit 4 is, as shown in Patent Document 2, provided so that a side end portion of the slit 4 opposes the air flow direction A, and by thinning a speed boundary layer and a temperature boundary layer of the air flow at the side end portion, such an advantage is provided that heat transfer is promoted and heat exchange capacity is increased.
  • the heat transfer pipe 3 is formed such that, as shown in FIG. 2 , the pipe is elongated along the air flow direction A, upper and lower outer faces 3 a, 3 b are flat and a section is substantially in an oval shape (or flat elliptic shape). That is, the upper and lower outer faces 3 a and 3 b are flat and side faces 3 c, 3 d on an upwind side and a downwind side have a flat outside shape forming a semicircle.
  • This flat-shaped heat transfer pipe 3 is made of a metal material such as copper or copper alloy or aluminum or aluminum alloy and the like and formed by an extrusion material (similarly in the other embodiments).
  • first and second refrigerant flow passages 31 a, 31 b made of two symmetric substantially D-shaped through holes are provided on both sides in the horizontal direction (hereinafter referred to as width direction) in the figure in parallel with the axial direction having a bulkhead 32 between them. That is, the heat transfer pipe 3 has a flat and substantially D-shaped two-hole structure.
  • a radius r after diameter expansion (which will be described later) of the first, second refrigerant flow passages 31 a, 31 b made of such substantially D-shaped through holes is 1 to 3 mm. That is because if the radius r is less than 1 mm, an increase amount of pressure loss becomes larger than an increase amount of heat transfer rate, which results in lowered heat exchange performance. On the other hand, if the radius r exceeds 3 mm, not only that an inter-pipe refrigerant flow velocity is slowed and the heat exchange performance is lowered but that a height (thickness) H and a width W of the flat-shaped heat transfer pipe 3 are increased and the pressure loss of the air flow is increased. Thus, the radius r after the diameter expansion of the first, second refrigerant flow passages 31 a , 31 b is set at 1 to 3 mm (the same applies to the radius r of the refrigerant flow passage in the other embodiments).
  • the long-hole mounting hole 22 is provided in a fin collar portion 21 of the pressed plate-like fin 2 , and each of the plate-like fins 2 is held by a jig (riot shown) or the like with the fin collar portion 21 aligned in the same direction.
  • the above-mentioned flat-shaped heat transfer pipe 3 is inserted into the mounting hole 22 of each of the plate-like fins 2 , and then, using a pipe expanding device using a pair of pipe-expanding burette balls 100 made of a metal material such as a super hard alloy or the like and having the same sectional shape (substantially D-shaped, see FIG.
  • the pair of pipe expanding burette balls 100 are pushed into the first, second refrigerant flow passages 31 a, 31 b by a mechanical method or a fluid pressure. Then, the first, second refrigerant flow passages 31 a, 31 b are diameter-expanded at the same time, and the heat transfer pipe 3 is sequentially bonded to each of the plate-like fins 2 and integrally fixed.
  • a thickness t 2 of the bulkhead 32 of the first, second refrigerant flow passages 31 a, 31 b is preferably formed thicker about 1.5 times a thickness t 1 of the first, second refrigerant flow passages 31 a, 31 b.
  • the flat-shaped heat transfer pipe 3 since the pressure capacity of the flat-shaped heat transfer pipe 3 can be maintained by the bulkhead 32 provided between the first, second flow passages 31 a, 31 b, the flat-shaped heat transfer pipe 3 is not deformed by the pressure inside the heat transfer pipe and the close contact with the plate-like fin 2 can be kept favorable. Thus, the heat transfer pipe with excellent heat transfer performance can be obtained. Also, since the flat-shaped heat transfer pipe 3 is bonded to the plate-like fin 2 by pipe expansion, assembling is far easier than brazing. Therefore, a manufacturing cost can be lowered.
  • an interval between the plate-like fins 2 can be kept constant by the fin collar portion 21 in the same direction and close contact between the flat-shaped heat transfer pipe 3 and the plate-like fin 2 is favorable, the heat exchanger in which the ventilation resistance is reduced and heat exchange capacity can be increased can be obtained even if the heat transfer pipe is made flat and the size and diameter are reduced.
  • FIG. 5 is a front view illustrating a flat-shaped heat transfer pipe of a second embodiment.
  • the heat transfer pipe 3 of this embodiment has, as in the case of FIG. 2 , the first, second refrigerant flow passages 31 a, 31 b made of through holes having substantially a D-shaped section provided on both sides in the width direction.
  • a plurality of protruding strips 33 having a substantially square section (its distal end portion is in a slightly rounded shape) are provided in the axial direction with a constant height and interval.
  • the above flat-shaped heat transfer pipe 3 is inserted into the mounting hole 22 of the plate-like fin 2 according to the above-mentioned procedure and fixed to the plate-like fin 2 by expanding the diameters of the first, second refrigerant flow passages 31 a, 31 b through each protruding strip 33 using the pipe-expanding burette balls 100 having the same sectional shape (substantially D-shape) as above.
  • the height h of the protruding strip 33 after the pipe expansion exceeds 0.3 mm, the increase amount of pressure loss becomes larger than the increase amount of the heat transfer rate, and as a result, the heat exchange rate is lowered.
  • the height h of the protruding strip 33 after the pipe expansion is less than 0.1 mm, the heat transfer rate is not improved.
  • the height h (protruding length) of the protruding strip 33 after the pipe expansion is preferably approximately 0.1 to 0.3 mm.
  • the sectional shape of the protruding strip 33 is not limited to a square, but any appropriate sectional shape such as triangle, trapezoid, semicircle and the like can be employed.
  • FIG. 7 is a front view illustrating a flat-shaped heat transfer pipe of a third embodiment.
  • the heat transfer pipe 3 of this embodiment has, similarly to FIG. 2 , the first and second refrigerant flow passages 31 a, 31 b made of through holes having sections substantially in the D-shape provided on both sides in the width direction.
  • a plurality of protruding strips 33 , 34 having a predetermined height and interval and sections substantially in a square shape (the distal end portions are in a slightly rounded shape) are provided in the axial direction.
  • the protruding strip 34 is provided at corner portions of the bulkhead 32 and further at a required height h so that distal ends of the protruding strips 33 , 34 are brought into contact with a circle with a radius R, that is, an outer circumferential face (See FIG. 9 ) of a circle of the pipe-expanding burette ball 100 .
  • the first, second refrigerant flow passages 31 a, 31 b on which the plurality of protruding strips 33 , 34 are provided are constituted so that a distance from predetermined points at the center parts of the refrigerant flow passages in the section (O 1 , O 2 in FIG. 7 ) to each of the distal end portions of the plurality of the protruding strips 33 , 34 becomes substantially equal.
  • the points O 1 , O 2 are points matching the centers of the pipe-expanding burette balls 100 when the pipe is expanded.
  • This flat-shaped heat transfer pipe 3 is inserted into the mounting hole 22 of the plate-like fin 2 as shown in FIG. 8 according to the above-mentioned procedure and fixed to the plate-like fin 2 by expanding the diameters of the first, second refrigerant flow passages 31 a, 31 b through each protruding strip 33 , 34 using pipe-expanding burette balls 41 having a circular section.
  • the height h (protruding length) of the protruding strip 33 is preferably approximately 0.1 to 0.3 mm.
  • FIG. 10 is a front view illustrating a flat-shaped heat transfer pipe of a fourth embodiment.
  • the heat transfer pipe 3 of this embodiment has the first refrigerant flow passage 31 a in the same shape as that of the first embodiment and the second refrigerant flow passage 31 b in the same shape as that of the third embodiment. It is needless to say that the combination may be opposite.
  • This flat-shaped heat transfer 3 is inserted into the mounting hole 21 of the plate-like fin 2 according to the above-mentioned procedure and fixed to the plate-like fin 2 by expanding the diameter of the first refrigerant flow passage 31 a using the pipe-expanding burette ball 41 having a substantially D-shaped section and by expanding the diameter of the second refrigerant flow passage 31 b using the pipe-expanding burette ball 41 having a circular section.
  • the height h (protruding length) of the protruding strip 33 is preferably approximately 0.1 to 0.3 mm.
  • the sectional shape of the protruding strip 33 is not limited to a square, but any appropriate sectional shape such as triangle, trapezoid, semicircle and the like can be employed.
  • the first embodiment and the third embodiment are applied in combination to the first, second refrigerant flow passages 31 a, 31 b, and the effect substantially similar to these embodiments can be obtained. That is, the flat-shaped heat transfer pipe 3 is not deformed by the pressure inside the heat transfer pipe, and close contact with the plate-like fin 2 can be maintained favorable. Thus, the heat transfer pipe having excellent heat transfer performance can be obtained. Also, since the flat-shaped heat transfer pipe 3 is bonded to the plate-like fin 2 by pipe expansion, assembling is far easier than brazing. Therefore, a manufacturing cost can be reduced.
  • each of the plate-like fins 2 can be maintained with a constant interval by the fin collar portion 21 in the same direction and close contact between the flat-shaped heat transfer pipe 3 and the plate-like fin 2 is favorable, even if the heat transfer pipe is made flat or reduced in size and diameter, a heat exchanger in which ventilation resistance is reduced and heat exchange capacity can be increased can be obtained.
  • the plurality of protruding strips 33 , 34 are provided on the inner wall face of the refrigerant flow passage 31 b, either of the refrigerant flow passages, a contact area with the refrigerant is increased, and since the height h of the protruding strip 33 is set at approximately 0.1 to 0.3 mm, a pressure inside the flow passage is not increased but the heat transfer performance can be further improved.
  • FIGS. 11 are explanatory diagrams illustrating a prior-art fin-tube heat exchanger, in which FIG. 11A shows a front face side, and FIG. 11B shows a back face side of a heat transfer pipe connected state.
  • FIG. 12 is a front view of a heat exchanger according to a fifth embodiment
  • FIG. 11 will be described.
  • the heat transfer pipe is given bending work in a hairpin state with a predetermined bending pitch at its intermediate portion so as to manufacture a plurality of hairpin pipes 51 , and then, the plurality of hairpin pipes 51 are inserted from the back face side into plate-like fins 2 arranged in parallel with each other with a predetermined interval. Then, the heat transfer pipe is expanded by a mechanical method or a liquid-pressure pipe expanding method and the plate-like fin 2 and the heat transfer pipe are bonded together.
  • the return bend pipe 5 having a braze ring on its outer face is attached to a pipe end of the adjacent hairpin pipe 51 after pipe expansion, and the both pipes are heated and brazed by a burner so as to manufacture a heat exchanger 50 .
  • the refrigerant enters from an inlet pipe 52 , flows out from “a” on the front face side to “b” on the back face side, flows in from “c” through the hairpin pipe 51 and flows out to “d” on the front face side, passes through the return bend pipe 5 on the front face side, and flows into the hairpin pipe 51 in the subsequent stage from “e”.
  • the refrigerant fluidizes downward through the heat transfer pipe as a ⁇ b ⁇ c ⁇ d ⁇ e ⁇ f ⁇ g ⁇ . . . , and the refrigerant finally flows out of a flow-out pipe 53 on the lower stage. During that period, heat exchange is performed with air passing between the plate-like fins 2 .
  • a plurality of hairpin pipes 30 are manufactured by applying bending work to the transfer pipe 3 at the intermediate part with predetermined bending pitch and then, the plurality of hairpin pipes 30 are inserted into the plate-like fins 2 arranged in parallel with each other with a predetermined interval from the back face side. Then, the heat transfer pipe 3 is expanded by the mechanical method or liquid pressure pipe expansion method as mentioned above, and the plate-like fin and the heat transfer pipe 3 are bonded together.
  • pipe ends of the heat transfer pipe 3 on the second stage and the heat transfer pipe 3 on the third stage are connected by two return bend pipes 5 a, 5 b made of a metal material of aluminum or aluminum alloy and the like in a cross state.
  • the first refrigerant flow passage 31 a on the upwind side of the heat transfer pipe 3 on the second stage and the second refrigerant flow passage 31 b on the downwind side of the heat transfer pipe 3 on the third stage are connected by the return bend pipe 5 a
  • the second refrigerant flow passage 31 b on the downwind side on the heat transfer pipes 3 on the second stage and the first refrigerant flow passage 31 a on the upwind side of the heat transfer pipe 3 on the third stage are connected by the return bend pipe 5 b.
  • the heat transfer pipe 3 on the third stage and on the fourth stage, not shown, are constituted as hairpin pipes 30 , and the heat transfer pipes on the fourth stage and the fifth stage, not shown, are connected by the return bend pipes similarly to the above in a cross state.
  • the heat exchanger 1 of this embodiment has a plurality of refrigerant circuits constituted in the column direction as above.
  • the refrigerant separately flows into the first, second refrigerant flow passages 31 a, 31 b of the heat transfer pipe 3 on the first stage, respectively, at the same time
  • the refrigerant flowing into the first refrigerant flow passage 31 a of the heat transfer pipe 3 on the first stage flows out of the first refrigerant flow passage 31 a of the heat transfer pipe 3 on the second stage through the hairpin pipe 30 and flows into the second refrigerant flow passage 31 b of the heat transfer pipe 3 on the third stage further through the return bend pipe 5 a.
  • the refrigerant flowing into the second refrigerant flow passage 31 b of the heat transfer pipe 3 on the first stage flows out of the second refrigerant flow passage 31 b of the heat transfer pipe 3 on the second stage through the hairpin pipe 30 and flows into the first refrigerant flow passage 31 a of the heat transfer pipe 3 on the third stage further through the return bend pipe 5 b.
  • the heat exchanger 1 of this embodiment since the refrigerant fluidizes alternately in a cross state by the return bend pipes 5 a, 5 b, the heat exchange capacity on the upwind side and the heat exchange capacity on the downwind side can be well-balanced, and a heat exchanger with high efficiency can be obtained.
  • FIG. 13 is a front view illustrating an outline of a heat exchanger according to a sixth embodiment. This embodiment is different from the fifth embodiment only in that the pipe ends of the heat transfer pipes 3 on the second stage and the third stage in the adjacent hairpin pipes 30 are connected by a return bend pipe 5 c having a single flow passage so that the refrigerants are mixed.
  • a mass ratio of a gas phase and a liquid phase becomes the same at outlet sides of the plurality of refrigerant circuits of the heat transfer pipe and it enters the refrigerant inlet portion of the heat transfer pipe on the subsequent stage, the heat exchange capacity on the upwind side and the heat exchange capacity on the downwind side can be well-balanced, and a heat exchanger with high efficiency can be obtained.
  • the heat exchanger 1 constituted by using the flat-shaped heat transfer pipe 3 of each of the above embodiments can be used, in a refrigerating cycle circuit constituted by sequentially connecting compressor, condenser, throttle device, evaporator by piping, as the condenser or evaporator using a HC single refrigerant of a mixed refrigerant containing HC or a refrigerant of any of R32, R410A, R407C, carbon dioxide and the like as an operating fluid.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US12/994,193 2008-06-19 2009-05-08 Heat exchanger and air conditioner provided with heat exchanger Abandoned US20110094258A1 (en)

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JP2008160060A JP4836996B2 (ja) 2008-06-19 2008-06-19 熱交換器及びこの熱交換器を備えた空気調和機
JP2008-160060 2008-06-19
PCT/JP2009/058685 WO2009154047A1 (ja) 2008-06-19 2009-05-08 熱交換器及びこの熱交換器を備えた空気調和機

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US20150059400A1 (en) * 2012-04-26 2015-03-05 Mitsubishi Electric Corporation Heat exchanger, indoor unit, and refrigeration cycle apparatus
US20150237872A1 (en) * 2012-09-14 2015-08-27 Revent International Ab Hot air oven
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US20170074564A1 (en) * 2014-05-15 2017-03-16 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus including the heat exchanger
US20170234590A1 (en) * 2014-09-17 2017-08-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus and air-conditioning apparatus
US20190049185A1 (en) * 2016-04-22 2019-02-14 Mitsubishi Electric Corporation Heat exchanger
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US20110030932A1 (en) * 2009-08-07 2011-02-10 Johnson Controls Technology Company Multichannel heat exchanger fins
US11395497B2 (en) 2010-03-04 2022-07-26 Revent International Ab Device for baking dough-based food products, net and method for baking such products
US20130074342A1 (en) * 2010-06-18 2013-03-28 Loren D. Hoffman Heat exchanger tube and method of making
US9702637B2 (en) * 2012-04-26 2017-07-11 Mitsubishi Electric Corporation Heat exchanger, indoor unit, and refrigeration cycle apparatus
US20150059400A1 (en) * 2012-04-26 2015-03-05 Mitsubishi Electric Corporation Heat exchanger, indoor unit, and refrigeration cycle apparatus
USD763417S1 (en) * 2012-08-02 2016-08-09 Mitsubishi Electric Corporation Heat exchanger tube
US20150237872A1 (en) * 2012-09-14 2015-08-27 Revent International Ab Hot air oven
US10258049B2 (en) * 2012-09-14 2019-04-16 Revent International Ab Hot air oven
US20170074564A1 (en) * 2014-05-15 2017-03-16 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus including the heat exchanger
US20170234590A1 (en) * 2014-09-17 2017-08-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus and air-conditioning apparatus
US10222086B2 (en) * 2014-09-17 2019-03-05 Mitsubishi Electric Corporation Refrigeration cycle apparatus and air-conditioning apparatus
US20190049185A1 (en) * 2016-04-22 2019-02-14 Mitsubishi Electric Corporation Heat exchanger
US10941985B2 (en) * 2016-04-22 2021-03-09 Mitsubishi Electric Corporation Heat exchanger
US11774187B2 (en) * 2018-04-19 2023-10-03 Kyungdong Navien Co., Ltd. Heat transfer fin of fin-tube type heat exchanger
US10921066B2 (en) * 2018-06-25 2021-02-16 Getac Technology Corporation Enhanced heat dissipation module, cooling fin structure and stamping method thereof
US20190390922A1 (en) * 2018-06-25 2019-12-26 Getac Technology Corporation Enhanced heat dissipation module, cooling fin struture and stamping method thereof
WO2020130657A1 (ko) * 2018-12-20 2020-06-25 한온시스템 주식회사 열교환기, 그 제조장치 및 제조방법
CN110131817A (zh) * 2019-05-10 2019-08-16 格力电器（合肥）有限公司 空调制热循环下冷媒的过冷换热系统及空调器
US20220136784A1 (en) * 2020-10-30 2022-05-05 Asrock Inc. Heat dissipation fin and heat dissipation module
US11781818B2 (en) * 2020-10-30 2023-10-10 Asrock Inc. Heat dissipation fin and heat dissipation module
USD1006966S1 (en) 2021-05-05 2023-12-05 Stego-Holding Gmbh Convector heater
USD1009234S1 (en) 2021-05-05 2023-12-26 Stego-Holding Gmbh Convector heater
USD1009235S1 (en) 2021-05-05 2023-12-26 Stego-Holding Gmbh Convector heater
USD1010782S1 (en) * 2021-08-16 2024-01-09 Webasto SE Mobile electric heater

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JP2010002093A (ja) 2010-01-07
US9322602B2 (en) 2016-04-26
US20150033789A1 (en) 2015-02-05
EP2312254B1 (en) 2017-08-30
ES2641760T3 (es) 2017-11-13
EP2312254A1 (en) 2011-04-20
CN102066866B (zh) 2013-09-18
HK1153804A1 (en) 2012-04-05
CN102066866A (zh) 2011-05-18
EP2312254A4 (en) 2014-04-02
JP4836996B2 (ja) 2011-12-14

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