WO2013018270A1 - Échangeur de chaleur à ailettes - Google Patents

Échangeur de chaleur à ailettes Download PDF

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Publication number
WO2013018270A1
WO2013018270A1 PCT/JP2012/004172 JP2012004172W WO2013018270A1 WO 2013018270 A1 WO2013018270 A1 WO 2013018270A1 JP 2012004172 W JP2012004172 W JP 2012004172W WO 2013018270 A1 WO2013018270 A1 WO 2013018270A1
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WO
WIPO (PCT)
Prior art keywords
heat transfer
fin
ridge line
heat exchanger
tube
Prior art date
Application number
PCT/JP2012/004172
Other languages
English (en)
Japanese (ja)
Inventor
横山　昭一
Original Assignee
パナソニック株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニック株式会社 filed Critical パナソニック株式会社
Priority to JP2013526717A priority Critical patent/JP5958917B2/ja
Priority to CN201280037973.1A priority patent/CN103717993B/zh
Publication of WO2013018270A1 publication Critical patent/WO2013018270A1/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
    • F28F1/32—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present invention is used in air conditioners such as room air conditioners, packaged air conditioners, and car air conditioners, heat pump hot water heaters, refrigerators, freezers, and the like, and a gas such as air that flows between a large number of stacked flat fins.
  • the present invention relates to a finned tube heat exchanger that transfers heat to and from a fluid such as water or refrigerant flowing in a heat transfer tube.
  • the fin tube type heat exchanger is generally composed of a plurality of stacked flat fins and heat transfer tubes. It is a fin-and-tube heat exchanger.
  • FIG. 10 is a perspective view showing a conventional heat exchanger.
  • FIG. 11 is a front view showing a part of the fin shown in FIG.
  • the conventional fin-tube heat exchanger 101 penetrates the fins 110 that are stacked in parallel with a certain interval, and the flat fins 110 that are stacked in parallel. It is comprised with the heat exchanger tube 130 inserted in this way.
  • the fin 110 is formed with a cylindrical fin collar 116 that rises vertically from the fin 110, and the inside of the fin collar 116 is a through hole 116a.
  • the heat transfer tube 130 is disposed through the through hole 116 a of the fin collar 116, and is closely bonded to the fin collar 116.
  • a fluid such as water or a refrigerant flows through the inside by flowing a gas such as air between the laminated plate-like fins 110.
  • the heat from the heat transfer tube 130 is configured to exchange heat with the gas flowing through the fins 110.
  • each fin 110 in the conventional fin tube type heat exchanger 101 is bent and laminated in the same shape.
  • the main flow direction W of the airflow flowing between the laminated fins 110 is the row direction (left-right direction in FIG. 11), and is orthogonal to the row direction.
  • the direction is a step direction (vertical direction in FIG. 11).
  • the fin 110 is formed with a plurality of ridge lines 112 (mountains) and ridge lines 114 (valleys) that are a plurality of fold lines extending in the step direction.
  • the ridgeline 112 that forms one peak is a mountain ridgeline
  • the ridgeline 114 that forms the other valley is a valley ridgeline.
  • the fin 110 is formed with a plurality of mountain ridge lines 112 and a valley ridge line 114 between the mountain ridge lines 112, and a undulation is formed by the mountain parts and the valley parts.
  • the fin 110 has a seat portion 118 in which a flat annular portion is formed concentrically around the fin collar 116 protruding in a cylindrical shape, and an inclined portion that rises from the seat portion 118 to the undulation portion. 120 is formed.
  • the present invention has been made in view of the above-mentioned problems of the prior art, and in order to improve the heat transfer performance between the fins and the airflow, a large number of fins are formed in a special shape, It aims at providing the fin tube type heat exchanger excellent in heat-transfer performance by increasing the ridgeline which is a line of intersection with a surface.
  • a finned tube heat exchanger includes: A plurality of heat transfer fins that are laminated substantially in parallel with a predetermined interval, and in which a laminated surface is arranged so as to be along a main flow direction of the heat exchange airflow; A heat transfer tube extending in a direction substantially orthogonal to the laminated surface direction of the heat transfer fin so as to penetrate the stacked heat transfer fins, The heat transfer fin has a through-hole through which the heat transfer tube passes, and a substantially cylindrical fin collar is formed around the through-hole so as to extend in a direction substantially perpendicular to the direction of the laminated surface of the heat transfer fin.
  • the heat transfer tube is inserted into the through-hole in a tightly coupled state with the fin collar, and the heat exchange airflow flowing in the direction of the laminated surface of the heat transfer fin and the thermal refrigerant flowing in the heat transfer tube
  • a finned tube heat exchanger configured to perform heat exchange at
  • the heat transfer fins are formed by a plurality of ridge lines extending in a direction (hereinafter, referred to as a step direction) orthogonal to a main flow direction (hereinafter, referred to as a row direction) of the heat exchange airflow on the laminated surface.
  • a seat portion having a flat surface that is concentric with the fin collar and parallel to the laminated surface, the seat portion An inclined surface rising from the undulation portion to the undulation portion, and an intermediate mountain portion that is arranged in the vicinity of the fin collar and that is formed by a ridge line on the mountain side that extends in the column direction in a valley portion that extends in the step direction.
  • a heat transfer fin in which a plurality of intermediate ridges extending in the column direction are provided in the valleys between the ridges extending in the step direction of the heat transfer fins, and the ridge lines for increasing the heat transfer coefficient are increased, and a plurality of heat transfer fins are stacked. It is possible to provide a finned tube heat exchanger excellent in heat transfer performance that can smoothly flow airflow between them and reduce the resistance to airflow between the heat transfer fins stacked in a large number.
  • FIG. 1 The perspective view which shows schematic structure of the fin tube type heat exchanger of Embodiment 1 which concerns on this invention.
  • the front view which expands and shows a part of heat-transfer fin in the fin tube type heat exchanger shown in FIG. Sectional view along line III-III in the laminated heat transfer fin shown in FIG. Sectional view taken along line IV-IV in the laminated heat transfer fin shown in FIG.
  • the side view which looked at the heat-transfer fin in the fin tube type heat exchanger of Embodiment 1 from the mainstream direction of airflow The front view which shows the laminated surface of the heat-transfer fin in the finned-tube type heat exchanger of Embodiment 2 which concerns on this invention
  • (A) is a front view which shows the lamination
  • (b) is A in the heat transfer fin shown to (a) of FIG.
  • a plurality of heat transfer fins that are laminated substantially in parallel with a predetermined interval, and in which a laminated surface is arranged so as to be along a main flow direction of the heat exchange airflow;
  • a heat transfer tube extending in a direction substantially orthogonal to the laminated surface direction of the heat transfer fin so as to penetrate the stacked heat transfer fins,
  • the heat transfer fin has a through-hole through which the heat transfer tube passes, and a substantially cylindrical fin collar is formed around the through-hole so as to extend in a direction substantially perpendicular to the direction of the laminated surface of the heat transfer fin.
  • the heat transfer tube is inserted into the through-hole in a tightly coupled state with the fin collar, and the heat exchange airflow flowing in the direction of the laminated surface of the heat transfer fin and the thermal refrigerant flowing in the heat transfer tube
  • a finned tube heat exchanger configured to perform heat exchange at
  • the heat transfer fins are formed by a plurality of ridge lines extending in a direction (hereinafter, referred to as a step direction) orthogonal to a main flow direction (hereinafter, referred to as a row direction) of the heat exchange airflow on the laminated surface.
  • a seat portion having a flat surface that is concentric with the fin collar and parallel to the laminated surface, the seat portion An inclined surface rising from the undulation portion to the undulation portion, and an intermediate mountain portion that is arranged in the vicinity of the fin collar and that is formed by a ridge line on the mountain side that extends in the column direction in a valley portion that extends in the step direction.
  • an intermediate peak portion extending in the column direction is provided in a valley portion between peak portions extending in the step direction, and a heat transfer coefficient is provided.
  • the flow of airflow between the heat transfer fins stacked in a large number can be smoothed to reduce the airflow resistance.
  • the intermediate collar portion in the first aspect is formed at an intermediate position between the fin collars adjacent in the step direction, and the fin collar You may arrange
  • the height of the intermediate peak in the second aspect from the flat surface of the seat position is the height of the peak extending in the step direction. You may form in the range of 1/4 to 3/4 of the height from a flat surface.
  • a wedge-shaped depression may be formed on the windward side and the leeward side of the fin collar in the first to third aspects.
  • wedge-shaped depressions are formed on the windward side and the leeward side of the fin collar
  • the wedge-shaped depressions include a first ridge line extending in a row direction on the windward side and leeward side of the fin collar, a ridgeline forming the valley portion extending in a step direction on the windward side and leeward side of the fin collar, and the first Two second ridge lines that lead out in two directions in a V-shape from the intersection with one ridge line toward the ridge line of the mountain portion, and the first ridge line and the second ridge line
  • An airflow passage on the leeward side and on the leeward side of the fin collar may be configured by two inclined surfaces arranged in a V shape formed between the two.
  • the finned tube heat exchanger of the present invention configured as described above is provided with an intermediate peak portion extending in the column direction in a valley portion extending in the step direction at a position near the fin collar of the heat transfer fin, While increasing the ridgeline which makes a heat transfer rate high in a fin, it becomes the structure which smoothes the airflow between many heat-transfer fins laminated
  • the finned tube heat exchanger of the present invention will be described with reference to the accompanying drawings.
  • the fin tube type heat exchanger of the following embodiment although it demonstrates with the specific example used for the air conditioner, the following embodiment is an illustration and the use of the fin tube type heat exchanger of this invention
  • the present invention is not limited to an air conditioner, but is used for various devices using a heat exchanger, and can be modified as appropriate within the technical scope of the present invention. Therefore, the present invention is not limited to the specific configurations of the following embodiments, but includes various configurations based on the same technical idea.
  • FIG. 1 is a perspective view showing a schematic structure of a finned tube heat exchanger according to Embodiment 1 of the present invention.
  • FIG. 2 is a front view showing a laminated surface which is a front surface of the heat transfer fins by enlarging a part of the heat transfer fins in the finned tube heat exchanger shown in FIG.
  • a heat exchange block in a state where a plurality of heat transfer fins 20 having the same shape are laminated in parallel with a constant interval L (laminated state). 10 is configured.
  • the heat transfer fins 20 are juxtaposed (laminated) with an interval L of about 1.5 mm.
  • the distance L between the heat transfer fins 20 is appropriately changed according to the specifications of the heat exchanger used, and is selected within the range of 1.0 mm to 3.0 mm, for example.
  • the heat transfer tubes 50 through which fluids such as water and refrigerant move are disposed so as to penetrate the large number of heat transfer fins 20 in the stacked state.
  • the heat transfer tubes 50 and the heat transfer fins 20 are tightly bonded through the fin collar 60 so as to transfer heat efficiently. As shown in FIG. 1, the heat transfer tubes 50 are disposed so as to meander through the inside of the heat exchange block 10 constituted by a large number of heat transfer fins 20 in a stacked state. The heat transfer tubes 50 and the heat transfer fins 20 are closely joined at a plurality of locations, and the heat transfer performance between the heat transfer tubes 50 and the heat transfer fins 20 is enhanced.
  • Each of the heat transfer fins 20 is formed with a plurality of cylindrical fin collars 60 that are vertically raised from the laminated surface that is the front surface of the heat transfer fin 20.
  • the inside of the fin collar 60 is a through hole 20a (see FIG. 2), and the heat transfer tube 50 is disposed through the through hole 20a of the fin collar 60.
  • the heat transfer tube 50 and the fin collar 60 are tightly bonded so as to allow heat transfer.
  • a heat exchange airflow is configured to flow with respect to the heat exchange block 10, and the main flow direction W of the airflow is the heat transfer fins 20 stacked in the heat exchange block 10. It is a direction parallel to the substantially laminated surface of each heat transfer fin 20, that is, a direction orthogonal to the longitudinal direction (penetration direction) of the heat transfer tubes 50 so that the wind flows into the gaps therebetween.
  • the air by the heat exchange airflow is caused to flow in the gaps between the stacked heat transfer fins 20.
  • the heat transferred from the heat transfer tube 50 in which a fluid such as water or refrigerant moves is exchanged with the gas flowing between the stacked heat transfer fins 20.
  • the laminated surface of the heat transfer fins 20 shown in a front view in FIG. 2 is a surface orthogonal to the penetration direction of the heat transfer tubes 50 with respect to the heat transfer fins 20 and is a surface parallel to the main flow direction W of the airflow. Yes (see FIG. 1).
  • the main flow direction W of the airflow is the same as the row direction (the left-right direction in FIG. 2) in each heat transfer fin 20, and the direction orthogonal to the row direction in each heat transfer fin 20 is the step direction. (Vertical direction in FIG. 2).
  • FIG. 3 is a cross-sectional view taken along the line III-III of the laminated heat transfer fin 20 shown in FIG. 2
  • FIG. 4 is a cross-sectional view taken along the line IV-IV of the laminated heat transfer fin 20 shown in FIG. is there.
  • FIG. 5 is a side view of one heat transfer fin 20 viewed from the main flow direction W of the airflow.
  • the heat exchange block 10 in the finned tube heat exchanger 1 includes a large number of heat transfer fins 20 stacked in parallel at a predetermined interval L, and the large number of heat transfer blocks.
  • a heat transfer tube 50 penetrating through the heat transfer fins 20 perpendicular to the laminated surface of the fins 20 is provided.
  • a heat medium such as a refrigerant flowing inside the heat transfer tubes 50 flows between the stacked heat transfer fins 20 and exchanges heat with the gas (air) flowing along the stacked surface of the heat transfer fins 20. .
  • each heat transfer fin 20 is formed with a plurality of fin collars 60, and each fin collar 60 has a through hole 20 a (3 in FIG. 2) through which the heat transfer tube 50 passes.
  • Two through-holes 20a are formed). That is, a substantially cylindrical fin collar 60 is formed around each through-hole 20a so as to extend in the direction of the laminated surface of the heat transfer fins 20 or in a direction substantially orthogonal to the main flow direction W of the airflow.
  • the heat transfer tubes 50 are tightly bonded to these fin collars 60.
  • the heat transfer tubes 50 are subjected to a diameter expansion process, which will be described later, so as to increase the diameter of the heat transfer tubes 50.
  • the diameter expansion process which is the close-bonding process for the heat transfer tube 50 will be described in detail.
  • the heat transfer fins 20 having a plurality of fin collars 60 are stacked, and the heat transfer tubes 50 are inserted into the fin collars 60.
  • the inner diameter D (see FIG. 3) of the fin collar 60 is processed to be slightly larger than the outer diameter of the heat transfer tube 50 when the heat transfer fin 20 is pressed.
  • the diameter of the heat transfer tube 50 is expanded by utilizing the hydraulic pressure in the heat transfer tube 50 or by a mechanical method, and the heat transfer tube 50 and the fin collar. 60 are closely attached to each other to improve the heat transfer performance.
  • Each heat transfer fin 20 in the finned tube heat exchanger 1 according to the first embodiment is formed by integrally forming a flat metal plate by pressing, and has a plurality of bending lines (including ridge lines). ing. As shown in FIG. 2, the heat transfer fin 20 is formed with a plurality of ridge lines 40 a and 40 b on the mountain side and the valley side extending in parallel to the step direction.
  • the mountain-side ridge line 40a extending in the step direction is a mountain ridge line
  • the valley-side ridge line 40b is a valley ridge line.
  • the undulating portion 40 having two ridges corresponds to one fin collar 60.
  • the configuration of the undulating portion 40 conforms to the specifications of the heat exchanger used. It will be changed accordingly.
  • the heat transfer fin 20 includes a plurality of mountain ridge lines 40a and a valley ridge line 40b between adjacent mountain ridge lines 40a.
  • the undulating portion 40 is configured.
  • a cylindrical fin collar 60 that protrudes perpendicularly to the laminated surface of the heat transfer fins 20 is formed by integral molding.
  • An annular seat portion 30 having a flat surface is formed around the cylindrical fin collar 60 in a concentric circle. The flat surface of the seat portion 30 is parallel to the laminated surface of the heat transfer fins 20.
  • the heat transfer fin 20 is formed with an inclined surface 30 a that rises from the annular seat portion 30 to the undulating portion 40.
  • the heat transfer fins 20 are positioned in the vicinity of the fin collar 60, and a plurality of heat transfer fins 20 are provided at intermediate positions between the fin collars 60 adjacent in the step direction.
  • the intermediate mountain part 80 comprised by the ridgeline of is formed.
  • the heat transfer fin 20 is an intermediate position between the fin collars 60 adjacent to each other in the step direction, and includes two peak portions 45 configured by adjacent peak lines 40 a and 40 a extending in the step direction.
  • An intermediate mountain portion 80 is formed at a valley position between 45. That is, the intermediate mountain portion 80 is on the central axis extending in the step direction including the center of the fin collar 60 (the center of the heat transfer tube 50) arranged in parallel in the step direction, that is, on the valley ridge line 40b in the first embodiment. Formed in position.
  • the intermediate mountain portion 80 is constituted by a mountain-side ridge line 80a extending in the row direction connecting the middle portions of the slopes of the adjacent mountain portions 45, 45 facing each other.
  • the valley-side ridge line 80b constituting the side surface 80c of the intermediate mountain portion 80 (the slopes located above and below the mountain-side ridge line 80a in FIG. 2) is a front view when the heat transfer fin 20 is viewed from the longitudinal direction of the heat transfer tube 50. 2 (on the laminated surface of the heat transfer fins 20 shown in FIG. 2), from both ends of the ridge line 80a on the mountain side to both sides thereof, the ridge line 80a on the mountain side is at an intermediate position and has an angle of approximately 90 degrees.
  • the front shape of the intermediate mountain portion 80 is substantially square will be described, but the front shape of the intermediate mountain portion of the present invention is a quadrangle.
  • the height of the seat position 30 of the intermediate mountain portion 80 from the flat surface (hereinafter referred to as the height of the intermediate mountain portion 80) is the height of the seat position 30 of the mountain portion 45 whose top is constituted by a mountain ridge line 40a extending in the step direction. It is formed lower than the height from the flat surface (hereinafter referred to as the height of the ridge 45). It is preferable that the height of the intermediate peak portion 80 is formed to a height within a range of about 1/4 to about 3/4 of the height of the peak portion 45.
  • one intermediate mountain portion 80 is constituted by one ridge line 80a extending in the column direction and four valley ridge lines 80b extending from both ends of the ridge line 80a to both sides. Two slopes 80c are formed on both sides of the ridge line 80a on the mountain side.
  • the four valley-side ridge lines 80b are formed in the middle part of the adjacent mountain portions 45 formed by the mountain ridge lines 40a extending in the step direction.
  • the vicinity of the valley-side ridge line 80b constituting the intermediate mountain portion 80 configured in this way is for heat exchange in the intermediate mountain portion 80 lower than the mountain portion 45, similarly to the mountain ridge line 40a and the valley ridge line 40b extending in the step direction.
  • the finned tube heat exchanger according to the first embodiment has a structure having high heat transfer performance, smoothes the airflow between the stacked heat transfer fins 20, and reduces the airflow resistance.
  • the structure has excellent characteristics.
  • the intermediate mountain portion 80 formed of a plurality of ridge lines is formed between the fin collars 60 adjacent in the step direction.
  • the height of the intermediate mountain portion 80 having the mountain-side ridge line 80a extending in the row direction is formed lower than the height of the mountain portion 45 having the mountain ridge line 40a extending in the step direction, and the height of the intermediate mountain portion 80 is the mountain portion.
  • the height is set within a range of about 1/4 to about 3/4 of the height of 45.
  • the height of the intermediate mountain portion 80 is set to be higher than 3/4 of the height of the mountain portion 45 having the mountain ridge line 40a extending in the step direction, the height of the intermediate mountain portion 80 extends in the step direction as it becomes closer to the height of the mountain portion 45.
  • the flow along the undulating portion 40 formed by the ridge line hardly occurs, and the heat transfer performance is deteriorated.
  • the height of the intermediate mountain portion 80 having the mountain-side ridge line extending in the row direction is preferably about 1 ⁇ 4 to about 3 ⁇ 4 of the height of the mountain portion 45 having the mountain ridge line 40a extending in the step direction.
  • the fin collar (60) adjacent in the step direction is not limited to the configuration example of the first embodiment described above.
  • the configuration of the present invention can be provided with the intermediate peak portion (80) in the present invention in other forms that can coexist, for example, Japanese Patent No. 2661356, Japanese Patent No. 2834339 and Japanese Patent No. 3367353.
  • the effect of improving the heat transfer performance described above can be added, and further, a synergistic effect of promoting heat transfer can be brought about.
  • FIG. 6 is a front view showing a laminated surface of heat transfer fins 20A in the finned tube heat exchanger of the second embodiment.
  • a flat seat portion 30 is formed in an annular shape around the fin collar 60, and a rising portion (ridge portion) 70 is formed around the seat portion 30.
  • the intermediate mountain portion 80 is formed at the intermediate position between the fin collars 60 adjacent in the step direction.
  • the airflow flowing between the stacked heat transfer fins 20A is in contact with the undulations of the heat transfer tubes 50 and the heat transfer fins 20A and the intermediate peak 80.
  • the heat of the heat transfer tubes 50 is efficiently exchanged with the airflow via the heat transfer fins 20A and the like.
  • an intermediate position between the fin collars 60 adjacent to each other in the step direction or the fin collar 60 As described above, also in the fin tube type heat exchanger of the second embodiment, as in the fin tube type heat exchanger of the first embodiment, an intermediate position between the fin collars 60 adjacent to each other in the step direction or the fin collar 60.
  • An intermediate mountain portion 80 is provided at a position of a valley ridge line 40b which is a position near the center of the fin collar 60 in the step direction of the fin collar 60.
  • FIG. 7 is a front view showing a laminated surface of heat transfer fins 20B in the finned tube heat exchanger of the third embodiment. As shown in FIG. 7, an elliptical seat portion 30 having a flat surface is formed around the fin collar 60, and a rising portion (ridge portion) 70 is formed around the seat portion 30. Yes.
  • the intermediate mountain portion 80 is the intermediate position of the fin collar 60 adjacent in the step direction, or a position in the vicinity of the fin collar 60. And it is provided in the position of the valley ridgeline 40b which is on the centerline in the step direction of the fin collar 60.
  • FIG. As a result, in the finned tube heat exchanger according to the third embodiment, the airflow is bent by the intermediate mountain portion 80 formed of a plurality of ridge lines, and the heat between the heat transfer fins 20B and the airflow. Exchange can be performed efficiently.
  • the heat transfer fin 20B is provided with the intermediate peak portion 80, thereby heat transfer.
  • the area that contributes to the heat transfer is increased, the amount of heat exchange between the heat transfer fins 20B and the airflow is increased, and the heat transfer performance is improved.
  • FIG. 8 (a) is a front view showing a laminated surface of heat transfer fins 20C in the finned tube heat exchanger of Embodiment 4, and FIG. 8 (b) is a heat transfer fin shown in FIG. 8 (a). It is sectional drawing by the AA in 20C.
  • the fin collar 60 is located at the intermediate position of the fin collar 60 adjacent in the step direction or in the vicinity of the fin collar 60.
  • An intermediate mountain portion 80 is formed at the position of the valley ridge line 40b on the center line in the step direction.
  • the heat transfer fins 20C are arranged along the main flow direction W of the heat exchange air flow from the left side to the right side of FIG. 8A, from the valley ridge line 40b, the mountain ridge line 40a, and the valley.
  • the ridgeline 40b, the mountain ridgeline 40a, and the valley ridgeline 40b have a wave shape formed in order.
  • the height (H1) of the mountain ridge line 40a from the seat portion 30 is larger than the distance (Fp) from the adjacent heat transfer fin 20C, and this distance (Fp) is 2. It is formed smaller than twice.
  • the intermediate peak portion 80 is located at an intermediate position between the fin collars 60 adjacent in the step direction or the fin collar 60. It is formed at a position of a valley ridge line 40 b that is a nearby position and is on the center line in the step direction of the fin collar 60. Therefore, the air flow is bent at the intermediate mountain portion 80 constituted by a plurality of ridge lines, contacts the heat transfer fins 20C and the heat transfer tubes 50, and heat exchange between the heat medium flowing in the heat transfer tubes 50 and the air flows is performed. It is performed with high efficiency through the heat transfer fins 20C and the like.
  • FIG. 9 is a front view showing a laminated surface of heat transfer fins 20D in the finned tube heat exchanger of the fifth embodiment.
  • the heat transfer fin 20D according to the fifth embodiment is similar to the heat transfer fin 20 according to the first embodiment in that wedge-shaped (inverted triangular shape) depressions 85 are formed on the windward side and leeward side of each fin collar 60. That is, the wedge-shaped dent 85 is formed in an inverted triangle shape so as to spread from the position of the flat surface of the seat portion 30 in the heat transfer fin 20 in the protruding direction of the fin collar 60.
  • the wedge-shaped dent 85 is located on the windward side and the leeward side of the fin collar 60 between the valley ridge line 40b and the mountain ridge line 40a formed on both sides of the fin collar 60 and extending in the step direction. Is formed.
  • the wedge-shaped dent 85 extends in the row direction orthogonal to the valley ridge line 40 b and is formed at the bottom (inverted triangular shape) of the valley 85 by the valley-side ridge lines 85 a formed on both sides of the seat portion 30 so as to pass through the center of the fin collar 60. Vertex) is configured.
  • This valley-side ridge line 85a is defined as a first ridge line.
  • the wedge-shaped dent 85 includes a valley ridge line 40b extending in the step direction formed on both the windward and leeward sides of the fin collar 60 and a valley-side ridgeline (first ridgeline) 85a that forms the bottom of the depression 85.
  • Two ridge lines 85b that are led out in the direction of the mountain ridge line 40a along the slope of the mountain part 45 from the intersection point P. This ridge line 85b on the mountain side is the second ridge line.
  • the wedge-shaped depressions 85 formed on the windward side and the leeward side of the fin collar 60 are valley-side ridgelines (first ridgelines) 85a extending in the column direction on the windward side and the leeward side of the fin collar 60, respectively. From the intersection P of the valley ridge line 40b forming the valley extending in the step direction on the windward side and leeward side of the fin collar 60 and the above-mentioned valley side ridgeline (first ridgeline) 85a, along the slope of the mountain 45 And two ridge lines (second ridge lines) 85b led out in two directions in a V shape toward the mountain ridge line 40a.
  • the wedge-shaped depression 85 has two slopes arranged in a V shape formed by the valley-side ridge line (first ridge line) 85a and the two mountain-side ridge lines (second ridge line) 85b. 85c, and constitutes an airflow passage on the windward side and leeward side of the fin collar 60.
  • the wedge-shaped dent 85 configured as described above is configured to reliably guide the airflow flowing between the heat transfer fins 20 to the fin collar 60 and smoothly guide the fin collar 60 to the leeward side.
  • the extension line of the ridge line (second ridge line) 85b constituting the wedge-shaped depression 85 is seen from the longitudinal direction (penetration direction) of the heat transfer tube 50 as shown in FIG. It is formed at a position of a tangent line T ⁇ b> 2 with the outermost peripheral line of the seat portion 30 formed around the fin collar 60.
  • the position of the ridge line 85b on the mountain side the position of the tangent line T1 with the outer peripheral line of the inclined surface 30a formed outside the seat part 30 and the innermost peripheral line of the seat part 30 (the outer peripheral line of the fin collar 60). Even if it is set in the area between the position of the tangent line T3 and the same effect, the same effect can be obtained.
  • the extension lines of the two second ridge lines 85 b are stepped on the leeward side and leeward side of the fin collar 60 when viewed from the longitudinal direction of the heat transfer tube 50.
  • the extension line of the second ridge line 85b in the wedge-shaped depression 85 is tangent T2 to the outermost peripheral line of the seat portion 30 when viewed from the longitudinal direction of the heat transfer tube 50. It consists of
  • the valley-side ridge line 85a (first ridge line) constituting the bottom of the wedge-shaped depression 85 formed on both the windward side and the leeward side of the fin collar 60 is the flat surface of the seat portion 30.
  • the extension line of the valley-side ridge line 85a is on the same plane and extends in the column direction through the center of the fin collar 60 (that is, the center of the heat transfer tube 50).
  • the mountain-side ridge line 85b (second ridge line) that forms the side surface of the wedge-shaped depression 85 extends from a predetermined point (intersection point P) of the valley ridge line 40b of the undulating portion 40 formed on both sides of the fin collar 60.
  • the extension line is, for example, at the position of the tangent line T2 in contact with the outermost peripheral line of the seat portion 30.
  • the wedge-shaped dent 85 has an inverted triangular bottom formed by a valley-side ridge line (first ridge line) 85a extending in the column direction, and a mountain-side ridge line (second line) formed on both sides of the valley-side ridge line 85a.
  • a slope 85c having an inverted triangular V shape is formed by the (ridge line) 85b. That is, the wedge-shaped dent 85 is formed to have a wedge shape (inverted triangle shape) in which the opening widens in the protruding direction of the fin collar 60.
  • the wedge-shaped depressions 85 are formed on both the windward side and the leeward side of the fin collar 60, so that the windward wedge-shaped depressions 85 have a large temperature difference from the air.
  • the airflow flows to the seat portion 30 around the heat transfer tube 50 and is guided to the inclined surface 30 a formed outside the seat portion 30, and then flows into the wake of the heat transfer tube 50. Go.
  • the wedge-shaped dent 85 formed on the leeward side is configured to guide and discharge the airflow that has entered the heat transfer tube 50 from the leeward side, and to flow to the next undulating portion 40.
  • the wedge-shaped depressions 85 formed on both the windward side and the leeward side of the fin collar 60 have excellent ventilation characteristics that allow airflow on the windward side and the leeward side to flow smoothly and reduce ventilation resistance. ing.
  • the finned tube heat exchanger according to the present invention has a lower height than the peak portion extending in the step direction between the adjacent peak portions extending in the step direction in the heat transfer fin, more preferably, An intermediate mountain portion having a ridge line extending in the column direction having a height of about 1/4 to about 3/4 of the height of the mountain portion extending in the step direction is formed.
  • the finned tube heat exchanger of the present invention has a configuration in which the ridge line having a high heat transfer rate is increased, smoothes the airflow between the heat transfer fins, improves the heat transfer performance, and reduces the ventilation resistance. It becomes the structure which has the outstanding heat-transfer characteristic that it can reduce.
  • the area contributing to heat transfer between the airflow and the heat transfer tube is increased, the amount of heat exchange is increased, and the air conditioner has excellent heat transfer characteristics. It is useful in heat exchangers used in heat pump water heaters, refrigerators, freezers, and the like.

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

La présente invention concerne un échangeur de chaleur à ailettes ayant une excellente performance de transfert de chaleur. Afin d'atteindre cette performance, la performance de transfert de chaleur entre un flux d'air et un grand nombre des ailettes empilées est améliorée en donnant aux ailettes une forme spéciale afin d'augmenter le nombre de lignes de crête qui sont les lignes sur lesquelles les surfaces se coupent. Chaque ailette de transfert de chaleur (20) d'un échangeur de chaleur à ailette comporte : une section d'ondulation (40) qui comprend des protubérances et un évidement ; des portions de siège (30) qui ont des surfaces plates concentriques avec des bagues d'ailettes (60) avec lesquelles les tuyaux de transfert de chaleur (50) sont joints de façon à être en contact étroit avec ces dernières ; des surfaces inclinées (30a) qui s'élèvent depuis les portions de siège (30) vers la section d'ondulation (40) ; et des protubérances intermédiaires (80) qui sont disposées à proximité des bagues d'ailettes (60) et qui sont formées par des lignes de crête côté protubérance s'étendant dans une direction en ligne dans l'évidement qui s'étend dans une direction d'étage.
PCT/JP2012/004172 2011-08-01 2012-06-27 Échangeur de chaleur à ailettes WO2013018270A1 (fr)

Priority Applications (2)

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JP2013526717A JP5958917B2 (ja) 2011-08-01 2012-06-27 フィンチューブ型熱交換器
CN201280037973.1A CN103717993B (zh) 2011-08-01 2012-06-27 翅片管型热交换器

Applications Claiming Priority (2)

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JP2011-168103 2011-08-01
JP2011168103 2011-08-01

Publications (1)

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WO2013018270A1 true WO2013018270A1 (fr) 2013-02-07

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JP (1) JP5958917B2 (fr)
CN (1) CN103717993B (fr)
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Cited By (1)

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JP2020063883A (ja) * 2018-10-18 2020-04-23 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 熱交換器及び空気調和機

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CN104848516A (zh) * 2015-06-15 2015-08-19 广州佳立空调技术有限公司 一种空调用层叠式管片及换热器
CN112066776A (zh) * 2020-08-04 2020-12-11 西安交通大学 一种用于空调换热器的仿生开缝波纹翅片

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JPS56103786U (fr) * 1979-12-29 1981-08-13
JPS63294494A (ja) * 1987-05-27 1988-12-01 Nippon Denso Co Ltd 熱交換器
JP2005090939A (ja) * 2003-09-15 2005-04-07 Lg Electronics Inc 熱交換器
WO2007108386A1 (fr) * 2006-03-23 2007-09-27 Matsushita Electric Industrial Co., Ltd. Echangeur de chaleur a tubes a ailettes, ailette d'echangeur de chaleur et dispositif de pompe a chaleur

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US4923002A (en) * 1986-10-22 1990-05-08 Thermal-Werke, Warme-Kalte-Klimatechnik GmbH Heat exchanger rib
JP2834339B2 (ja) * 1991-02-21 1998-12-09 松下電器産業株式会社 フィン付き熱交換器
JP3367353B2 (ja) * 1996-11-12 2003-01-14 松下電器産業株式会社 フィン付き熱交換器
KR100518854B1 (ko) * 2003-09-02 2005-09-30 엘지전자 주식회사 열교환기
JP3815491B2 (ja) * 2004-06-30 2006-08-30 ダイキン工業株式会社 熱交換器及び空気調和装置

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Publication number Priority date Publication date Assignee Title
JPS56103786U (fr) * 1979-12-29 1981-08-13
JPS63294494A (ja) * 1987-05-27 1988-12-01 Nippon Denso Co Ltd 熱交換器
JP2005090939A (ja) * 2003-09-15 2005-04-07 Lg Electronics Inc 熱交換器
WO2007108386A1 (fr) * 2006-03-23 2007-09-27 Matsushita Electric Industrial Co., Ltd. Echangeur de chaleur a tubes a ailettes, ailette d'echangeur de chaleur et dispositif de pompe a chaleur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2020063883A (ja) * 2018-10-18 2020-04-23 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． 熱交換器及び空気調和機

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JP5958917B2 (ja) 2016-08-02
CN103717993A (zh) 2014-04-09
JPWO2013018270A1 (ja) 2015-03-05
CN103717993B (zh) 2016-04-27

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