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WO2018139162A1 - Échangeur thermique - Google Patents

Échangeur thermique Download PDF

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Publication number
WO2018139162A1
WO2018139162A1 PCT/JP2017/047004 JP2017047004W WO2018139162A1 WO 2018139162 A1 WO2018139162 A1 WO 2018139162A1 JP 2017047004 W JP2017047004 W JP 2017047004W WO 2018139162 A1 WO2018139162 A1 WO 2018139162A1
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WO
WIPO (PCT)
Prior art keywords
fin
heat exchanger
fins
bent
collar
Prior art date
Application number
PCT/JP2017/047004
Other languages
English (en)
Japanese (ja)
Inventor
寿守務 吉村
吉田　育弘
一普 宮
皓亮 宮脇
典宏 米田
貴博 堀
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2018564185A priority Critical patent/JP6755338B2/ja
Publication of WO2018139162A1 publication Critical patent/WO2018139162A1/fr

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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
    • 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
    • F28F1/26—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 being integral with the element
    • F28F1/28—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 being integral with the element the element being built-up from finned sections
    • 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
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element

Definitions

  • the present invention relates to a plate fin type heat exchanger.
  • a conventional heat exchanger includes, for example, a plurality of flat plate-shaped fins provided with a plurality of fin collars as disclosed in Patent Document 1.
  • a plurality of fins are laminated so that the hole centers of the plurality of cylindrical fin collars coincide with each other to form a fin core.
  • the fin collars connected to each other are joined and sealed with a resin to form a plurality of liquid passing pipes.
  • the liquid passage tube is anticorrosive on the surface by a resin film formed on the inner peripheral surface.
  • the resin film formed on the inner peripheral surface of the liquid flow pipe serves as a thermal resistance. For this reason, heat exchange performance falls.
  • a relatively high-viscosity fluid such as water or antifreeze flows through the flow tube, or when the flow tube is configured with a small diameter for high heat transfer, the flow of the flow tube is laminar. There is a problem that the heat exchange performance deteriorates.
  • the present invention is intended to solve the above-described problems, and an object of the present invention is to provide a heat exchanger capable of obtaining high heat exchange performance even when a fluid flowing in a liquid passage tube is easily laminarized. .
  • a plurality of plate-like fins having a collar portion extending in a tapered shape from one surface are stacked, and the collar portions of fins adjacent to each other in the stacking direction are connected to form a liquid flow pipe.
  • the second fin discontinuous in the circumferential direction of the collar portion is provided inside the collar portion.
  • the second fins that are discontinuous in the circumferential direction are arranged inside the collar portion, and the resin film is formed on the inner surface of the liquid passage tube, so that it flows in the liquid passage tube. Even when the fluid is easily laminarized, the heat exchange performance is improved by the leading edge effect.
  • the second fin is formed discontinuously, a portion without the second fin, specifically a gap, can be formed in the circumferential direction, and flow resistance can be suppressed.
  • FIG. 2 is a front view showing fins when the heat exchanger according to Embodiment 1 of the present invention is viewed from the AA direction of FIG.
  • FIG. 3 is a cross-sectional view showing the heat exchanger according to Embodiment 1 of the present invention when viewed from the BB direction of FIG.
  • It is a perspective view which shows the structure of the fin collar of the heat exchanger which concerns on Embodiment 1 of this invention.
  • FIG. 1 is a perspective view showing an appearance of a heat exchanger 10 according to Embodiment 1 of the present invention.
  • the heat exchanger 10 has a fin core constituted by a plurality of plate-like fins 1 stacked at intervals and a liquid passage 13 penetrating the plurality of fins 1 in the overlapping direction.
  • FIG. 2 is a front view showing the fin 1 when the heat exchanger 10 according to Embodiment 1 of the present invention is viewed from the AA direction (the overlapping direction of the fins 1) in FIG. Note that the direction in which the fins 1 overlap and the direction in which the fluid flows in the fluid passage 13, that is, the fluid passage direction, are the same direction.
  • the heat exchanger 10 performs heat exchange between the air on the surface of the fin 1 and the fluid flowing in the liquid passage 13.
  • the fluid which flows into the liquid flow pipe 13 is demonstrated as water.
  • the fluid flowing through the liquid passage 13 may be water or a fluorine-based inert liquid to which a chemical that lowers the freezing point of the fluid is added.
  • the air WF is generated by, for example, a blower.
  • the air WF may use natural convection or wind generated by other driving force instead of the blower.
  • Water RF enters from one end of the fin 1 on which the liquid passage 13 of the fin 1 is overlapped and exits from the other end.
  • a plurality of liquid passing pipes 13 are provided in the fin 1, and the plurality of liquid passing pipes 13 are connected to each other by a U-shaped pipe (not shown) or the like so as to be reversed and flow in parallel at the other end.
  • the liquid flow pipes 13 are arranged in two rows in the flow direction (row direction) of the air WF orthogonal to the overlapping direction of the fins 1, and a plurality of the liquid passage tubes 13 are arranged in the vertical direction (stage direction) for each row.
  • the structure is shown. Further, the arrangement structure in which the liquid passage pipes 13 are formed is formed in a staggered arrangement as shown in FIG.
  • the water RF since water RF flows into a large number of liquid passages 13 from one end in the overlapping direction, the water RF branches at the inlet header 2 and connects the connection pipes 4 to the respective liquid passages 13. It flows in through.
  • the water RF that is reversed by the U-shaped tube at the other end of the heat exchanger 10 and flows out in parallel from the inflow pipes 13 flowing in the opposite direction to the inflow direction is joined to the outlet header 3 via another connection pipe 4. It flows out after.
  • the liquid passing pipe 13 is formed at a different position in the direction in which the wind flows.
  • the water RF flows from the inlet header 2 into the liquid flow pipe 13 positioned on the downstream side of the wind, and the water RF flows out from the liquid flow pipe 13 positioned on the upstream side to the outlet header 3. For this reason, heat exchange becomes favorable.
  • the water RF is configured so as to reciprocate the fin 1 that is formed by inverting the two liquid-passing tubes 13 at the other end.
  • the liquid passage 13 can be variously changed.
  • the water RF may flow out from the outlet header 3 installed at the other end without reciprocating the overlapped fins 1.
  • the water RF may be connected so as to reciprocate a plurality of times while meandering inside the superposed fins 1.
  • the liquid flow tube 13 of the first embodiment is formed by connecting fin collars formed on the fins 1.
  • the fin 1 is made of metal (for example, aluminum).
  • the fin collar is a portion protruding in a cylindrical shape from one surface of the fin 1 by, for example, drawing.
  • the fin collar is typically cylindrical and protrudes from one surface of the fin 1 in the vertical direction. Further, as will be described later, a part of the fin collar is deformed.
  • the fin collar has a cylindrical inner surface and an outer surface that are tapered in the vertical direction from one surface of the fin 1.
  • the tapered portion of the fin collar is referred to as a collar portion 11.
  • the tip of the collar portion 11 of the fin 1 on the other side in the overlapping direction is inserted into the opening of the collar portion 11 of the fin 1 on one side in the overlapping direction.
  • the fin collars of the two fins 1 are bonded to each other between the inner surface and the outer surface of the cylindrical portion, so that the liquid passing tube 13 is configured.
  • a resin adhesive or brazing is used for adhesion between the collar portions 11 of the two fins 1.
  • a resin film 14 is formed of a resin material on the inner surface of the liquid flow pipe 13 (see FIG. 27).
  • the resin film 14 may be used for joining the collar portion 11.
  • the fin 1 is a metal whose main component is aluminum
  • the formation of the resin film 14 can prevent corrosion due to water.
  • manufacturing becomes easy and productivity is improved.
  • FIG. 3 is a cross-sectional view showing a cross section of the heat exchanger 10 according to the first embodiment of the present invention as seen from the BB direction of FIG.
  • FIG. 4 is a perspective view schematically showing the shape of the fin collar according to the first embodiment of the present invention.
  • FIG. 3 shows an enlarged view of the vicinity of the portion where the water RF is distributed from the inlet header 2 via the connecting pipe 4 to the liquid passing pipe 13.
  • the connecting pipe 4 has a flange-like portion formed at the tip thereof.
  • the flange-like portion of the connecting pipe 4 is bonded to the exposed surface of the fin 1 exposed on the inlet header 2 side so that the connecting pipe 4 and the liquid passing pipe 13 communicate with each other.
  • the resin film 14 formed on the inner surface of the liquid flow pipe 13 is thin. For this reason, the resin film 14 is omitted in FIG.
  • the fin collar has second fins 12 that protrude inside the liquid passage tube 13.
  • the second fin 12 is a protrusion protruding toward the center of the cross section of the pipe perpendicular to the liquid passing direction of the liquid passing pipe 13.
  • the second fin 12 is made of a material continuous with the collar portion 11.
  • the second fin 12 has a surface portion that is inclined with respect to the tapered surface of the collar portion 11.
  • the tapered surface of the collar portion 11 is a surface formed in a cylindrical shape that is tapered toward the tip.
  • the tapered surface of the collar portion 11 has a surface slightly inclined with respect to the liquid flow direction.
  • the second fins 12 exist as protruding structures that are discontinuous in the circumferential direction and liquid passing direction of the collar portion 11 inside the collar portion 11.
  • the second fins 12 are not continuous in the circumferential direction and the liquid passing direction. For this reason, a portion without the second fin 12 exists somewhere in the circumferential direction or somewhere in the liquid flow direction inside the collar portion 11.
  • second fins 12 that are two protrusions at positions separated in the circumferential direction.
  • the second fins 12, which are two protrusions, are provided at positions where they face each other, that is, at positions that are point-symmetric with respect to the center of the cross section of the tube perpendicular to the liquid passing direction of the collar portion 11.
  • FIG. 3 shows a case where the protrusion of the second fin 12 has a dome-shaped cross section.
  • the second fins 12 may protrude in a columnar shape, a prismatic shape, a rectangular shape, or the like.
  • the length by which the second fin 12 protrudes toward the inside becomes too long, the flow resistance in the liquid passage tube 13 increases, and the power for flowing the water RF into the tube increases.
  • the length by which the second fin 12 projects inward is, for example, about 1/10 of the inner diameter of the collar portion 11 to about 1 ⁇ 2 of the inner diameter of the collar portion 11 at the maximum. It is good to set.
  • the length of the second fin 12 is shorter than the length of the collar portion 11. In the direction in which the fins 1 are overlapped, the length of the second fins 12 is shorter than the interval between the adjacent fins 1.
  • the second fins 12 are provided in the middle of the overlapping direction of the collar portion 11 in the overlapping direction of the fins 1.
  • the second fins 12 are not formed on the fin 1 side having the second fins 12 and the front end side of the collar portion 11.
  • the cylindrical surface of the collar portion 11 is left. As a result, the tapered surfaces of the two collar portions 11 are in close contact with each other between the adjacent fins 1, and the liquid passing tube 13 having excellent sealing performance and strength is configured.
  • a method for manufacturing the heat exchanger 10 according to the first embodiment will be described.
  • a thin metal plate is prepared as a material for the fin 1, and a fin collar is formed by drawing with a press. Furthermore, the press work which forms the 2nd fin 12 which is protrusion toward the center from the outer side of the taper surface of the collar part 11 in a fin collar is performed. In this way, the fin 1 in which the second fin 12 is formed can be manufactured.
  • the front end portion of the collar portion 11 provided on the fin 1 is inserted into the opening of the collar portion 11 provided on the adjacent fin 1.
  • the insertion of the tip of the collar portion 11 into the opening of the collar portion 11 is repeated using the other plurality of fins 1, and the plurality of collar portions 11 are sequentially connected to form the liquid passage 13.
  • a resin material is injected into each of the plurality of liquid pipes 13 from each opening (opening of the collar portion 11) of the fin 1 arranged at one end among the plurality of fins 1 stacked at intervals.
  • the connecting pipe 4 fixed to the inlet header 2 and the outlet header 3 is fitted into each opening after the resin material is injected. Further, as described above, the tip end portion of the collar portion 11 protruding from the fin 1 arranged at the other end of the plurality of fins 1 stacked at intervals is inserted into the U-shaped tube and fixed.
  • the heat-treated fin 1 is fluidized to fluidize the resin material, and the inner peripheral surface of the liquid passage 13, that is, the entire fin collar interior that is the collar portion 11 and the second fin 12 is fluidized resin. Cover with wood. Then, the resin material is infiltrated and joined to the joining surfaces of the fin fins connected to each other, and the resin material is cooled and solidified to be fixed. In addition, after applying the resin material to the fin collar and sequentially connecting the collar portions 11 to assemble the fin core, the fin core may be heated and cooled to fix the resin material.
  • the film thickness of the resin film 14 formed of a resin material on the inner peripheral surface of the liquid flow pipe 13 is desirably 50 ⁇ m or less.
  • the collar portion 11 when the front end portion of the collar portion 11 is inserted into the adjacent collar portions 11 and the plurality of collar portions 11 are sequentially connected, the collar portion 11 has a tapered cylindrical shape with a taper. If the taper shape is adjusted, the distance between the two fins 1 through which air flows is maintained. However, if an assembly spacer jig is inserted between the two fins 1, the distance between the two fins 1 can be maintained with higher accuracy.
  • the operation of the heat exchanger 10 according to the first embodiment will be described by taking as an example a case where hot water or cold water is used as a heat transfer medium and accommodated in an indoor unit of an air conditioner.
  • the heat transfer medium is heated by heat exchange with the refrigerant in the outdoor unit, and flows into the indoor unit as hot water (here, the flow of water RF is used as the hot water RF).
  • the hot water RF flows in from the inlet header 2 of the heat exchanger 10 accommodated in the indoor unit, and flows through the liquid passage pipes 13 positioned on the downstream side of the air WF via the connection pipes 4.
  • the hot water RF that has flowed through the respective flow pipes 13 on the downstream side of the air WF flows into the respective liquid flow pipes 13 positioned on the upstream side of the air WF via U-shaped pipes.
  • the heat transfer medium is cooled by heat exchange with the refrigerant in the outdoor unit, and flows into the indoor unit as cold water (here, the flow of water RF is used as the cold water RF).
  • the heat exchanger 10 flows.
  • the flow of the cold water RF in the heat exchanger 10 is the same as the flow during the heating operation.
  • the indoor air WF is sucked by the blower of the indoor unit and blown into the room in the flow direction of the air WF via the heat exchanger 10.
  • the air WF sucked by the blower flows between the fins 1 adjacent to each other in the overlapping direction from the direction orthogonal to the overlapping direction of the fins 1.
  • the air WF exchanges heat with the hot water RF in each flow-through pipe 13 located on the windward side, and exchanges heat with the hot water RF in each liquid-flow pipe 13 located on the leeward side to become warm air. It flows out into the room.
  • the air WF heat-exchanged with the cold air is sent into the room by the cold water RF flowing in the liquid passages 13 on the leeward side and the windward side.
  • the second fin 12 is configured so as to block a part of the flow of the fluid flowing along the inner surface of the collar portion 11 inside the liquid passage 13. Is arranged. For this reason, even when there is a laminar flow of the heat transfer medium, the heat transfer rate is improved by the leading edge effect.
  • the leading edge effect is that a thin thermal boundary layer is formed from the leading edge of the tip of the second fin 12 around the second fin 12 placed in isolation in the laminar flow, and the heat transfer coefficient Says the effect of improving.
  • a case where two second fins 12 are arranged in the circumferential direction inside one collar portion 11 is shown.
  • the number of the second fins 12 may be one, and the heat transfer promoting effect becomes higher as the number is larger.
  • the second fin 12 directly exchanges heat between water and air at the front and back of the expanded area portion. For this reason, unlike the case of providing a normal area expansion fin, for example, a plurality of thin plates on the inner surface of the collar portion 11, the expansion area portion has no heat conduction loss (fin efficiency is almost 100%) and is maximally effective. Heat transfer promotion effect is obtained.
  • the fin 1 and the second fin 12 having no heat conduction loss inside the liquid passage 13, water can flow in the liquid passage 13 compared to the case without the second fin 12. Since the area for heat exchange can be increased efficiently, the heat exchange performance is improved.
  • the flow of water tends to be a smooth flow with no flow separation, and the effect of expanding the area of the second fin 12 is more effectively applied.
  • a smooth tapered surface in which the second fin 12 is not formed is formed in a portion where the collar portion 11 rises from the fin 1, that is, a base portion (root portion) of the collar portion 11. .
  • the sealing property and the adhesive strength are improved.
  • the several 2nd fin 12 exists intermittently with respect to the water which flows in a liquid flow direction, and many front edges by the several 2nd fin 12 are made, the heat-transfer promotion effect becomes high.
  • FIG. 5 is a perspective view showing the structure of the fin 1 of a modification of the heat exchanger 10 according to Embodiment 1 of the present invention.
  • a cut-and-raised portion 43 is provided in a part of the fin 1.
  • the configuration is the same as that of the first embodiment except that the cut-and-raised portion 43 is provided. Therefore, sectional views and the like are omitted.
  • FIG. 5 shows a case where the cut and raised portion 43 is trapezoidal. However, the shape of the cut-and-raised portion 43 can be arbitrarily changed.
  • the cut and raised portion 43 may be formed by inserting a plurality of cut portions 44 into the fin 1 and raising the cut portions 44 in the direction in which the fins 1 are overlapped.
  • the cut-and-raised portion 43 By forming the cut-and-raised portion 43, heat transfer between the fin 1 and the air WF is promoted by the leading edge effect. In order to enhance the leading edge effect, the cut-and-raised portion 43 is preferably parallel to the flow of the air WF. Further, at the time of manufacturing the heat exchanger 10 of the modified example, the cut and raised portion 43 may be used for holding between the adjacent fins 1. The strength between the adjacent fins 1 can be improved by connecting the raised portions 43 between the adjacent fins 1.
  • the second fins 12 are present, and the resin film 14 is formed on the inner surface of the liquid passage 13.
  • the heat exchange performance can be effectively improved.
  • the 2nd fin 12 is discontinuous in the circumferential direction, the part without a 2nd fin, ie, a clearance gap, can be formed in the circumferential direction, and flow resistance can be suppressed.
  • Water RF which is a heat transfer medium, due to an increase in the operation frequency of air conditioners during the mid-season when the air conditioning load is relatively small, such as spring or autumn, or a decrease in the air conditioning load due to high thermal insulation of buildings or houses.
  • the flow rate of water is decreasing, and the operation ratio at which the flow of water RF is laminarized is increasing. Therefore, the necessity of improving the heat exchange performance even when the water RF flow is laminarized is becoming more and more important.
  • FIG. 6 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 2 of the present invention.
  • FIG. 6 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 2 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 7 is a perspective view showing the structure of a part of the fin collar of the heat exchanger according to Embodiment 2 of the present invention.
  • the second fin 12 of the second embodiment is different from the protrusion of FIG. 4 in that the position of the protrusion is shifted in the circumferential direction.
  • the heat exchanger 10 of this Embodiment 2 connects the fin collar shown in FIG. 4 and the fin collar shown in FIG. 7 alternately, and the liquid-flow pipe
  • the arrangement of the second fins 12 is alternately shifted in the circumferential direction when viewed from the liquid passing direction. Note that the manufacturing method and operation are the same as those in the first embodiment, and a description thereof will be omitted.
  • the second fin 12 of the other fin 1 when viewed from the liquid passing direction, is in the middle of the circumferential pitch of the two second fins 12 of the one fin 1. Is located. That is, in the adjacent fins 1, the second fins 12 are arranged so as to be shifted from each other by a half pitch (half cycle) in the circumferential direction.
  • the pitch is shifted in the circumferential direction, the influence of the wake of the second fins 12 arranged upstream can be suppressed, and the heat transfer performance is further improved.
  • the interval between the second fins 12 at the same position when viewed from the liquid passing direction is the same as that between the fins 1 in the overlapping direction.
  • the 2nd fin 12 existed discontinuously in the liquid flow direction.
  • the distance between the second fin 12 on the upstream side and the second fin 12 on the downstream side is narrow, and a high leading edge effect may not be obtained with the second fin 12 on the downstream side. is there.
  • the density of the second fins 12 is the same as that in the first embodiment, but the second fins 12 seen from the liquid passing direction are doubled, and a high leading edge effect is obtained. .
  • the position of the second fin 12 in the adjacent collar part 11 is a tube cross section orthogonal to the liquid passing direction of the collar part 11.
  • the position may be 180 degrees opposite to the center of.
  • the position of the 2nd fin 12 can also be shifted and offset arrangement
  • FIG. 8 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 3 of the present invention.
  • FIG. 8 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 3 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 9 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to Embodiment 3 of the present invention when viewed from the liquid direction.
  • FIG. 10 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to Embodiment 3 of the present invention.
  • a plurality of second fins 12 are formed in the circumferential direction inside the collar portion 11 of the fin collar.
  • the second fin 12 of the third embodiment is formed by processing the tip of the fin collar.
  • the second fin 12 is formed in the middle of the liquid passage direction of the collar portion 11.
  • the second fin 12 of the third embodiment is at the tip of the collar portion 11. Therefore, the second fin 12 is a portion that continues from the tip of the collar portion 11.
  • the second fin 12 is a portion bent inward from the tip of the collar portion 11.
  • the cylindrical shape does not change from the base portion of the collar portion 11 rising from the fin 1 to the tip end of the collar portion 11 connected to the second fin 12. For this reason, the surface of the collar portion 11 connecting the two fins 1 remains cylindrical.
  • the second fin 12 is formed by dividing the tip of the fin collar into a plurality of portions in the circumferential direction and bending the divided portions so as to project inside the collar portion 11.
  • the plurality of second fins 12 are bent so as to incline in the same direction of the liquid flow direction.
  • the collar portion 11 extends in the vertical direction with respect to one surface of the fin 1. And the 2nd fin 12 of this Embodiment 3 is bent so that the tip may return toward one side of fin 1.
  • the second fin 12 has a shape that is folded at an acute angle so that both surfaces form an acute angle at the tip of the collar portion 11. For this reason, the flow path area inside the liquid flow pipe 13 is ensured widely.
  • such a fin collar is divided into a plurality in the circumferential direction by forming a slit at the tip thereof. Then, it can form by performing the process which bend
  • FIG. The tapered surface of the base portion of the fin collar remains as the collar portion 11, and this portion is used for connection with the adjacent collar portion 11. Except for the structure part of the second fin 12, the manufacturing process of the other parts and the operation of the heat exchanger are the same as those in the above embodiment, and thus the description thereof is omitted.
  • the tip portions of the plurality of second fins 12 are intermittently present in the circumferential direction, and the tip portions of the plurality of second fins 12 are present.
  • a part of the flow of the water RF that flows along the inner surface of the liquid flow pipe 13 is blocked.
  • the flow of the water RF that flows in the vicinity of the collar portion 11 of the liquid flow pipe 13 flows so as to flow between the adjacent second fins 12 or the inner center of the collar portion 11 by colliding with the second fin 12.
  • a line with an arrow in FIG. 10 schematically shows how the flow along the inner surface of the collar portion 11 changes.
  • the heat exchange performance is improved by the leading edge effect and the effect of increasing the contact area even when the flow of the water RF is laminarized. Further, when a flow in which the flow of the water RF is made into a laminar flow is generated, the surface of the second fin 12 and the end thereof are in contact with the water RF to exchange heat. Since a gap is formed in the circumferential direction between the adjacent second fins 12, heat exchange performance can be improved while suppressing flow resistance.
  • a case where eight second fins 12 are arranged in the circumferential direction of the opening of the collar portion 11 is shown. However, the number of the second fins 12 may be two, and the greater the number of the second fins 12, the higher the heat transfer promoting effect and the easier the bending process.
  • the area expansion portion where the leading edge effect is obtained and the collar portion 11 are continuous. For this reason, the thermal resistance between the area enlarged portion and the collar portion 11 is relatively small (decrease in fin efficiency is suppressed). As a result, the effect of promoting heat transfer can be obtained as effectively as possible.
  • the second fin 12 having a relatively small heat conduction loss inside the liquid passage 13, the water RF is heated in the liquid passage 13 compared to the case where the second fin 12 is not provided.
  • the exchange area can be increased efficiently, and the heat exchange performance is improved.
  • the second fin 12 directly exchanges heat between water and air at the front and back of the expanded area portion.
  • the expansion area portion has no heat conduction loss (fin efficiency is almost 100%).
  • the effect of promoting heat transfer can be obtained as effectively as possible.
  • FIG. 11 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 4 of the present invention.
  • FIG. 11 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 4 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 12 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the fourth embodiment of the present invention as viewed from the liquid direction.
  • FIG. 13 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the fourth embodiment.
  • the heat exchanger 10 of the fourth embodiment is the same as that of the third embodiment in that there are a plurality of bent second fins at the tip of the collar portion 11. However, the heat exchanger 10 of the fourth embodiment is different in that second fins having different bending directions with respect to the liquid passing direction in the plurality of second fins bent are mixed.
  • Some of the second fins 12 a have a shape that is bent at an acute angle with respect to the collar portion 11 so that the tip is directed to one surface of the fin 1 as in the third embodiment.
  • the second fin 12b that is adjacent to the second fin 12a in the circumferential direction is bent so as to protrude inward from the collar portion 11, and the tip thereof is away from one surface of the fin 1 with respect to the collar portion 11.
  • the shape is bent at an obtuse angle. Therefore, the latter second fin 12 b is inclined in the same direction as the collar portion 11 and is bent inside the collar portion 11 at a slight angle so as to form an obtuse angle with respect to the tapered surface of the collar portion 11. Note that the manufacturing method and operation are the same as those in the third embodiment, and a description thereof is omitted.
  • the 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1.
  • the 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1.
  • the second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction.
  • the second fins 12a and 12b adjacent to each other in the circumferential direction inside one collar portion 11 are bent in opposite directions in the liquid passing direction. Since it is configured in this way, a larger gap is formed between the second fins 12 than in the third embodiment, and the heat exchange performance can be improved as in the third embodiment while the flow resistance is suppressed.
  • FIG. 13 the flow of the water RF along the inner surface of the collar portion 11 is changed in the flow direction by the second fins 12 a, flows between the adjacent second fins 12 a, and downstream in the liquid flow direction.
  • the state of flowing on the surface of the existing second fin 12b is schematically shown.
  • Such a flow of water RF also leads to suppression of upstream disturbance. For this reason, the leading edge effect of the second fin 12b on the downstream side can be obtained to the maximum (the influence of the wake can be suppressed to the maximum), and the heat transfer performance is further improved.
  • FIG. 14 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 5 of the present invention. 14 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 5 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 15 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the fifth embodiment of the present invention as viewed from the liquid direction.
  • FIG. 16 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the fifth embodiment of the present invention.
  • the heat exchanger 10 of the fifth embodiment is the same as the third and fourth embodiments in that there are a plurality of bent second fins at the tip of the collar portion 11.
  • the shapes of the second fins 12a and 12b are different.
  • the second fins 12a and 12b according to the fifth embodiment are configured by second fins 12a and 12b that are bent portions in which a part of the circumferential direction is bent in the liquid passing direction and a flat portion 12c that is orthogonal to the liquid passing direction. Is done.
  • the flat portion 12c is formed in a fan-shaped shape that protrudes from a part in the circumferential direction at the tip of the collar portion 11 toward the center side of the tube cross section orthogonal to the liquid direction.
  • the flat part 12c is bent so as to have a surface substantially orthogonal to the liquid flow direction. Further, the second fins 12a and 12b, which are bent portions, are provided at both ends of the flat portion 12c. When viewed from the liquid passing direction, the second fin 12a that is the bent portion and the second fin 12b that is the bent portion are at opposite ends in the circumferential direction with respect to the flat portion 12c.
  • the second fin 12a that is a bent portion is a portion that is bent toward the upstream side in the liquid passing direction.
  • the second fin 12b, which is a bent portion is a portion bent toward the downstream side in the liquid passing direction.
  • the second fin 12a which is a bent portion
  • the second fin 12b that is a bent portion is located at the end in the counterclockwise direction with respect to the flat portion 12c when viewed from the upstream side in the liquid passing direction to the downstream side.
  • the second fins 12a and 12b, which are bent portions may be arranged in reverse.
  • the flat part 12c was fan-shaped, it may be formed in a shape such as a triangle, a trapezoid, or a rectangle.
  • 15 and 16 show a configuration in which two second fin bodies are located at different positions in the circumferential direction inside one fin collar. When viewed from the liquid passing direction, the inner periphery of the collar portion 11 includes a region where two second fin bodies are formed and a region where the second fin bodies are not formed between them.
  • the 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1.
  • the 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1.
  • the second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction.
  • a slit is formed at the tip of the fin collar for the second fins 12 a and 12 b that are bent portions and the flat portion 12 c. It can be manufactured by bending each part after that.
  • the tapered surface of the base portion of the fin collar remains as the collar portion 11, and this portion is used for connection with the adjacent collar portion 11.
  • the manufacturing process of the other parts and the operation of the heat exchanger are the same as those in the above embodiment, and thus the description thereof is omitted.
  • the flow of the water RF along the inner surface of the collar portion 11 changes as shown by the line with an arrow in FIG. Since the second fin body protrudes inside, the heat exchange performance is improved by the leading edge effect as in the above embodiment. Further, the second fin body has different height portions in the liquid passing direction in different circumferential directions in the collar portion 11. Thereby, the flow of the water RF generates an asymmetric flow in the circumferential direction, and as a result, a flow in the circumferential direction is generated.
  • the water RF that flows toward the flat portion 12c with respect to the upstream end of the second fin 12a that is the bent portion collides with the flat portion 12c, and then is opposite to the second fin 12a that is the bent portion along the circumferential direction.
  • FIG. 17 is a cross-sectional view showing a modified example in which both ends of the flat portion 12c are second fins 12a which are bent portions bent toward the inlet header 2 side. Since the bent tip of the second fin 12a faces the upstream side of the flow, the leading edge effect is enhanced.
  • both ends of the flat portion 12c are bent to the opposite side of the outlet header 3, so that the bent tip of the second fin 12a faces the upstream side and the leading edge effect is enhanced. It is done.
  • the performance change due to the flow direction of the water RF may be smaller when the second fins with different bending directions are mixed as shown in FIG. That is, only the second fin 12a having the first shape that is bent so that the tip approaches one surface of the fin 1 may be provided. Further, as described later in the sixth embodiment, only the second fin 12b having the second shape whose tip is bent so as to be away from one surface of the fin 1 may be provided.
  • the area of the second fins 12a and 12b increases, the effect of improving heat transfer and reducing flow resistance due to the leading edge effect can be obtained.
  • the second fin since the second fin is divided in the circumferential direction (perpendicular to heat transfer), there is no influence that heat transfer is reduced by the division.
  • the second fins 12a and 12b, which are the bent portions in the fifth embodiment are divided in the radial direction (heat transfer direction) from the collar portion 11, there is a possibility that heat conduction loss will increase if it is made too large. There is. Therefore, for example, the area of the second fins 12a and 12b, which are the bent portions, is preferably set to an appropriate size, such as smaller than the flat portion 12c.
  • FIG. 18 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 6 of the present invention.
  • FIG. 18 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 6 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 19 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the sixth embodiment of the present invention when viewed from the liquid direction.
  • the second fin 12 of the sixth embodiment has a shape in which the second fin 12a of the fourth embodiment is removed and only the second fin 12b is left.
  • the second fin 12 is bent inside the collar portion 11 at a slight angle so as to form an obtuse angle with respect to the tapered surface of the collar portion 11, and is inclined in the same direction as the tapered surface of the collar portion 11.
  • a plurality of second fins 12 are provided at intervals in the circumferential direction.
  • the manufacturing method and operation are the same as those in the third and fourth embodiments, and the description thereof is omitted.
  • the sixth embodiment no second fin is formed between the second fins 12 adjacent in the circumferential direction. For this reason, the improvement in heat exchange performance is slightly inferior to that of the fourth embodiment. However, the flow resistance can be further suppressed.
  • the sixth embodiment is effective when the diameter of the liquid passage pipe 13 is reduced.
  • FIG. 20 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 7 of the present invention. 20 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 7 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 21 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the seventh embodiment of the present invention as viewed from the liquid direction.
  • the second fin 12 of the seventh embodiment is inclined in the same direction as the tapered surface of the collar portion 11 and inside the collar portion 11 as in the sixth embodiment.
  • a plurality of second fins 12 are provided at intervals in the circumferential direction.
  • the positions of the second fins 12 in the circumferential direction are shifted between the two fins 1 connected to each other.
  • FIG. 21 when viewed from the liquid flow direction, the second fin 12 of the fin 1 on the upstream side in the front liquid flow direction indicated by the solid line is connected to the downstream side in the liquid flow direction immediately behind the second fin 12 indicated by the broken line. It is shown that the second fin 12 of the fin 1 is displaced in the circumferential direction of the center of the tube cross section perpendicular to the liquid passing direction of the collar portion 11.
  • the space region between the adjacent second fins 12 of the fin 1 on the upstream side in the front liquid flow direction indicated by the solid line is connected to the downstream side in the liquid flow direction immediately behind that indicated by the broken line.
  • no second fin is formed between the second fins 12 adjacent in the circumferential direction. For this reason, flow resistance can be suppressed. Further, the fins 1 connected to each other have second fins 12 at different circumferential positions. Thereby, the water flowing in the vicinity of the inner surface of the collar portion 11 can easily come into contact with the second fin 12 of any one of the fins 1 and the heat exchange performance is improved.
  • the second fins 12 of the fins 1 connected to each other may be slightly overlapped so that no gap can be seen in the circumferential direction when viewed from the liquid passing direction.
  • FIG. 22 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 8 of the present invention. 22 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 8 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 23 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the eighth embodiment of the present invention when viewed from the liquid direction.
  • the tip of the fin collar is formed in a concavo-convex shape such as a triangle shape.
  • the second fin 12 is formed by bending the concavo-convex portion in the center direction of the tube cross section perpendicular to the airflow direction of the fin collar.
  • the tapered tubular portion of the fin collar that is not bent remains as the collar portion 11.
  • the cylindrical tip of the collar portion 11 is parallel to one surface of the fin 1 and has a smooth ring shape. At the height in the liquid passing direction from one surface of the fin 1, the bending positions of the uneven portions of the plurality of jagged portions are the same. For this reason, the airtightness by the connection of the collar portion 11 is improved.
  • the tip of the collar portion 11 is preferably formed in a smooth ring shape.
  • the concave and convex shape of the second fin 12 is formed into a shape such as a triangle that becomes narrower toward the center side of the cross section of the tube orthogonal to the ventilation direction. For this reason, a high leading edge effect can be obtained and the heat exchange performance can be improved while the area where the second fin 12 blocks the liquid passage 13 is reduced.
  • FIG. 24 is a cross-sectional view showing a heat exchanger 10 according to Embodiment 9 of the present invention. 24 corresponds to a cross-sectional view of the first embodiment viewed from the BB direction in FIG.
  • the whole structure of the heat exchanger 10 of this Embodiment 9 is the same as that of the perspective view of FIG. 1 of Embodiment 1, and the front view of FIG. 2, and description is abbreviate
  • FIG. 25 is a plan view showing the inside of the fin collar of the heat exchanger 10 according to the ninth embodiment of the present invention as seen from the liquid direction.
  • FIG. 26 is a perspective view showing the structure of the fin collar of the heat exchanger 10 according to the ninth embodiment of the present invention.
  • the ninth embodiment is similar to the fifth embodiment, but the shape of the second fin 12 is different.
  • the second fin 12 is formed with a rectangular plate portion or the like at the tip of the collar portion 11, bent toward the center of the tube cross section perpendicular to the ventilation direction of the collar portion 11, It is formed by bending one corner of the shaped plate piece portion so as to approach one surface of the fin 1 and bending the other corner of the plate piece portion toward the side away from one surface of the fin 1. Therefore, as in the fifth embodiment, the second fin 12 includes a flat portion 12c that protrudes from the tip of the collar portion 11 toward the center of the tube cross section perpendicular to the ventilation direction of the opening portion, and the collar portion 11.
  • a second fin 12a that is a bent portion that is bent toward one end in the liquid passing direction at an end of the flat portion 12c on one side in the circumferential direction, and a second fin that is a bent portion at the opposite end of the flat portion 12c.
  • a second fin 12b that is a bent portion that is bent in the opposite direction to the fin 12a.
  • the 2nd fin 12a is the 1st shape bent so that the tip might approach one side of fin 1.
  • the 2nd fin 12b is the 2nd shape bent so that the tip may go away from one side of fin 1.
  • the second fins 12a having the first shape and the second fins 12b having the second shape are alternately arranged in the circumferential direction.
  • the second fin 12 corresponds to the second fin body of the fifth embodiment.
  • the second fins 12a and 12b which are the bent portions, are not bent perpendicularly to the flat portion 12c as in the fifth embodiment, and are bent at a smaller angle than a right angle.
  • the 2nd fin 12a, 12b which is a bending part with respect to a liquid flow direction has a slope which inclines.
  • the bending part between the 2nd fins 12a and 12b and the flat part 12c which are bending parts may be formed in a continuous curved surface.
  • the 2nd fins 12a and 12b which are a bending part may be formed in a curved surface.
  • the second fins 12a and 12b which are bent portions, are formed by bending the corners of the plate pieces.
  • the flat part 12c is formed in a triangular or trapezoidal shape with a thinner central side. For this reason, these inclined surfaces are directed to the inner center of the liquid passage 13.
  • the shape used as the origin of the 2nd fin 12 demonstrated in the example made into the rectangular shape.
  • the shape on which the second fin 12 is based may be another shape.
  • the ninth embodiment since one of the second fins 12a and 12b, which are the bent portions, has an end portion on the upstream side of the flow, the heat exchange performance is improved by the leading edge effect. Further, since the second fin 12a that is the bent portion is opposite in the liquid passing direction, the second fin 12a has an action of rotating the liquid and changes the flow of the liquid, so that the same effect as in the fifth embodiment can be obtained. . In particular, since at least one of the second fins 12a and 12b, which are the bent portions, has its inclined surface inclined toward the inner center of the liquid pipe 13, the water RF flowing near the center of the liquid pipe 13 flows. It is guided near the inner wall of the collar portion 11. For this reason, heat exchange at the tube wall of the liquid flow tube 13 can also be promoted.
  • the flat portion 12c and the second fins 12a and 12b which are bent portions at both ends thereof constitute one second fin 12 (second fin body).
  • the second fin 12a that is the bent portion is formed at one end of the flat portion 12c and the second fin 12b that is the bent portion is not provided at the other end, or one end of the flat portion 12c is not provided.
  • a similar effect can be obtained when the second fin 12b, which is a bent portion, is formed at the end on the side, and the second fin 12a, which is a bent portion, is not provided at the other end. That is, only the second fin 12a having the first shape that is bent so that the tip approaches one surface of the fin 1 may be provided.
  • the second fin 12b having the second shape bent so that the tip is away from one surface of the fin 1 may be provided.
  • a part of the flat portion 12c may be bent toward the liquid passing direction.
  • the resin film 14 formed on the second fin 12 may be thinner than the resin film 14 formed on the collar portion 11.
  • at least part of the resin film 14 in the resin film 14 formed on the second fin 12 may not cover the second fin.
  • the region where the resin film 14 of the second fin 12 is thin or not covered is not necessarily the entire surface of the second fin 12 and may be only a part.
  • FIG. 27 is an enlarged cross-sectional view showing the heat exchanger 10 according to Embodiment 10 of the present invention.
  • FIG. 27 shows, as an example, a structure in which the thickness and adhesion of the resin film 14 are changed depending on the site in the structure of the seventh embodiment shown in FIG.
  • the resin film 14 of the second fin 12 protruding toward the inner center of the liquid passage 13 is thin or has a structure in which a part of the resin film 14 is not attached.
  • This example shows a structure in which the resin film 14 becomes thinner toward the tip of the second fin 12, that is, toward the inner center of the liquid passage 13, and there is no resin film 14 at the tip of the second fin 12. . Similar structures can be used for other embodiments.
  • the resin film 14 of the second fin 12 is attached with a brush inserted into the liquid passage tube 13. There is a way to rub.
  • a brush having a size smaller than the inner diameter of the collar portion 11 and capable of rubbing the second fin 12 may be used.
  • a solvent that gradually dissolves the resin film 14 instead of the brush may be used so that the solvent flows vigorously in the central portion of the liquid passage 13.
  • the heat exchange performance between the second fin 12 and the fluid flowing through the liquid passage 13 is remarkably improved.
  • the second fin 12 has a structure in which the tip of the collar portion 11 is bent toward the inner center of the liquid passage tube 13, the collar portion 11 constituting the liquid passage tube 13 is protected even when the resin film 14 becomes thin. Therefore, heat exchange performance can be improved while maintaining reliability.

Landscapes

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

Abstract

L'invention concerne un échangeur thermique dans lequel est empilée une pluralité d'ailettes plates ayant des parties de collier s'étendant chacune à partir d'une surface en une forme cylindrique effilée, les parties de collier des ailettes les unes à côté des autres dans la direction d'empilement sont reliées les unes aux autres de façon à constituer un tube de passage de liquide, et un film de résine est formé sur la surface interne du tube de passage de liquide. À l'intérieur des parties de collier, des secondes ailettes qui sont discontinues dans la direction périphérique des parties de collier sont fournies.
PCT/JP2017/047004 2017-01-24 2017-12-27 Échangeur thermique WO2018139162A1 (fr)

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JP2017010198 2017-01-24

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Citations (10)

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Publication number Priority date Publication date Assignee Title
US3068905A (en) * 1960-03-28 1962-12-18 Westinghouse Electric Corp Extended surface fins for heat exchange tubes
US3195626A (en) * 1962-07-09 1965-07-20 Gen Motors Corp Heat exchanger
FR2191087A1 (fr) * 1972-07-05 1974-02-01 Delamair Limited
JPS4992548U (fr) * 1972-11-30 1974-08-10
GB2129538A (en) * 1982-11-03 1984-05-16 Eric Smith Heat exchanger
JPS6115359B2 (fr) * 1978-02-28 1986-04-23 Nihon Radiator Co
JP2007518962A (ja) * 2004-01-20 2007-07-12 オートクンプ ヒートクラフト ユーエスエー リミテッド ライアビリティー カンパニー ろう付プレートフィン型熱交換器
JP2011021824A (ja) * 2009-07-16 2011-02-03 Kakinuma Kinzoku Seiki Kk 熱交換器及び熱交換器のフィンの延出部の形成方法
WO2013069299A1 (fr) * 2011-11-10 2013-05-16 パナソニック株式会社 Ailette de transfert de chaleur, échangeur de chaleur à tube à ailettes et dispositif de pompe à chaleur
WO2017010120A1 (fr) * 2015-07-10 2017-01-19 三菱電機株式会社 Échangeur thermique et dispositif de climatisation

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010169344A (ja) * 2009-01-26 2010-08-05 Fujitsu General Ltd 熱交換器
JP2017089905A (ja) * 2015-11-02 2017-05-25 三菱電機株式会社 熱交換器及び熱交換器を備えた空気調和機

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3068905A (en) * 1960-03-28 1962-12-18 Westinghouse Electric Corp Extended surface fins for heat exchange tubes
US3195626A (en) * 1962-07-09 1965-07-20 Gen Motors Corp Heat exchanger
FR2191087A1 (fr) * 1972-07-05 1974-02-01 Delamair Limited
JPS4992548U (fr) * 1972-11-30 1974-08-10
JPS6115359B2 (fr) * 1978-02-28 1986-04-23 Nihon Radiator Co
GB2129538A (en) * 1982-11-03 1984-05-16 Eric Smith Heat exchanger
JP2007518962A (ja) * 2004-01-20 2007-07-12 オートクンプ ヒートクラフト ユーエスエー リミテッド ライアビリティー カンパニー ろう付プレートフィン型熱交換器
JP2011021824A (ja) * 2009-07-16 2011-02-03 Kakinuma Kinzoku Seiki Kk 熱交換器及び熱交換器のフィンの延出部の形成方法
WO2013069299A1 (fr) * 2011-11-10 2013-05-16 パナソニック株式会社 Ailette de transfert de chaleur, échangeur de chaleur à tube à ailettes et dispositif de pompe à chaleur
WO2017010120A1 (fr) * 2015-07-10 2017-01-19 三菱電機株式会社 Échangeur thermique et dispositif de climatisation

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