WO2013054540A1 - Échangeur de chaleur à tube à ailettes - Google Patents

Échangeur de chaleur à tube à ailettes Download PDF

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Publication number
WO2013054540A1
WO2013054540A1 PCT/JP2012/006562 JP2012006562W WO2013054540A1 WO 2013054540 A1 WO2013054540 A1 WO 2013054540A1 JP 2012006562 W JP2012006562 W JP 2012006562W WO 2013054540 A1 WO2013054540 A1 WO 2013054540A1
Authority
WO
WIPO (PCT)
Prior art keywords
slit
fin
heat exchanger
inclined portion
tube
Prior art date
Application number
PCT/JP2012/006562
Other languages
English (en)
Japanese (ja)
Inventor
健二 名越
岡市　敦雄
雅也 本間
周平 大坪
長谷川　寛
谷口　和宏
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 EP12839875.7A priority Critical patent/EP2767790B1/fr
Priority to JP2013538446A priority patent/JP6052510B2/ja
Priority to CN201280050031.7A priority patent/CN103874901B/zh
Publication of WO2013054540A1 publication Critical patent/WO2013054540A1/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
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/06—Safety or protection arrangements; Arrangements for preventing malfunction by using means for draining heat exchange media from heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
    • F28F2265/22—Safety or protection arrangements; Arrangements for preventing malfunction for draining

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.
  • FIG. 15 is a plan view of fins used in a conventional fin tube heat exchanger.
  • the fin 1 is formed so that the peaks 4 and 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.
  • Patent Document 1 describes a fin having a drainage slit.
  • the fin described in Patent Document 1 is shown in FIG.
  • the fin 11 is provided with a drainage slit 8 extending obliquely downward from a drain retention area below the heat transfer tube 7.
  • Patent Document 1 assumes an unbent fin (so-called flat fin), and its application range is not necessarily wide. Therefore, a technique that can be applied to corrugated fins is desired.
  • the present invention aims to improve the drainage performance of a finned tube heat exchanger using corrugated fins.
  • a heat transfer tube that passes through the plurality of fins and is configured such that a medium that exchanges heat with the air flows therein;
  • the fin is a corrugated fin formed so that a peak portion appears at at least one position in the airflow direction, and a tube peripheral portion formed around the heat transfer tube and the peak portion so as to form the peak portion.
  • a first inclined portion that is inclined with respect to the airflow direction, a second inclined portion that connects the pipe peripheral portion and the first inclined portion to each other, and a slit formed in the second inclined portion,
  • a finned tube heat exchanger is provided.
  • the slit is formed in the second inclined portion. Water is guided from the front side of the fin to the back side of the fin through the slit, and is collected in the valley on the back side of the fin. The water collected in the valley flows downward along the valley. As a result, water is efficiently removed from the surface of the fin.
  • the top view of the fin used for the fin tube heat exchanger of FIG. Sectional drawing along the IIB-IIB line of the fin shown in FIG. 2A Sectional drawing along the IIC-IIC line of the fin shown in FIG. 2A Sectional view along the IID-IID line of the fin shown in Fig. 2A
  • the top view of the fin which concerns on the modification 1 The top view of the fin concerning modification 2 Sectional drawing along the IVB-IVB line of the fin shown in FIG.
  • Action explanatory drawing of the fin which omitted the slit from the fin of modification 3 Action explanatory drawing of the fin of modification 3
  • the top view of the fin concerning a 2nd embodiment 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 Sectional drawing along the XD-XD line of the fin shown in FIG. 10A
  • the top view of the fin concerning modification 4 The partial top view of the fin which concerns on the modification 5
  • the top view of the fin concerning modification 6 Sectional drawing along the XIIIB-XIIIB line of the fin shown in FIG. 13A Sectional drawing along the XIIIC-XIIIC line of the fin shown in FIG.
  • FIG. 13A Sectional drawing along the XIIID-XIIID line of the fin shown in FIG. 13A The top view of the fin concerning modification 7 Sectional drawing along the XIVB-XIVB line of the fin shown in FIG. 14A Sectional drawing along the XIVC-XIVC line of the fin shown to FIG. 14A Sectional drawing along the XIVD-XIVD line of the fin shown to FIG. 14A Plan view of conventional corrugated fin Plan view of fin described in Patent Document 1
  • the first aspect of the present disclosure is: A plurality of fins arranged in parallel to form an air flow path; A heat transfer tube that passes through the plurality of fins and is configured such that a medium that exchanges heat with the air flows therein;
  • the fin is a corrugated fin formed so that a peak portion appears at at least one position in the airflow direction, and a tube peripheral portion formed around the heat transfer tube and the peak portion so as to form the peak portion.
  • a first inclined portion that is inclined with respect to the airflow direction, a second inclined portion that connects the pipe peripheral portion and the first inclined portion to each other, and a slit formed in the second inclined portion,
  • a finned tube heat exchanger is provided.
  • the water adhering to the fin surface usually flows downward due to its own weight. However, some of the attached water may stay on the surface of the fin. Water retention is likely to occur in corrugated fins. Examples of the portion where the water tends to stay in the corrugated fin include a pipe peripheral portion and a second inclined portion. The water that cannot get over the peak portion is retained and stabilized in the tube peripheral portion and the second inclined portion in a manner that makes the surface area as small as possible.
  • a slit is formed in the second inclined portion.
  • the slit guides water from the pipe peripheral part and the second inclined part to the mountain part.
  • water is guided from the front side of the fin to the back side of the fin through the slit. That is, water is collected in the valleys behind the fins.
  • the water collected in the valley flows downward along the valley. As a result, water is efficiently removed from the surface of the fin.
  • the longitudinal direction of the slit is inclined with respect to the airflow direction or is perpendicular to the airflow direction, and the slit is formed on the periphery of the tube.
  • a finned tube heat exchanger extending from the side toward the peak side is provided. According to such a slit, water can be efficiently guided from the pipe peripheral part and the second inclined part to the mountain part.
  • the slit in addition to the first or second aspect, has a center line parallel to the longitudinal direction of the slit, and the center of the heat transfer tube is positioned on an extension line of the center line.
  • a finned tube heat exchanger is provided.
  • the slit has a width capable of guiding water from the front side of the fin to the back side of the fin by capillary action.
  • a finned tube heat exchanger is provided. According to such a structure, water is efficiently excluded from the surface of the fin.
  • the fifth aspect of the present disclosure provides a finned tube heat exchanger in addition to any one of the first to fourth aspects, wherein the width of the slit is in the range of 0.01 to 1 mm.
  • the width of the slit is adjusted in such a range, water is smoothly guided from the front side of the fin to the back side of the fin.
  • the sixth aspect of the present disclosure provides a finned tube heat exchanger, in addition to any one of the first to fifth aspects, in which an end of the slit is in contact with the pipe peripheral part or the peak part. Since the slit extends from the flat portion side to the peak portion side, an effect of guiding water to the peak portion is exhibited.
  • a finned tube heat exchanger in addition to any one of the first to fifth aspects, is provided in which both end portions of the slit are in contact with the tube peripheral portion and the peak portion, respectively. According to such a configuration, water is efficiently collected from the flat portion and the second inclined portion to the mountain portion.
  • the fin is a V-shaped corrugated fin formed so that the peak portion appears only at one position in the airflow direction.
  • a finned tube heat exchanger is provided. According to such a configuration, all the water guided from the front side to the back side of the fin through the slit is collected in one valley. As more water is collected in one valley, the collected water flows easily down.
  • the slit has a center line parallel to the longitudinal direction of the slit, and when the fin is viewed in plan, the ridge line of the peak portion, the heat transfer tube
  • the fin tube heat exchanger is provided in which the center of the slit and the center line of the slit are on the same straight line perpendicular to the airflow direction. According to such a positional relationship, since almost no water remains in the flat portion and the second inclined portion, a dramatic improvement in drainage performance can be expected.
  • the fin is an M-shaped corrugated fin in which the ridges are formed at a plurality of positions along the airflow direction.
  • a finned tube heat exchanger in which a plurality of the slits are formed in the second inclined portion in a shape corresponding to each of the peak portions. According to such a configuration, an excellent drainage effect can be obtained.
  • the inclined portion when the direction perpendicular to both the airflow direction and the arrangement direction of the plurality of fins is defined as a step direction,
  • the inclined portion includes an upper region and a lower region with a plane perpendicular to the step direction and passing through the center of the heat transfer tube as a boundary, and the slit is formed in each of the upper region and the lower region.
  • a finned tube heat exchanger Provided is a finned tube heat exchanger. According to such a structure, the drainage effect by a slit can fully be acquired.
  • the second inclined portion on one side of the slit when the cross section perpendicular to the longitudinal direction of the slit is observed, the second inclined portion on one side of the slit and the Provided is a finned tube heat exchanger in which the slit is formed by providing a step with the second inclined portion on the other side of the slit. According to the slit having such a shape, an effect of improving the drainage performance of the fin can be obtained.
  • a finned tube heat exchanger in which the slit is formed by deforming the second inclined portion into an arcuate shape. According to the slit having such a shape, an effect of improving the drainage performance of the fin can be obtained.
  • the tube peripheral portion is a flat portion formed around a cylindrical fin collar that is in close contact with the heat transfer tube.
  • a finned tube heat exchanger which is a cylindrical fin collar which is in close contact with the heat transfer tube.
  • 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 air flow direction is perpendicular to the longitudinal direction of the fins 31 and is parallel to the horizontal direction in the actual use state of the fin tube heat exchanger 100.
  • 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 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 fins 31 are formed such that peaks 34 and valleys 36 appear alternately in the airflow direction.
  • the peak portion 34 and the valley portion 36 are located between the adjacent heat transfer tubes 21.
  • the ridge line of the mountain part 34 and the valley line of the valley part 36 are each parallel to the step direction. That is, the fin 31 is a fin called a corrugated fin. If a portion protruding in the same direction as the protruding direction of the fin collar 37 is defined as a “mountain portion 34”, in the present embodiment, the fin 31 has two peak portions 34 and one valley portion 36 in the airflow direction. .
  • the position of the valley portion 36 coincides with the position of the center of the heat transfer tube 21.
  • the positional relationship between the valley portion 36 and the heat transfer tube 21 and the positional relationship between the peak portion 34 and the heat transfer tube 21 are not particularly limited.
  • the number of peaks 34 and the number of valleys 36 are not particularly limited.
  • the fin 31 further includes a flat portion 35, a first inclined portion 38, and a second inclined portion 39 (peripheral inclined portion).
  • the flat portion 35 is a portion adjacent to the fin collar 37 and is a tube peripheral portion formed around the through hole 37h.
  • the flat portion 35 is formed between the through hole 37h and the second inclined portion 39, and has an annular shape in plan view.
  • the surface of the flat part 35 is parallel to the airflow direction and perpendicular to the height direction. However, the flat part 35 may be slightly inclined with respect to the airflow direction.
  • the 1st inclination part 38 is a part inclined with respect to the airflow direction so that the peak part 34 and the trough part 36 may be formed.
  • the first inclined portion 38 occupies the widest area in the fin 31.
  • the surface of the first inclined portion 38 is flat.
  • the second inclined portion 39 is a portion that smoothly connects the flat portion 35 and the first inclined portion 38 so as to eliminate the difference in height between the flat portion 35 and the first inclined portion 38. .
  • the surface of the second inclined portion 39 is a gentle curved surface. That is, the second inclined portion 39 is an inclined portion that protrudes from the through hole 37 h toward the peak portion 34.
  • the flat portion 35 and the second inclined portion 39 form a concave portion around the fin collar 37 and the through hole 37h.
  • the second inclined portion 39 seems to be divided into two at the position of the valley portion 36, but one annular second inclined portion 39 is formed around one flat portion 35. It is assumed that
  • An appropriate radius (for example, R0.5 mm to R2.0 mm) may be applied to the boundary portion between the first inclined portion 38 and the second inclined portion 39.
  • an appropriate radius (for example, R0.5 mm to R2.0 mm) may be given to the boundary portion between the peak portion 34 and the second inclined portion 39.
  • the fin 31 further has a slit 23 formed in the second inclined portion 39.
  • the slit 23 penetrates the fin 31 and extends from the through hole 37h side to the peak portion 34 side. Specifically, the slit 23 extends from the flat portion 35 side toward the peak portion 34 side.
  • the slit 23 has a longitudinal direction that is inclined or perpendicular to the airflow direction.
  • the edge 45 of the ridge line of the peak portion 34 is on the extension line of the slit 23.
  • the slit 23 is formed on an imaginary line extending from the center of the through hole 37h (the center 25 of the heat transfer tube 21) toward the end 45 of the ridge line of the mountain portion 34.
  • water can be guided from the flat portion 35 and the second inclined portion 39 to the mountain portion 34.
  • water is guided from the front side of the fin 31 to the back side of the fin 31 through the slit 23. That is, the water is collected in the valley on the back side of the fin 31.
  • the water collected in the valley flows downward along the valley. As a result, water is efficiently removed from the surface of the fin 31.
  • the slit 23 is formed so as to be positioned in at least the lower half region of the second inclined portion 39.
  • the second inclined portion 39 includes an upper region 39a and a lower region 39b with a plane H perpendicular to the step direction and passing through the center 25 of the heat transfer tube 21 as a boundary.
  • the slits 23 are formed in each of the upper region 39a and the lower region 39b. Thereby, the drainage effect by the slit 23 can be sufficiently obtained. Since the fins 31 have a vertically symmetrical structure, the fin tube heat exchanger 100 can be easily assembled.
  • the slit 23 may be formed in at least one selected from the upper region 39a and the lower region 39b. As shown in FIG. 3, in the fin 31B according to the first modification, the slit 23 is formed in the lower region 39b. Specifically, the slit 23 is formed only in the lower region 39b. Also with this configuration, the drainage effect by the slit 23 can be sufficiently obtained.
  • the “actual use state of the fin tube heat exchanger 100” means a state in which the fin tube heat exchanger 100 is installed so that the longitudinal direction of the fins 31 is substantially parallel to the vertical direction. If the finned tube heat exchanger 100 is used in such an installation state, water hardly collects on the surface of the fins 31.
  • the fin 31 is an M-shaped corrugated fin in which peaks 34 are formed at a plurality of positions in the airflow direction.
  • a plurality of slits 23 are formed in the second inclined portion 39 so as to correspond to each of the peak portions 34.
  • a plurality of slits 23 are formed in the second inclined portion 39 so as to guide water to each of the two peak portions 34. Yes.
  • four slits 23 are formed around one flat portion 35. That is, four slits 23 are formed in the second inclined portion 39. According to such a configuration, an excellent drainage effect can be obtained.
  • two slits 23 may be formed in the second inclined portion 39 as in the fin 31B shown in FIG. Even with such a configuration, a sufficient drainage effect can be obtained.
  • At least one slit 23 is formed around all the flat portions 35. Thereby, the drainage effect by the slits 23 is obtained around all the flat portions 35.
  • the slit 23 may be formed only around one periphery selected from two adjacent flat portions 35. In this case, a certain drainage effect can be obtained.
  • the longitudinal direction of the slit 23 is substantially along the direction of gravity. Thereby, not only can the water on the flat portion 35 and the second inclined portion 39 be promptly guided to the mountain portion 34, but the water on the flat portion 35 and the second inclined portion 39 can be supplied from the front side of the fin 31. It can be quickly guided to the back side.
  • the longitudinal direction of the slit 23 can be determined so that an angle formed by a straight line parallel to the longitudinal direction of the slit 23 and a straight line parallel to the longitudinal direction of the fin 31 is 45 degrees or less.
  • the slit 23 has a center line CL parallel to the longitudinal direction.
  • the center 25 of the heat transfer tube 21 (the center of the through hole 37h) is located on the extended line of the center line CL. If the slit 23 extends in such a direction, the slit 23 is unlikely to hinder heat conduction in the fin 31. The reason is as follows.
  • the temperature distribution of the fins 31 in the vicinity of the heat transfer tube 21 usually spreads substantially concentrically around the heat transfer tube 21.
  • the center 25 of the heat transfer tube 21 is positioned on the extended line of the center line CL of the slit 23, the temperature of the fin 31 on the left side of the center line CL substantially matches the temperature of the fin 31 on the right side of the center line CL. Even if the slit 23 is not provided, the heat hardly moves in the direction crossing the slit 23. Therefore, according to this embodiment, the heat transfer performance of the fin 31 is maintained.
  • the longitudinal direction of the slit 23 is not particularly limited as long as drainage performance can be improved. 4A and 4B, in the fin 31C according to the modification 2, the longitudinal direction of the slit 23 is parallel to the vertical direction (longitudinal direction of the fin 31C). In other words, the longitudinal direction of the slit 23 is perpendicular to the airflow direction. A slit 23 is formed on the extended line EL of the ridge line of the mountain portion 34.
  • both end portions of the slit 23 are in contact with the flat portion 35 and the mountain portion 34, respectively. According to such a configuration, water is efficiently collected from the flat portion 35 and the second inclined portion 39 to the mountain portion 34.
  • the position of the end portion of the slit 23 is not particularly limited as long as a certain water collecting action is exhibited.
  • both end portions of the slit 23 may be separated from the flat portion 35 and the mountain portion 34.
  • the slit 23 may have one end in contact with the flat portion 35 and the other end away from the peak portion 34.
  • the slit 23 has one end portion away from the flat portion 35 and the other end portion in contact with the peak portion 34 (specifically, the end portion 45 of the ridge line of the peak portion 34). You may do it.
  • the other end of the slit 23 may be located on a ridge line between the first inclined portion 38 and the second inclined portion 39.
  • the edge 45 of the ridge line of the peak portion 34 may be located at a position different from the extension line of the slit 23. Further, the ridge line of the mountain portion 34 may be separated from the extension line of the slit 23. Also in these cases, the slit 23 extends from the flat portion 35 side to the peak portion 34 side. In other words, in FIGS. 5A to 5D, the slit 23 is formed on an imaginary line extending from the center of the through hole 37h (the center 25 of the heat transfer tube 21) toward the peak portion 34 side. Therefore, the effect
  • the slit 23 is formed on a virtual line extending from the center of the through hole 37h toward the edge 45 of the ridge line of the mountain portion 34.
  • the slit 23 may be formed on an imaginary line extending from the position shifted from the center of the through hole 37h toward the peak portion 34.
  • the slit 23 may be formed on an imaginary line extending from the position shifted from the center of the through-hole 37 h toward the end portion 45 of the ridge line of the mountain portion 34. It is desirable that the slit 23 is formed in the second inclined portion 39 so as to extend toward the end portion 45 of the ridge line of the mountain portion 34.
  • the width of the slit 23 is not particularly limited.
  • the slit 23 preferably has a width G that can guide water from the front side of the fin 31 to the back side of the fin 31 by capillary action. According to such a configuration, water is efficiently removed from the surface of the fin 31.
  • the width G of the slit 23 can be adjusted to a range of 0.01 to 1 mm (preferably 0.05 to 0.3 mm), for example.
  • the width G of the slit can be adjusted to satisfy the relationship of 0.005FP ⁇ G ⁇ FP (desirably, 0.025FP ⁇ G ⁇ 0.3FP).
  • the width G is adjusted to such a range, water is smoothly guided from the front side of the fin 31 to the back side of the fin 31.
  • “Fin pitch FP” means an interval between adjacent fins.
  • the cross-sectional shape of the slit 23 is not particularly limited. Specific examples of the cross-sectional shape of the slit 23 are shown in FIGS. 6A and 6B.
  • the example shown in FIG. 6A can be formed by applying a shear load to the fins 31 along the thickness direction. That is, when a cross section perpendicular to the longitudinal direction of the slit 23 is observed, the gap between the second inclined portion 39 on one side (left side) of the slit 23 and the second inclined portion 39 on the other side (right side) of the slit 23.
  • a slit 23 is formed by providing a step to the surface. The slit 23 shown in FIG.
  • the 6B can be formed by piercing a fin 31 from one surface of the fin 31 with a sharp blade (for example, one incorporated in a mold). That is, when a cross section perpendicular to the longitudinal direction of the slit 23 is observed, the second inclined portion 39 is deformed into an arcuate shape on each of one side (left side) and the other side (right side) of the slit 23, thereby causing the slit 23. May be formed. With any shape of the slit 23, the effect of improving the drainage performance of the fin 31 can be obtained.
  • the processing direction when forming the slit 23 is not particularly limited.
  • 7A and 7B represent the fin surface states in time series.
  • water W adheres to the surface of the fin 1 around the heat transfer tube 2 (left figure).
  • the water W flows downward (in the direction of gravity) along the folds of the fin 1 and starts to stay in the flat portion 5 and the inclined portion 9.
  • a part of the water W overflows along the valley 6 and flows downward (center view).
  • the remaining portion of the water W is left in the flat portion 5 and the inclined portion 9 due to the surface tension, and stays around the heat transfer tube 2 without flowing downward (right diagram).
  • the water W hinders the air flow and has a large thermal resistance, so that the performance of the heat exchanger is greatly reduced.
  • the fin 31 of this embodiment has the following operations and effects.
  • the water W adheres to the surface of the fin 31 around the heat transfer tube 21 (left figure).
  • the water W flows downward along the folds of the fins 31 and starts to stay in the flat portion 35 and the second inclined portion 39.
  • a part of the water W overflows along the valley 36 and flows downward.
  • the remaining portion of the water W penetrates from the front side of the fin 31 to the back side of the fin 31 through the slit 23 due to the influence of surface tension (capillary phenomenon) and gravity.
  • the mountain portion 34 constitutes a valley portion
  • the valley portion 36 constitutes a mountain portion. Therefore, the valley is waiting for the water W to reach through the slit 23.
  • frost when the outside air temperature approaches 0 ° C., frost starts to accumulate on the fin surface of the fin tube heat exchanger incorporated in the outdoor unit. Since frost greatly impairs the performance of the finned tube heat exchanger, it is necessary to periodically perform an operation for melting and removing the frost, so-called defrost operation.
  • defrost operation water generated by melting frost cannot be sufficiently removed from the surface of the fin 1. Therefore, a part of the water generated by melting frost remains on the surface of the fin 1 as it is, and is re-frozen after the defrost operation is completed. That is, useless energy is consumed for melting frost and freezing residual water.
  • frost or ice
  • the fin tube heat exchanger 100 of the present embodiment has excellent drainage performance. Excluded from the surface. As a result, it is possible to avoid disadvantages such as wasteful energy consumption and shortening of the defrost operation interval. After the defrosting operation, water is sufficiently removed from the surface of the fins 31, so that the original performance of the finned tube heat exchanger 100 is reliably exhibited.
  • the position of the flat portion 35 coincides with the position of the valley portion 36 in the height direction (Y direction). According to such a configuration, as described with reference to FIG. 7A, even if the slit 23 does not exist, the water W is transferred from the flat portion 5 and the second inclined portion 9 to the valley portion 6 to some extent. I can move. However, this configuration is not essential.
  • the position of the flat portion 35 is different from the position of the valley portion 36, and the front edge 30a and the rear edge 30b. Match the position of.
  • a valley portion 36 is located between the flat portion 35 and the peak portion 34, and a step is generated between the valley portion 36 and the flat portion 35.
  • the step between the valley portion 36 and the flat portion 35 is filled with an annular second inclined portion 39 formed around the flat portion 35.
  • the slit 23 is formed at the following position. That is, a plane that passes through the center 25 of the heat transfer tube 21 (the center of the through hole 37h) and is perpendicular to the airflow direction is defined as a first central plane P1.
  • the slit 23 is formed in the second inclined portion 39 so as to overlap the first central plane P1. Specifically, the slit 23 overlaps the first central plane P1 and extends in the step direction. That is, the longitudinal direction of the slit 23 is parallel to the valley line of the valley portion 36. Further, the slit 23 extends from the through hole 37h side toward the trough 36 side. Specifically, the slit 23 extends from the flat portion 35 side toward the valley portion 34 side.
  • the slits 23 may be formed in both the upper region 39a and the lower region 39b, or only one selected from the upper region 39a and the lower region 39b. May be formed. That is, as shown in FIG. 8A, two slits 23 may be formed in the second inclined portion 39, and as shown in FIG. 8C, one slit 23 is formed in the second inclined portion 39. Also good. In the latter case, the slit 23 is typically formed only in the lower region 39b.
  • the water W penetrates from the front side to the back side of the fin 31D through the slit 23, spreads from the peak portion to the valley portion, and then along the valley portion. And flows downward (left and center views). Therefore, the water W is sufficiently removed from the surface of the fin 31D (right figure).
  • the fin 31D exhibits the same action as the action of the fin 31 described with reference to FIG. 7B.
  • the fin 31F according to the second embodiment is a V-shaped corrugated fin formed such that the peak portion 34 appears only at one position in the airflow direction.
  • the fin 31 ⁇ / b> F of the present embodiment has a flat portion 35, a first inclined portion 38, a second inclined portion 39, and a slit 23, similarly to the fin 31 of the first embodiment.
  • the slit 23 is formed in the second inclined portion 39 and extends from the through hole 37 h side toward the peak portion 34 side. Specifically, the slit 23 extends from the flat portion 35 side toward the peak portion 34 side.
  • the components of the fin 31F of the present embodiment are those of the fin 31 of the first embodiment, as indicated by the same reference numerals, except that the crest 34 is formed only at one position in the airflow direction. Is the same. Therefore, as long as there is no technical contradiction, all the descriptions related to the first embodiment and its modifications can be applied to the fin 31F of this embodiment and its modifications.
  • the drainage performance is improved by the slit 23 in the same manner as the fin 31 of the first embodiment.
  • the longitudinal direction of the slit 23 is perpendicular to the airflow direction.
  • the slit 23 has a center line CL parallel to the longitudinal direction of the slit 23. Since the longitudinal direction of the slit 23 is parallel to the gravity direction and the step direction, the center line CL is also parallel to the gravity direction and the step direction.
  • the fin 31F is viewed in plan, the ridgeline of the mountain portion 34, the center 25 of the heat transfer tube 21, and the centerline CL of the slit 23 are present on the same straight line perpendicular to the airflow direction.
  • One end (upper end) of the slit 23 is located at or near the lower end of the annular flat portion 35. According to such a positional relationship, since almost no water remains in the flat portion 35 and the second inclined portion 39, a dramatic improvement in drainage performance can be expected.
  • the slit 23 is formed on an imaginary line extending from the center of the through hole 37h (the center 25 of the heat transfer tube 21) toward the mountain portion 34 side. Further, the edge 45 of the ridge line of the peak portion 34 is on the extension line of the slit 23. Therefore, the same effects as those described in the first embodiment can be obtained in this embodiment.
  • the fin 31F of the present embodiment is a V-shaped corrugated fin. Therefore, all of the water guided from the front side to the back side of the fin 31F through the slit 23 is collected in one valley. That is, as compared with the M-shaped corrugated fin (first embodiment), more water is collected in one valley, and thus the collected water easily flows downward.
  • the drainage performance of the fin 31F of this embodiment is equivalent to or exceeds the drainage performance of the fin 31 (M-shaped corrugated fin) of the first embodiment. If the length in the airflow direction is constant, the surface area of the V-shaped corrugated fin exceeds the surface area of the M-shaped corrugated fin. Therefore, the heat exchange performance of the V-shaped corrugated fin is equal to or higher than the heat exchange performance of the M-shaped corrugated fin.
  • the slits 23 are formed in the upper region 39a of the second inclined portion 39 and the lower region 39b of the second inclined portion 39, respectively. That is, two slits 23 are formed in the second inclined portion 39.
  • the slit 23 may be formed in at least one selected from the upper region 39a and the lower region 39b. As shown in FIG. 11, in the fin 31G according to the modified example 4, the slit 23 is formed in the lower region 39b. Specifically, the slit 23 is formed only in the lower region 39b.
  • the configuration of the slit 23 is not particularly limited as long as the drainage effect is exhibited.
  • the slits 23 may be inclined with respect to both the airflow direction and the step direction.
  • the positions of both ends of the slit 23 are not particularly limited.
  • a plurality of slits 23 are formed in the fin 31 ⁇ / b> H according to the modified example 5 so as to extend toward one peak portion 34.
  • the fin 31I according to the modified example 6 does not have the flat portion 35.
  • the second inclined portion 39 (peripheral inclined portion) is adjacent to the fin collar 37 and gently protrudes from the through hole 37 h side toward the mountain portion 34. Except for not having the flat portion 35, the structure of the fin 31I is the same as the fin 31 of the first embodiment. 14A to 14D, the fin 31J according to the modified example 7 also does not have the flat portion 35. Except for not having the flat portion 35, the structure of the fin 31J is the same as the fin 31F of the second embodiment. Thus, the flat part 35 is not essential and may be omitted.
  • the cylindrical fin collar 37 formed so as to extend in the height direction may be a tube peripheral portion formed around the heat transfer tube 21.
  • the slit 23 is formed only in the lower region 39b of the second inclined portion 39.
  • one slit 23 or a plurality of slits 23 are formed in the region 39a on the upper side of the second inclined portion 39 so that the fins shown in FIGS. 4A, 5A to 5D, and 12 each have a vertically symmetrical structure. It may be.
  • the finned tube heat exchanger disclosed in the present specification 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)

Abstract

La présente invention concerne un échangeur de chaleur à tube à ailettes (100) pourvu : d'une pluralité d'ailettes (31) disposées en parallèle ; et d'un tube de transfert de chaleur (21) configuré de telle sorte qu'un milieu qui échange la chaleur avec l'air circule à l'intérieur de ce dernier. Les ailettes (31) sont des ailettes ondulées formées de telle sorte qu'une section colline (34) apparaît dans au moins une position dans le sens de l'écoulement d'air, et comprennent : une section périphérie de tube (35 ou 37) formée à la périphérie du tube de transfert de chaleur (21) ; une première section inclinée (38) inclinée par rapport au sens de l'écoulement d'air de façon à former la section colline (34) ; une seconde section inclinée (39) raccordant la section périphérie de tube (35) et la première section inclinée (38) l'une à l'autre ; et une fente (23) formée dans la seconde section inclinée (39).
PCT/JP2012/006562 2011-10-14 2012-10-12 Échangeur de chaleur à tube à ailettes WO2013054540A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP12839875.7A EP2767790B1 (fr) 2011-10-14 2012-10-12 Échangeur de chaleur à tube à ailettes
JP2013538446A JP6052510B2 (ja) 2011-10-14 2012-10-12 フィンチューブ熱交換器
CN201280050031.7A CN103874901B (zh) 2011-10-14 2012-10-12 翅片管热交换器

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JP2011-227334 2011-10-14
JP2011227334 2011-10-14

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WO2013054540A1 true WO2013054540A1 (fr) 2013-04-18

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EP2985558B1 (fr) * 2013-04-12 2017-03-01 Panasonic Intellectual Property Management Co., Ltd. Échangeur de chaleur à ailettes et à tubes et dispositif à cycle frigorifique
CN103837014B (zh) * 2014-03-21 2016-08-31 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其连接方法
CN103940284B (zh) * 2014-03-21 2016-09-14 丹佛斯微通道换热器（嘉兴）有限公司 换热器及其连接方法
DE102014107408B4 (de) 2014-05-26 2022-07-14 Kelvion Machine Cooling Systems Gmbh Wärmetauscher
CN104101244B (zh) * 2014-08-01 2016-06-08 兰州交通大学 椭圆管管翅式换热器流线型变波幅波纹翅片
CN104110992B (zh) * 2014-08-01 2016-06-08 兰州交通大学 椭圆管管翅式换热器流线型变波幅圆弧形波纹翅片
JP6337742B2 (ja) * 2014-11-04 2018-06-06 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
CN106403689A (zh) * 2016-11-30 2017-02-15 海信科龙电器股份有限公司 一种波纹翅片及空调换热器
US11573056B2 (en) * 2018-07-11 2023-02-07 Mitsubishi Electric Corporation Heat exchanger, heat exchanger unit, and refrigeration cycle apparatus
TWI801732B (zh) * 2020-04-13 2023-05-11 國立成功大學 換熱模組及換熱方法
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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JPS5761375U (fr) * 1980-09-19 1982-04-12
JPS57104185U (fr) * 1980-12-15 1982-06-26
JPS6422186U (fr) 1987-07-28 1989-02-03
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JP2008111646A (ja) * 2006-10-02 2008-05-15 Daikin Ind Ltd フィンチューブ型熱交換器
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EP2767790A4 (fr) 2015-05-27
EP2767790A1 (fr) 2014-08-20
CN103874901B (zh) 2015-12-23
JP6052510B2 (ja) 2016-12-27
JPWO2013054540A1 (ja) 2015-03-30
CN202853449U (zh) 2013-04-03
CN103874901A (zh) 2014-06-18
EP2767790B1 (fr) 2019-12-11

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