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WO2013161239A1 - Échangeur de chaleur à tubes à ailettes - Google Patents

Échangeur de chaleur à tubes à ailettes Download PDF

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Publication number
WO2013161239A1
WO2013161239A1 PCT/JP2013/002659 JP2013002659W WO2013161239A1 WO 2013161239 A1 WO2013161239 A1 WO 2013161239A1 JP 2013002659 W JP2013002659 W JP 2013002659W WO 2013161239 A1 WO2013161239 A1 WO 2013161239A1
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WO
WIPO (PCT)
Prior art keywords
inclined portion
heat exchanger
fin
tube heat
tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2013/002659
Other languages
English (en)
Japanese (ja)
Inventor
明広 重田
昭一 横山
正宣 広田
由樹 山岡
達夫 野瀬
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Priority to CN201380021241.8A priority Critical patent/CN104246408B/zh
Priority to JP2014512336A priority patent/JP6090699B2/ja
Publication of WO2013161239A1 publication Critical patent/WO2013161239A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the present invention relates to a finned-tube heat exchanger, and more particularly to a finned-tube heat exchanger that performs heat exchange using a refrigerant.
  • this type of finned tube heat exchanger (finned tube heat ⁇ ⁇ exchanger) has a wave-portion irregularity on the fin to promote heat transfer in response to the pursuit of high efficiency (for example, see Patent Document 1).
  • FIG. 14 (a) is a partial plan view of fins in the finned tube heat exchanger of Patent Document 1.
  • FIG. FIG. 14B and FIG. 14C are an AA sectional view and a BB sectional view of FIG. 14A, respectively.
  • the finned tube heat exchanger of Patent Document 1 has fins 101 and heat transfer tubes 102 as shown in FIGS. 14 (a) and 14 (c). As shown in FIG. 14C, a plurality of fins 101 are arranged in parallel at regular intervals, and air flows between them. As shown in FIG. 14A, the heat transfer tubes 102 are inserted into the fins 101 at a predetermined step pitch and row pitch at a substantially right angle, and the refrigerant flows inside.
  • the fin 101 includes a fin collar 109 and a tube peripheral portion 107.
  • the fin collar 109 protrudes from the surface of the fin 101 and passes the heat transfer tube 102.
  • the tube peripheral portion 107 has an annular shape with a diameter D and surrounds the fin collar 109 on the fin 101.
  • the fin 101 further includes a first inclined portion 105 and a second inclined portion 106.
  • the trough part 104a, the peak part 103, the trough part 104, the peak part 103, and the trough part 104a continue in order.
  • the fin 101 has a wave shape.
  • the 2nd inclination part 106 connects the pipe surrounding part 107 and the 1st inclination part 105 (the peak part 103).
  • the peak height H1 of the peak portion 103 is set to be larger than the distance Fp between adjacent fins 101 and smaller than twice the distance Fp. Thereby, the improvement of the heat transfer performance (namely, heat exchange performance) by a fin tube heat exchanger is aimed at.
  • FIG. 14C shows a finned tube heat exchanger in which the peak height H1 is substantially the same as the distance Fp.
  • the second inclined portion 106 is recessed.
  • the water condensed on the fins 101 accumulates and the condensed water 110 is generated.
  • the condensed water 110 increases the resistance to air flow and reduces the heat transfer area of the fins 101, resulting in a problem that the heat exchange performance of the finned tube heat exchanger is deteriorated.
  • This invention solves the said conventional subject, and it aims at providing the fin tube heat exchanger which improved the heat exchange performance.
  • a finned tube heat exchanger includes a plurality of fins through which air flows, a plurality of heat transfer tubes that pass through the plurality of fins and through which fluid flows.
  • the fin includes a first inclined portion inclined with respect to the air flow direction so as to form at least one peak, a tube surrounding portion surrounding the heat transfer tube passing through the first inclined portion, and a tube surrounding portion And a second inclined portion inclined with respect to the air flow direction so as to connect the first inclined portion and a through hole is formed in the second inclined portion, or the first inclined portion and the second inclined portion A recess is formed at the boundary with the part.
  • a finned tube heat exchanger with improved heat exchange performance can be provided.
  • FIG. 2 (a) (A) The figure explaining the drainage effect
  • the figure explaining the drainage action of a fin tube heat exchanger (A) A partial plan view of the fins and the periphery of the tube in the fin tube heat exchanger in the modification of the first embodiment, (b) AA sectional view of FIG. 4 (a), (c) FIG. 4 (a). BB sectional view of FIG. 4, (d) CC sectional view of FIG.
  • FIG. 8 Partial plan view of fins and tube peripheral portion of fin-tube heat exchanger in modification 6 of embodiment 2, (b) AA cross-sectional view of FIG. 8 (a), (c) FIG. BB sectional view of), (d) CC sectional view of FIG.
  • A Partial plan view of fins of the finned-tube heat exchanger in Embodiment 3, (b) AA sectional view of FIG. 9 (a), (c) BB sectional view of FIG.
  • BB sectional view A) Partial plan view of fins of a conventional fin tube heat exchanger, (b) AA sectional view of FIG. 14 (a), (c) BB sectional view of FIG. 14 (a) (A) The figure explaining the drainage action of the conventional fin tube heat exchanger, (b) The figure explaining the drainage action of the conventional fin tube heat exchanger, (c) The drainage action of the conventional fin tube heat exchanger Illustration to explain
  • a first invention includes a plurality of fins through which air flows and a plurality of heat transfer tubes that pass through the plurality of fins and through which fluid flows, and the fins form at least one peak portion. Air flow so as to connect the first inclined portion inclined with respect to the air flow direction, the tube peripheral portion surrounding the heat transfer tube penetrating the first inclined portion, and the tube peripheral portion and the first inclined portion.
  • a finned tube heat exchanger including a second inclined portion inclined with respect to a direction, and having a through hole formed in the second inclined portion.
  • the water flowing through the second inclined portion is drained from the front surface of the fin to the back surface through the through hole. Therefore, it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger.
  • the through-hole of the first invention is positioned below the lowest point of the pipe periphery in the direction of gravity.
  • the through hole below the lowest point of the pipe peripheral part the water that flows downward from the pipe peripheral part through the gravity can be drained from the surface of the fin, for example, to the back surface through the through hole. It is possible to improve water drainage. Therefore, it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger.
  • the through hole of the second aspect of the invention is arranged on the straight line connecting the lowest point of the pipe peripheral part in the direction of gravity and the intersection of the second inclined part and the peak part of the first inclined part.
  • the straight line extends along the direction of gravity.
  • the through hole of the first invention is a cut formed at the boundary between the first inclined portion and the second inclined portion.
  • the water flowing through the second inclined portion is drained, for example, from the front surface of the fin to the back surface through a cut formed at the boundary between the first inclined portion and the second inclined portion. Therefore, it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger.
  • the cut according to the fourth invention is located at the lower end of the second inclined portion in the direction of gravity.
  • the water when water flows downward in the direction of gravity in the second inclined portion and reaches the lower end of the second inclined portion, the water is drained, for example, from the front surface of the fin to the back surface through a notch provided at the lower end.
  • the water drainage By improving the water drainage in this way, it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger. it can.
  • a cut is further formed at the upper end of the second inclined portion in the direction of gravity at the boundary between the first inclined portion and the second inclined portion of the fifth invention.
  • the water that has reached the uppermost point flows through the notch, for example, from the back surface of the fin to the surface, and the water that has reached the lowest point, for example, from the front surface of the fin to the back surface It flows into and drains.
  • the heat exchange performance of the finned tube heat exchanger is improved. Can be improved.
  • a seventh invention includes a plurality of fins through which air flows, and a plurality of heat transfer tubes that pass through the plurality of fins and through which fluid flows, and the fins form at least one peak portion. Air flow so as to connect the first inclined portion inclined with respect to the air flow direction, the tube peripheral portion surrounding the heat transfer tube penetrating the first inclined portion, and the tube peripheral portion and the first inclined portion. It is a finned tube heat exchanger that includes a second inclined portion that is inclined with respect to the direction and in which a recess is formed at the boundary between the first inclined portion and the second inclined portion.
  • a water drainage channel is formed by the recess formed at the boundary between the second inclined portion and the first inclined portion. Therefore, it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger.
  • the crests and troughs are alternately formed, and the recess sandwiches the intersection of the second inclined portion and the crest of the first inclined portion. Two are provided in the vicinity of the intersection,
  • the water staying in the second inclined portion is guided to the first inclined portion through the concave portion, and further guided to the valley portion formed in the first inclined portion, and smoothly drained downward in the gravity direction. Is done.
  • By improving the water drainage in this way it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, it is possible to improve the heat exchange performance of the finned tube heat exchanger. it can.
  • the distance between the concave portion and the intersection of the seventh or eighth invention is within twice the pitch of the fins.
  • Embodiment 1-3 of the present invention will be described with reference to the drawings. Note that the present invention is not limited to these Embodiments 1-3.
  • FIG. 1 is a configuration diagram of a finned-tube heat exchanger according to Embodiment 1 of the present invention.
  • Fig.2 (a) is a partial top view of the fin 1 of the fin tube heat exchanger.
  • 2 (b), 2 (c) and 2 (d) are cross-sectional views taken along lines AA, BB and CC, respectively, of FIG. 2 (a).
  • FIGS. 3A to 3C are views for explaining the drainage action of the finned tube heat exchanger.
  • the fin tube heat exchanger includes a plurality of fins 1, a plurality of heat transfer tubes 2, and an end plate 20.
  • the plurality of fins 1 are stacked such that a flow path is formed in the air flow direction S and the distance between them is a predetermined pitch Fp. Air flows between each of the plurality of fins 1.
  • the plurality of heat transfer tubes 2 pass through the plurality of fins 1 and are arranged along the vertical direction. A fluid flows inside the heat transfer tube 2.
  • the end plate 20 is used as a fixing part when the fin tube heat exchanger is placed on the outdoor unit, and is also used as a connection part for connecting a plurality of fin tube heat exchangers to each other.
  • the fin 1 has a valley portion 4a, a mountain portion 3, a valley portion 4, a mountain portion 3, and a valley portion 4a successively arranged along the air flow direction S.
  • This is a corrugated fin having a wave shape.
  • the peak part 3 and the trough part 4 exist also between the adjacent heat exchanger tubes 2, as shown to Fig.2 (a).
  • the ridge line of the mountain part 3 and the valley line of the valley part 4 are substantially parallel to each other.
  • the fin 1 further includes a cylindrical fin collar 9. By performing mechanical expansion or hydraulic expansion on the heat transfer tube 2 inserted into the fin collar 9, the fin 1 and the heat transfer tube 2 are joined to each other.
  • the fin 1 includes a first inclined portion 5 inclined with respect to the air flow direction S so as to form alternately continuous peaks 3 and valleys 4, and a first inclination.
  • FIG. 2 illustrates a finned tube heat exchanger in which the tube peripheral portion 7 is formed as a flat portion parallel to the air flow direction S.
  • the present invention is not limited to such a case, and the air flow direction S It may be inclined with respect to, and may be an undulating portion.
  • the notch 8 is provided at the boundary between the first inclined portion 5 and the second inclined portion 6 (that is, the ridge line formed by the first inclined portion 5 and the second inclined portion 6). It has been.
  • the cuts 8 extend in two directions (generally in the vertical direction and the horizontal direction) from the intersection of the first inclined portion 5 (the crest portion 3) and the second inclined portion 6, respectively.
  • the length L of the cut 8 on the ridge line extending from the intersection may be set to about 0.5 Fp to 1.5 Fp, for example.
  • the width W of the notch 8 shown in FIG. 2 (d) may be set to such a length that water can be guided to the back side (that is, the valley) of the peak 3 by capillary action.
  • the width W may be set to about 0.05 mm to 0.5 mm, the capillary phenomenon can be generated more favorably.
  • the finned tube heat exchanger in the first embodiment performs heat exchange between the air passing between the plurality of fins 1 and the refrigerant flowing inside the plurality of heat transfer tubes 2.
  • the refrigerant flowing inside the heat transfer tube 2 may be, for example, R410A, propane, propylene, carbon dioxide or the like having a low environmental load, but is not particularly limited thereto.
  • 3A to 3C are arranged in time series (in chronological order).
  • the accumulated water 10 deposited on the pipe peripheral portion 7 and the second inclined portion 6 shown in FIG. 3 (a) passes through the notches 8, that is, on the back side of the fin 1, that is, on the peak portion 3. Guided to the valley on the back side.
  • the accumulated water 10 is drained before it becomes water droplets.
  • the fin tube heat exchanger is used as an evaporator by providing the notch 8 in the ridgeline formed by the first inclined portion 5 and the second inclined portion 6.
  • the staying water 10 staying in the second inclined portion 6 can be smoothly guided and drained downward in the gravity direction G through the notch 8. Therefore, an increase in ventilation resistance and a decrease in the heat transfer area of the fin can be suppressed, and the heat exchange performance of the fin tube heat exchanger can be improved.
  • frost may adhere to the surface of the fin 1, and even when the frost melts, water remains in the second inclined portion 6, but the fin tube heat exchange according to the first embodiment is performed. According to the vessel, the accumulated water can be drained smoothly. Therefore, it can suppress that frost grows again and can reduce the frequency which melts frost, and can improve the energy efficiency as a heat pump apparatus as a result.
  • the notches 8 are formed at the intersections of the first inclined portion 5 (the crest portion 3) and the second inclined portion 6, and are formed at the upper and lower ends of the second inclined portion 6 in the direction of gravity. Thereby, the terminal end of the notch 8 and the upper end and lower end of the 2nd inclination part 6 in a gravitational direction contact
  • the accumulated water 10 flowing on the back side of the fin 1 is smoothly guided to the front side of the fin 1, and the lower end of the second inclined portion 6.
  • the stagnant water 10 is smoothly guided to the back side of the fin 1 and then drained downward in the gravity direction G as needed. Therefore, the heat exchange performance of the fin tube heat exchanger can be improved.
  • the notch 8 is located at the lower end of the second inclined portion 6 in the gravity direction G, so that water flows downward in the gravity direction G in the second inclined portion 6.
  • water is drained from the front surface of the fin 1 to the back surface through the notches 8 provided at the lower end.
  • the smooth drainage flow is generated in the second inclined portion 6, so that it is possible to suppress an increase in ventilation resistance and a decrease in heat transfer area due to water, and as a result, heat exchange of the finned tube heat exchanger Performance can be improved.
  • the cuts 8 are formed in both the upper and lower ridge lines of the heat transfer tube 2 in the gravity direction G.
  • the present invention is not limited to this case. Since the accumulated water 10 is often generated around the heat transfer tube 2, for example, if the cuts 8 are formed at least in the ridge line on the lower side of the heat transfer tube 2, the drainage performance as a finned tube heat exchanger can be improved.
  • the fin 1 may be a V-shaped corrugated fin in which the peak portion 3 is formed only at one place. According to the V-shaped corrugated fin, the number of meandering times of the air flowing between the fins 1 can be minimized while keeping the heat transfer area of the fins 1. Therefore, increase in ventilation resistance can be suppressed and blowing noise can be reduced.
  • Embodiment 2 Next, the finned-tube heat exchanger in Embodiment 2 of this invention is demonstrated using FIGS. 5-7.
  • FIG. 5A is a partial plan view of the fins 31 of the finned tube heat exchanger according to the second embodiment.
  • FIGS. 5B, 5C and 5D are cross-sectional views taken along lines AA, BB and CC in FIG. 5A, respectively.
  • 6 (a) -6 (e) are partial plan views showing the detailed shapes of the through holes formed in the fins 31 of the fin tube heat exchanger in Modification 1-5 of Embodiment 2.
  • FIG. 7 (a) -7 (c) are views for explaining the drainage action of the finned tube heat exchanger.
  • the finned-tube heat exchanger according to the second embodiment as compared with the finned-tube heat exchanger according to the first embodiment, not only the cut formed between the first inclined part and the second inclined part. The difference is that a through hole is formed in the second inclined portion. Since the other configuration is common, the description is omitted.
  • a through-hole that communicates (penetrates) the front and back of the fin 31 on the second inclined portion 36 and in the vicinity of the intersection of the peak portion 33 of the first inclined portion 35 and the second inclined portion 36. 38 is provided.
  • a part of the through hole 38 is in contact with the intersection of the peak portion 33 of the first inclined portion 35 and the second inclined portion 36, but may not be in contact.
  • the 2nd inclination part 36 and the pipe surrounding part 37 may be shape
  • the through-hole 38 is formed below the heat transfer tube 32 in the gravity direction G and below the intersection 60 between the valley portion 34 of the first inclined portion 35 and the second inclined portion 36.
  • the through-hole 38 is formed at a place where it tends to stay. Thereby, drainage can be improved more.
  • the through hole 38 is formed above the heat transfer tube 32 in the gravity direction G and above the intersection 61 between the valley portion 34 of the first inclined portion 35 and the second inclined portion 36, the fin The water flowing on 31 can be guided to the front side or the back side of the fin 31. Thereby, drainage can be improved more.
  • the diameter D of the through hole 38 shown in FIG. 5D may be set to, for example, about 0.2 mm to 1.0 mm, or about 0.1 Fp to Fp.
  • the shape of the through hole 38 is a circular shape that is relatively easy to process as shown in FIG. 5, but is not limited thereto.
  • FIGS. 6A to 6E show through holes of a finned-tube heat exchanger according to Modification 1-5 of the second embodiment.
  • the shape of the through hole 38a is an ellipse.
  • the shape of the through hole 38b is a triangle.
  • the shape of the through-hole 38c is a rhombus.
  • the shapes of the through holes 38d and 38e are geometric shapes.
  • the equivalent diameter De may be applied instead of the diameter D.
  • the air passing between the plurality of stacked fins 31 meanders by being meandered by the peaks 33, valleys 34, and valleys 34 a formed in the fins 1.
  • a flow Sc is formed.
  • turbulent flow can be promoted and the temperature boundary layer can be made thinner, and as a result, the heat exchange performance in the finned tube heat exchanger can be improved.
  • the staying water 40 that is deposited on the pipe periphery 37 and stays in the second inclined portion 36 is shown in FIG. As shown in FIG. 6, it is guided to the back side of the fin 31, that is, the trough portion on the back side of the peak portion 33 through the through hole 38. Finally, as shown in FIG. 7 (c), almost all of the water is drained. In this way, the accumulated water 40 can be drained at any time before it becomes water droplets.
  • the fin tube is particularly provided.
  • the heat exchanger is used as an evaporator, the accumulated water 40 retained in the second inclined portion 36 can be smoothly guided and drained downward in the gravity direction G through the through hole 38. Therefore, an increase in ventilation resistance and a decrease in the heat transfer area of the fins 31 can be suppressed, and the heat exchange performance of the fin tube heat exchanger can be improved.
  • the through hole 38 is formed in the second inclined portion 36, the water flowing through the second inclined portion 36 is drained from the surface of the fin 31 to the back surface through the through hole 38, for example. Thereby, the increase in the ventilation resistance by water and the reduction in the heat transfer area can be suppressed, and as a result, the heat exchange performance of the finned tube heat exchanger can be improved.
  • the through hole 38 is formed as a water drainage path, the strength of the fin 31 after the formation is small, and it is not necessary to perform a reinforcing process such as a rib or a bead. Therefore, an increase in design man-hours can be suppressed.
  • FIGS. 8 (a) to 8 (d) a finned tube heat exchanger according to Modification 6 of Embodiment 2 is shown in FIGS. 8 (a) to 8 (d).
  • the fin 31 may be a V-shaped corrugated fin in which the crest 33 is formed only at one place.
  • the through-hole 38 is formed on the second inclined portion 36 and below the lowest point of the pipe surrounding portion 37 in the gravity direction G, the through-hole is formed at a location where water is likely to stay. 38 will be formed. Thereby, drainage can be improved more. Further, when the through hole 38 is formed on the second inclined part 36 and above the uppermost point of the pipe surrounding part 37 in the gravity direction G, the water flowing through the fin 31 is allowed to flow on the front side or the back side of the fin. Can be guided to. Thereby, drainage can be improved more.
  • the through-hole 38 is formed on a straight line connecting the lowest point of the tube peripheral portion 37 in the gravity direction G and the intersection 62 of the peak portion 33 of the first inclined portion 35 and the second inclined portion 36, Water can be guided more smoothly to improve drainage. Furthermore, if this straight line extends along the gravity direction G, the drainage can be further improved.
  • Embodiment 3 Next, the finned-tube heat exchanger in Embodiment 3 of this invention is demonstrated using FIGS. 9-12.
  • FIG. 9A is a partial plan view of the fins 71 of the finned tube heat exchanger according to the third embodiment.
  • FIGS. 9B and 9C are cross-sectional views taken along lines AA and BB in FIG. 9A, respectively.
  • FIG. 10 is a cross-sectional view showing the detailed shape of the recess 78 of the finned tube heat exchanger according to the third embodiment.
  • FIG. 11 is a cross-sectional view showing a detailed shape of the concave portion 78 of the finned tube heat exchanger in the first modification of the third embodiment.
  • 12 (a) -12 (c) are views for explaining the drainage action of the funnel heat exchanger.
  • a recess is formed at the boundary (ridge line) between the first inclined portion and the second inclined portion as compared with the fin tube heat exchanger according to the first and second embodiments. Since the difference is formed and the other configurations are common, the description is omitted.
  • one recess 78 is formed on each side of the intersection.
  • the position near the intersection where the recess 78 is formed means, for example, a position where the distance L between the recess 78 (the center position thereof) and the intersection is within about twice the pitch Fp of the fins 71.
  • the concave portion 78 is formed at a position lower than the highest point on the boundary (ridge line) between the first inclined portion 75 and the second inclined portion 76, that is, at a position where water tends to stay. Therefore, it can drain more smoothly.
  • the dimension (width length) X of the opening of the recess 78 may be set within about 0.05 mm to 0.5 mm, for example. By setting in this way, water can be guided more smoothly by capillary action.
  • the side surface 78a of the recess 78 is inclined and connected by the bottom surface 78b as shown in FIG. 10, but the shape is not limited to this.
  • the side surface 78a may be formed vertically. Further, the side surfaces 78a may be directly contacted without forming the bottom surface 78b, and may have a pointed shape (V shape).
  • the concave portion 78 forms a single groove.
  • the depth Y of the recess 78 may be set to about 0.1 h to 0.6 h.
  • the inclined water 75 can be more smoothly guided to the first inclined portion 75 by tilting ⁇ 15 ° to 90 ° with respect to the direction in which the ridge line of the portion 73 extends.
  • the fin tube heat exchanger of the third embodiment for example, when the temperature of the fin tube heat exchanger is equal to or lower than the dew point temperature of the surrounding air, or when rain enters the fin tube heat exchanger, As shown in FIG. 12A, stagnant water 80 is generated in the pipe peripheral portion 77, the second inclined portion 76, and the like.
  • the accumulated water 80 on the second inclined portion 76 travels along the recess 78, and the boundary between the first inclined portion 75 and the second inclined portion 76 (the first inclined portion 75 and the first inclined portion 75).
  • the ridgeline formed by the two inclined portions 76 is overcome and guided downward in the gravity direction G.
  • the drainage can be improved.
  • the concave portions 78 are formed on both sides of the intersection of the mountain portion 73 of the first inclined portion 75 and the second inclined portion 76 and on the ridge line of the mountain portion 73 in the vicinity of the intersection point. It is provided so that it may incline with respect to it. Therefore, the stagnant water 80 that has passed through the recess 78 and has overcome the ridgeline formed by the first inclined portion 75 and the second inclined portion 76 is formed along the inclination of the first inclined portion 75 along the valley portion 74 and the valley portion. Guided toward 74a. The stagnant water 80 then flows downward in the direction of gravity G through the valley 74 and valley 74a.
  • the recessed part 78 forms the drainage path
  • the drainage property as a finned-tube heat exchanger can be improved. Therefore, an increase in ventilation resistance and a decrease in heat transfer area can be suppressed, and the heat exchange performance of the finned tube heat exchanger can be improved.
  • the concave portion 78 is formed at the boundary between the first inclined portion 75 and the second inclined portion 76, and the water drainage path is formed by the concave portion 78, the increase of the ventilation resistance due to water and the reduction of the heat transfer area are reduced. Therefore, the heat exchange performance of the finned tube heat exchanger can be improved.
  • the shape of the concave portion 78 may be made in a mold for pressing the fin 71. Therefore, a finned tube heat exchanger with improved drainage can be manufactured without increasing the number of steps.
  • the crests 73 and the troughs 74 are alternately formed, and the concave portion 78 is formed between the crest 73 of the first inclined portion 75 and the second inclined portion 76.
  • Two are provided in the vicinity of the intersection so as to sandwich the intersection.
  • the water staying in the second inclined portion 76 is guided to the first inclined portion 75 through the concave portion 78 and further guided to the valley portion 74 formed by the first inclined portion 75, and the gravity direction G
  • the water is smoothly drained downward.
  • the distance between the recess 78 and the intersection is within twice the pitch Fp of the fins 71.
  • the recessed part 78 was formed in both the upper ridgeline and the lower ridgeline of the heat exchanger tube 72 in the gravity direction G, it is not restricted to such a case. Since a large amount of the retained water 80 is generated around the heat transfer tube 72, for example, if the concave portion 78 is formed at least on the lower ridgeline, the drainage performance as a finned tube heat exchanger can be improved.
  • the finned tube heat exchanger in the second modification of the third embodiment is shown in FIGS. 13 (a) to 13 (c).
  • the fin 71 may be a V-shaped corrugated fin in which the crest 73 is formed only at one place.
  • this invention is not limited to the above-mentioned structure, It can implement in another various aspect.
  • the heat transfer tube is a round tube has been described.
  • the present invention is not limited to such a case, and may be a flattened tube.
  • the finned tube heat exchanger according to the first to third embodiments can be applied to a heat exchanger used in an air conditioner, a hot water supply device, a heating device, or the like.

Landscapes

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

Abstract

La présente invention concerne un échangeur de chaleur à tubes à ailettes qui comporte une pluralité d'ailettes et de tubes de transfert de chaleur. Les ailettes comprennent une première partie inclinée qui est inclinée par rapport à la direction d'écoulement de l'air de manière à former au moins une section de pointe, une partie périphérie de tube qui entoure un tube de transfert de chaleur traversant la première partie inclinée, et une seconde partie inclinée qui est inclinée par rapport à la direction d'écoulement de l'air de manière à raccorder la partie périphérie de tube et la première partie inclinée. Un trou traversant est formé dans la seconde partie inclinée ou bien une partie concave est formée dans le bord entre la première partie inclinée et la seconde partie inclinée. Il résulte de cette configuration que l'efficacité d'échange de chaleur de l'échangeur de chaleur à tubes à ailettes est améliorée.
PCT/JP2013/002659 2012-04-23 2013-04-19 Échangeur de chaleur à tubes à ailettes Ceased WO2013161239A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201380021241.8A CN104246408B (zh) 2012-04-23 2013-04-19 翅片管热交换器
JP2014512336A JP6090699B2 (ja) 2012-04-23 2013-04-19 フィンチューブ熱交換器

Applications Claiming Priority (6)

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JP2012097379 2012-04-23
JP2012-097379 2012-04-23
JP2012099467 2012-04-25
JP2012-099467 2012-04-25
JP2012099462 2012-04-25
JP2012-099462 2012-04-25

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WO2013161239A1 true WO2013161239A1 (fr) 2013-10-31

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Cited By (1)

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WO2016198664A1 (fr) * 2015-06-12 2016-12-15 Valeo Systemes Thermiques Ailette d'un échangeur thermique notamment pour véhicule automobile, et échangeur thermique correspondant

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JPS5439764U (fr) * 1977-08-25 1979-03-16
JPH08189790A (ja) * 1995-01-04 1996-07-23 Daikin Ind Ltd フィン付熱交換器
JPH10141880A (ja) * 1996-11-12 1998-05-29 Matsushita Electric Ind Co Ltd フィン付き熱交換器

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JPS5569288U (fr) * 1978-11-01 1980-05-13
JPS5761375U (fr) * 1980-09-19 1982-04-12
JPH01256795A (ja) * 1988-04-07 1989-10-13 Matsushita Electric Ind Co Ltd フィン付熱交換器
JPH0229597A (ja) * 1988-07-15 1990-01-31 Matsushita Refrig Co Ltd 熱交換器
JP2600410Y2 (ja) * 1993-11-01 1999-10-12 東洋ラジエーター株式会社 空調用熱交換器
JP3367395B2 (ja) * 1997-10-22 2003-01-14 松下電器産業株式会社 フィン付き熱交換器
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JP2006038311A (ja) * 2004-07-26 2006-02-09 Daikin Ind Ltd フィンチューブ式熱交換器
JP5166062B2 (ja) * 2008-02-15 2013-03-21 株式会社ティラド 熱交換器の製造方法および熱交換器
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KR20110083020A (ko) * 2010-01-13 2011-07-20 엘지전자 주식회사 열 교환기

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JPS5439764U (fr) * 1977-08-25 1979-03-16
JPH08189790A (ja) * 1995-01-04 1996-07-23 Daikin Ind Ltd フィン付熱交換器
JPH10141880A (ja) * 1996-11-12 1998-05-29 Matsushita Electric Ind Co Ltd フィン付き熱交換器

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016198664A1 (fr) * 2015-06-12 2016-12-15 Valeo Systemes Thermiques Ailette d'un échangeur thermique notamment pour véhicule automobile, et échangeur thermique correspondant
FR3037388A1 (fr) * 2015-06-12 2016-12-16 Valeo Systemes Thermiques Ailette d'un echangeur thermique notamment pour vehicule automobile, et echangeur thermique correspondant

Also Published As

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JP6090699B2 (ja) 2017-03-08
CN104246408B (zh) 2016-06-15
CN104246408A (zh) 2014-12-24
JPWO2013161239A1 (ja) 2015-12-21

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