WO2013054508A1 - フィンチューブ熱交換器 - Google Patents

フィンチューブ熱交換器 Download PDF

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Publication number
WO2013054508A1
WO2013054508A1 PCT/JP2012/006469 JP2012006469W WO2013054508A1 WO 2013054508 A1 WO2013054508 A1 WO 2013054508A1 JP 2012006469 W JP2012006469 W JP 2012006469W WO 2013054508 A1 WO2013054508 A1 WO 2013054508A1
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WIPO (PCT)
Prior art keywords
fin
heat transfer
heat exchanger
angle
reference plane
Prior art date
Application number
PCT/JP2012/006469
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English (en)
French (fr)
Japanese (ja)
Inventor
健二 名越
雅也 本間
岡市　敦雄
長谷川　寛
周平 大坪
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.)
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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 CN201280050084.9A priority Critical patent/CN103890527B/zh
Priority to JP2013538435A priority patent/JP5958771B2/ja
Priority to EP12840153.6A priority patent/EP2767791B1/en
Publication of WO2013054508A1 publication Critical patent/WO2013054508A1/ja

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    • 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
    • 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
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings

Definitions

  • the present invention relates to a finned tube heat exchanger.
  • the finned tube heat exchanger is composed of a plurality of fins arranged at predetermined intervals and a heat transfer tube penetrating the plurality of fins. The air flows between the fins and exchanges heat with the fluid in the heat transfer tubes.
  • FIGS. 9A to 9D are respectively a plan view of fins used in a conventional fin tube heat exchanger, a sectional view taken along line IXB-IXB, a sectional view taken along line IXC-IXC, and a line taken along line IXD-IXD.
  • FIG. The fin 10 is formed so that the peaks 4 and the valleys 6 appear alternately in the airflow direction.
  • Such fins are commonly referred to as “corrugated fins”. According to the corrugated fin, not only the effect of increasing the heat transfer area but also the effect of thinning the temperature boundary layer by meandering the air flow 3 can be obtained.
  • Cut and raised portions 41a, 41b, 41c and 41d are provided on the fin inclined surfaces 42a, 42b, 42c and 42d of the fin 1.
  • the heights H1, H2, H3, and H4 of the cut-and-raised portions 41a, 41b, 41c, and 41d are 1/5 ⁇ Fp ⁇ (H1, H2, H3, H4) ⁇ 1 when the distance between adjacent fins 1 is Fp. / 3 ⁇ Fp is satisfied.
  • Patent Document 1 also describes another fin configured to reduce the ventilation resistance during the frosting operation as much as possible.
  • the fin inclined surfaces 12a and 12b of the fin 1 are provided with cut-and-raised portions 11a and 11b that satisfy the above-described relationship. Since the number of times of bending of the fin 1 is small, the inclination angles of the fin inclined surfaces 12a and 12b are relatively gentle.
  • This invention aims at providing the finned-tube heat exchanger which has the outstanding basic performance irrespective of the time of frost operation and non-frost operation.
  • a heat transfer tube configured to pass through the plurality of fins and to have a medium that exchanges heat with the gas flow therein;
  • the fin is a corrugated fin formed so that a peak portion appears only at one place in the airflow direction, and a plurality of through holes in which the heat transfer tubes are fitted, and a flat portion formed around the through holes And a first inclined part that is inclined with respect to the airflow direction so as to form the mountain part, and a second inclined part that connects the flat part and the first inclined part,
  • the plurality of through holes are formed along a step direction perpendicular to both the direction of arrangement of the plurality of fins and the airflow direction,
  • the length of the fin in the airflow direction is S1
  • the distance between the centers of the heat transfer tubes in the step direction is S2
  • the diameter of the flat portion is D1
  • the perspective view of the finned-tube heat exchanger which concerns on one Embodiment of this invention.
  • FIG. 9A Top view of another fin used in a conventional fin tube heat exchanger Sectional drawing along the XB-XB line of the fin shown in FIG. 10A Sectional drawing along the XC-XC line of the fin shown in FIG. 10A
  • the first aspect of the present disclosure is: A plurality of fins arranged in parallel to form a gas flow path; A heat transfer tube configured to pass through the plurality of fins and to have a medium that exchanges heat with the gas flow therein;
  • the fin is a corrugated fin formed so that a peak portion appears only at one place in the airflow direction, and a plurality of through holes in which the heat transfer tubes are fitted, and a flat portion formed around the through holes And a first inclined part that is inclined with respect to the airflow direction so as to form the mountain part, and a second inclined part that connects the flat part and the first inclined part,
  • the plurality of through holes are formed along a step direction perpendicular to both the direction of the plurality of fins and the airflow direction,
  • the length of the fin in the airflow direction is S1
  • the distance between the centers of the heat transfer tubes in the step direction is S2
  • the diameter of the flat portion is D1
  • the angle ⁇ 2 satisfies a relationship of tan ⁇ 1 ⁇ (S1 ⁇ tan ⁇ 1 ⁇ 2 ⁇ ) / (S2-D1) ⁇ ⁇ ⁇ 2 ⁇ 70 ° ⁇ 1.
  • a finned tube heat exchanger is provided.
  • the fin in addition to the first or second aspect, is configured to prohibit the flow of the gas from the front side to the back side of the fin in other regions excluding the plurality of through holes.
  • a finned tube heat exchanger Provided is a finned tube heat exchanger.
  • the fourth aspect of the present disclosure is: A plurality of fins arranged in parallel to form a gas flow path; A heat transfer tube configured to pass through the plurality of fins and to have a medium that exchanges heat with the gas flow therein;
  • the fin is a corrugated fin formed so that a peak portion appears only at one place in the airflow direction, and is closely attached to the heat transfer tube around the through hole in which the heat transfer tube is fitted.
  • the plurality of through holes are formed along a step direction perpendicular to both the direction of arrangement of the plurality of fins and the airflow direction,
  • the length of the fin in the airflow direction is S1
  • the distance between the centers of the heat transfer tubes in the step direction is S2
  • the outer diameter of the fin collar is D2
  • the upstream end and the downstream end of the fin in the airflow direction are passed.
  • a plane is defined as a reference plane
  • an angle formed between the reference plane and the first inclined portion is defined as ⁇ 1
  • an angle formed between the reference plane and the second inclined portion is defined as ⁇ 2.
  • a finned tube heat exchanger that satisfies the relationship of tan ⁇ 1 ⁇ (S1 ⁇ tan ⁇ 1) / (S2-D2) ⁇ ⁇ ⁇ 2 ⁇ 80 ° ⁇ 1.
  • the angle ⁇ 2 satisfies the relationship of tan ⁇ 1 ⁇ (S1 ⁇ tan ⁇ 1) / (S2-D2) ⁇ ⁇ ⁇ 2 ⁇ 70 ° ⁇ 1.
  • the fins prohibit the flow of the gas from the front side to the back side of the fins in other regions excluding the plurality of through holes.
  • a finned tube heat exchanger Provided is a finned tube heat exchanger.
  • the finned tube heat exchanger 100 of the present embodiment passes through a plurality of fins 31 arranged in parallel to form a flow path of air A (gas) and these fins 31. And a heat transfer tube 21.
  • the finned tube heat exchanger 100 is configured to exchange heat between the medium B flowing inside the heat transfer tube 21 and the air A flowing along the surface of the fin 31.
  • the medium B is a refrigerant such as carbon dioxide or hydrofluorocarbon.
  • the heat transfer tube 21 may be connected to one or may be divided into a plurality.
  • the fin 31 has a front edge 30a and a rear edge 30b.
  • the front edge 30a and the rear edge 30b are each linear.
  • the fins 31 have a symmetrical structure with respect to the center of the heat transfer tube 21. Therefore, it is not necessary to consider the direction of the fins 31 when assembling the heat exchanger 100.
  • the arrangement direction of the fins 31 is defined as the height direction
  • the direction parallel to the front edge 30a is defined as the step direction
  • the height direction and the direction perpendicular to the step direction are defined as the airflow direction (the flow direction of the air A).
  • the step direction is a direction perpendicular to both the height direction and the airflow direction.
  • the airflow direction is perpendicular to the longitudinal direction of the fins 31.
  • the airflow direction, the height direction, and the step direction correspond to the X direction, the Y direction, and the Z direction, respectively.
  • the fin 31 typically has a rectangular and flat plate shape.
  • the longitudinal direction of the fin 31 coincides with the step direction.
  • the fins 31 are arranged at a constant interval (fin pitch FP).
  • the interval between the two fins 31 adjacent to each other in the height direction is not necessarily constant, and may be different.
  • the fin pitch FP is adjusted to a range of 1.0 to 1.5 mm, for example.
  • the fin pitch FP is represented by the distance between two adjacent fins 31.
  • the constant width portion including the front edge 30a and the constant width portion including the rear edge 30b are parallel to the airflow direction. However, these portions are portions used for fixing the fins 31 to the mold during molding, and do not greatly affect the performance of the fins 31.
  • a flat plate made of aluminum having a thickness of 0.05 to 0.8 mm that has been punched can be suitably used as the material of the fin 31 .
  • the surface of the fin 31 may be subjected to hydrophilic treatment such as boehmite treatment or application of a hydrophilic paint. It is also possible to perform a water repellent treatment instead of the hydrophilic treatment.
  • a plurality of through holes 37h are formed in a row and at equal intervals along the step direction. Straight lines passing through the centers of the plurality of through holes 37h are parallel to the step direction.
  • the heat transfer tube 21 is fitted in each of the plurality of through holes 37h.
  • a cylindrical fin collar 37 is formed by a part of the fin 31 around the through hole 37h, and the fin collar 37 and the heat transfer tube 21 are in close contact with each other.
  • the diameter of the through hole 37h is, for example, 1 to 20 mm, and may be 4 mm or less.
  • the diameter of the through-hole 37 h matches the outer diameter of the heat transfer tube 21.
  • the center distance (pipe pitch) between two through holes 37h adjacent to each other in the step direction is, for example, 2 to 3 times the diameter of the through hole 37h.
  • the length of the fin 31 in the airflow direction is, for example, 15 to 25 mm.
  • the fin 31 is formed so that the mountain portion 34 appears only in one place in the airflow direction.
  • the ridge line of the mountain portion 34 is parallel to the step direction. That is, the fin 31 is a fin called a corrugated fin. If a portion projecting in the same direction as the projecting direction of the fin collar 37 is defined as a “mountain portion 34”, in the present embodiment, the fin 31 has only one mountain portion 34 in the airflow direction.
  • the front edge 30a and the rear edge 30b correspond to the valleys. In the airflow direction, the position of the mountain portion 34 coincides with the center position of the heat transfer tube 21.
  • the fin 31 is configured to prohibit the flow of air A from the front side (upper surface side) to the back side (lower surface side) of the fin 31 in other regions excluding the plurality of through holes 37h. Yes.
  • no opening other than the through hole 37h is provided in the fin 31. If there is no opening, there is no problem of clogging due to frost formation, which is advantageous in terms of pressure loss.
  • no opening is provided means that no slit, louver or the like is provided, that is, no hole penetrating the fin is provided.
  • the fin 31 further includes a flat portion 35, a first inclined portion 36, and a second inclined portion 38.
  • the flat portion 35 is a portion adjacent to the fin collar 37 and an annular portion formed around the through hole 37h.
  • the surface of the flat part 35 is parallel to the airflow direction and perpendicular to the height direction.
  • the first inclined portion 36 is a portion inclined with respect to the airflow direction so as to form the mountain portion 34.
  • the first inclined portion 36 occupies the widest area in the fin 31.
  • the surface of the first inclined portion 38 is flat.
  • the first inclined portions 36 are located on the left and right sides of a reference line that is parallel to the step direction and passes through the center of the heat transfer tube 21.
  • the peak portion 34 is formed by the first slope portion 36 on the windward side and the first slope portion 36 on the leeward side.
  • the second inclined portion 38 is a portion that smoothly connects the flat portion 35 and the first inclined portion 36 so as to eliminate the difference in height between the flat portion 35 and the first inclined portion 36. .
  • the surface of the second inclined portion 38 is a gently curved surface.
  • the flat portion 35 and the second inclined portion 39 form a concave portion around the fin collar 37 and the through hole 37h.
  • an appropriate radius for example, R0.5 mm to R2.0 mm
  • an appropriate radius for example, R0.5 mm to R2.0 mm
  • Such a round improves the drainage of the fin 31.
  • the length of the fin 31 in the airflow direction is defined as S1.
  • the center-to-center distance (tube pitch) of the heat transfer tubes 21 in the step direction is defined as S2.
  • the diameter of the flat part 35 is defined as D1.
  • a plane passing through the upstream end and the downstream end of the fin 31 in the airflow direction is defined as a reference plane H1.
  • the upstream end and the downstream end of the fin 31 correspond to the leading edges 30a and 30b, respectively.
  • An angle formed by the reference plane H1 and the first inclined portion 36 is defined as ⁇ 1.
  • An angle formed by the reference plane H1 and the second inclined portion 38 is defined as ⁇ 2.
  • the angle ⁇ ⁇ b> 1 is an acute angle side among the angles formed by the reference plane H ⁇ b> 1 and the first inclined portion 36.
  • the angle ⁇ ⁇ b> 2 is an acute angle side angle among the angles formed by the reference plane H ⁇ b> 1 and the second inclined portion 38.
  • the angle ⁇ 1 and the angle ⁇ 2 are respectively referred to as “first inclination angle ⁇ 1” and “second inclination angle ⁇ 2”.
  • the distance from the reference plane H1 to the flat portion 35 is defined as ⁇ . In the embodiment shown in FIGS. 2A-2D, the distance ⁇ is zero. That is, in the height direction, the position of the flat portion 35, the position of the front edge 30a, and the position of the rear edge 30b coincide. At this time, the reference plane H1 coincides with a plane including the surface of the flat portion 35.
  • the finned tube heat exchanger 100 satisfies the following formula (1).
  • the position of the flat portion 35 may be different from the position of the front edge 30a and the position of the rear edge 30b.
  • the left side of the equation (1) is expressed as tan ⁇ 1 ⁇ (S1 ⁇ tan ⁇ 1-2 ⁇ ) / (S2 ⁇ D1) ⁇ . If the flat portion 35 is located closer to the ridgeline of the mountain portion 34 than the reference plane H1, the angle formed by the first inclined portion 36 and the second inclined portion 38 is increased, so that the surface area of the fin 31 is reduced. However, pressure loss is reduced. That is, the fin 31 with a low pressure loss is obtained.
  • the left side of the expression (1) is tan ⁇ 1 ⁇ (S1 ⁇ tan ⁇ 1 + 2 ⁇ ) / (S2-D1) ⁇ .
  • the angle formed by the first inclined portion 36 and the second inclined portion 38 is reduced, so that the pressure loss increases, but the fin 31 Increases surface area.
  • produces behind the heat exchanger tube 21 can also be anticipated by the angle (theta) 2 of the 2nd inclination part 38 increasing. That is, the fin 31 with high heat exchange capability is obtained.
  • 2nd inclination part 38 is a curved surface as a whole
  • 2nd inclination angle (theta) 2 can be specified in the cross section shown to FIG. 2C or FIG. 2D.
  • the cross section of FIG. 2C is a cross section observed when the fins 31 are cut along a plane perpendicular to the step direction and passing through the center of the heat transfer tube 21.
  • 2D is a cross section observed when the fins 31 are cut along a plane perpendicular to the flow direction and passing through the center of the heat transfer tube.
  • Equation (1) the technical significance of Equation (1) will be described in detail.
  • the surface area of the corrugated fin is necessarily larger than the surface area of the flat fin (unbent fin).
  • the surface area of the corrugated fin (V-shaped corrugated fin) in which the number of bendings is limited to one is the corrugated fin (M-shaped corrugated fin) having two or more times of bending. It is wider than the surface area. This reason can be understood by comparing the cross section of the fin 31 of this embodiment with the cross section of the conventional fin 10.
  • the length of the cross-sectional contour shown in FIG. 2B is equal to the length of the cross-sectional contour shown in FIG. 9B. Since the cross section shown in FIG. 2C corresponds to the cross section shown in FIG. 9C, the lengths of both contours are equal. On the other hand, as can be understood by comparing FIG. 2D and FIG. 9D, the length of the cross-sectional contour shown in FIG. 2D exceeds the length of the cross-sectional contour shown in FIG. 9D. This is because according to the fin 31 of the present embodiment, the second inclined portion 38 having the second inclination angle ⁇ 2 is included in the cross section shown in FIG. 2D.
  • the inclined portion 8 is not included in the cross section shown in FIG. 9D, and only the flat portion 5 and the valley portion 6 are included. Due to the increase of the surface area based on the second inclined portion 38, the surface area of the fin 31 of the present embodiment exceeds the surface area of the conventional two-folded fin 10.
  • the surface area of the fin increases as the second inclination angle ⁇ 2 increases, regardless of the number of bendings.
  • the increase rate of the surface area of the V-shaped corrugated fin with respect to the second inclination angle ⁇ 2 exceeds that of the M-shaped corrugated fin.
  • the surface area of the V-shaped corrugated fin substantially matches the surface area of the M-shaped corrugated fin. That is, the surface area ratio is about 100%. The larger the second tilt angle ⁇ 2, the greater the difference in surface area.
  • the threshold angle ⁇ 2L corresponding to the point A is an angle at which the second inclined portions 38 adjacent to each other in the step direction come into contact with each other in the V-shaped corrugated fin.
  • the erosion of the adjacent second inclined portions 38 proceeds, so the reduction in the surface area ratio is accelerated.
  • the threshold angle ⁇ 2L is expressed by the following formula (2) using the length S1 of the fin 31, the center-to-center distance S2 of the heat transfer tube 21, the diameter D1 of the flat portion 35, the first inclination angle ⁇ 1, and the distance ⁇ .
  • ⁇ 2L tan -1 ⁇ (S1 ⁇ tan ⁇ 1 ⁇ 2 ⁇ ) / (S2-D1) ⁇ (2)
  • the second inclination angle ⁇ 2 when the second inclination angle ⁇ 2 is less than the threshold angle ⁇ 2L, the adjacent second inclined portions 38 are eroded and the mountain portions 34 disappear, and the contact portions between the second inclined portions 38 are substantially parallel to each other. It becomes. When passing over a horizontal plane at the contact portion, the air is decelerated, causing a decrease in heat transfer coefficient. For this reason, when the second inclination angle ⁇ 2 is less than the threshold angle ⁇ 2L, a decrease in heat exchange capability due to a decrease in heat transfer coefficient is added to a decrease in heat exchange capability due to a rapid decrease in surface area. As a result, the heat exchange capacity of the finned tube heat exchanger is significantly reduced.
  • the second inclination angle ⁇ 2 is equal to or greater than the threshold angle ⁇ 2L.
  • FIG. 5A shows the results obtained by numerical analysis for a V-shaped corrugated fin having only one peak.
  • FIG. 5B shows the results obtained by numerical analysis for an M-shaped corrugated fin having two peaks.
  • a portion having a high heat flux (heat exchange amount) is indicated by a thick line.
  • the heat flux in the front edge 30a and the peak part 34 is very high.
  • the heat flux at the leading edge 9 and the peak 4 is extremely high.
  • the total length of the thick line shown in FIG. 5A exceeds the total length of the thick line shown in FIG. 5B. That is, the V-shaped corrugated fin can ensure a longer region of high heat flux. Therefore, the fin 31 of this embodiment is advantageous to the conventional fin 10 also in terms of heat transfer coefficient.
  • the vortex flow in the separation region not only causes a significant increase in ventilation resistance, but also reduces the effective heat transfer area. That is, if the meander angle ( ⁇ 1 + ⁇ 2) is too large, an increase in heat exchange amount due to an increase in surface area may be offset. Therefore, the meandering angle ( ⁇ 1 + ⁇ 2) is desirably in a range that does not cause a significant increase in ventilation resistance.
  • the first inclination angle ⁇ 1 is not particularly limited, but is preferably less than 40 °.
  • the bending angle of the peak part 34 will be 80 degrees or more. In this case, a thick separation region is generated in the peak portion 34, and there is a possibility that a vortex flow including a vector in the opposite direction to the main flow is generated. Therefore, the first inclination angle ⁇ 1 is preferably less than 40 °.
  • the lower limit of the first inclination angle ⁇ 1 is not particularly limited. In the corrugated fin, the first inclination angle ⁇ 1 is larger than 0 °.
  • FIG. 7 is a graph showing the relationship between the second inclination angle ⁇ 2 and the performance (heat exchange amount and pressure loss) of the finned tube heat exchanger.
  • the rate of change of the heat exchange amount greatly changes with the threshold angle ⁇ 2L as a boundary. That is, when the second inclination angle ⁇ 2 is equal to or greater than the threshold angle ⁇ 2L, a sufficient heat exchange amount can be ensured.
  • the value of ⁇ at the distance (S1 / 2) tan ⁇ 1 + ⁇ from the flat portion 35 to the ridge line of the mountain portion 34 gradually increases.
  • the threshold angle ⁇ 2L increases as the value of ⁇ increases.
  • a new step does not appear due to the fin structure. Accordingly, the value of ⁇ is not limited as long as it is within a range where no significant vortex flow is generated in the separation region ( ⁇ 2 ⁇ 80 ° ⁇ 1 or ⁇ 2 ⁇ 70 ° ⁇ 1).
  • the fin 41 of the present embodiment has the same structure as the fin 31 of the first embodiment, except that the flat portion 35 is not provided around the fin collar 37.
  • Elements common to the fins 41 of the present embodiment and the fins 31 of the first embodiment are assigned the same reference numerals, and descriptions thereof are omitted.
  • the fin 41 has a fin collar 37, a first inclined portion 36, and a second inclined portion 38.
  • the fin collar 37 is a cylindrical portion that is in close contact with the heat transfer tube 21 around the through hole 37h.
  • the second inclined portion 38 is a portion connecting the fin collar 37 and the first inclined portion 36.
  • the position of the lower end of the fin collar 37 coincides with the position of the reference plane H1, and does not vary like the flat portion 35 of the first embodiment.
  • the height of the peak portion 34 is represented by (S1 ⁇ tan ⁇ 1) / 2.
  • the fin 41 does not have the flat portion 35, when the second inclined portions 38 adjacent to each other in the step direction come into contact with each other, the length of the second inclined portion 38 in the step direction is (S2-D2) / 2. It is represented by Furthermore, as estimated from the results of the airflow analysis shown in FIGS. 6A to 6F, the presence or absence of the flat portion 35 is considered not to have a large effect on the increase or decrease in the ventilation resistance.
  • the finned tube heat exchanger 100 including the fins 41 has a low ventilation resistance and a high heat exchange capacity.
  • the second inclination angle ⁇ 2 is preferably less than (70 ° ⁇ 1).
  • the finned tube heat exchanger of the present invention is useful for a heat pump used in an air conditioner, a hot water supply device, a heating device, or the like.
  • it is useful for an evaporator for evaporating a refrigerant.

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  • 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)
PCT/JP2012/006469 2011-10-11 2012-10-10 フィンチューブ熱交換器 WO2013054508A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201280050084.9A CN103890527B (zh) 2011-10-11 2012-10-10 翅片管热交换器
JP2013538435A JP5958771B2 (ja) 2011-10-11 2012-10-10 フィンチューブ熱交換器
EP12840153.6A EP2767791B1 (en) 2011-10-11 2012-10-10 Fin tube heat exchanger

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Application Number Priority Date Filing Date Title
JP2011-223922 2011-10-11
JP2011223922 2011-10-11

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WO2013054508A1 true WO2013054508A1 (ja) 2013-04-18

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EP (1) EP2767791B1 (zh)
JP (1) JP5958771B2 (zh)
CN (1) CN103890527B (zh)
WO (1) WO2013054508A1 (zh)

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JP2016090122A (ja) * 2014-11-04 2016-05-23 パナソニックＩｐマネジメント株式会社 フィンチューブ熱交換器

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EP2767791A1 (en) 2014-08-20

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