WO2013161193A1 - フィンチューブ熱交換器及びそれを備えた冷凍サイクル装置 - Google Patents

フィンチューブ熱交換器及びそれを備えた冷凍サイクル装置 Download PDF

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Publication number
WO2013161193A1
WO2013161193A1 PCT/JP2013/002312 JP2013002312W WO2013161193A1 WO 2013161193 A1 WO2013161193 A1 WO 2013161193A1 JP 2013002312 W JP2013002312 W JP 2013002312W WO 2013161193 A1 WO2013161193 A1 WO 2013161193A1
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WIPO (PCT)
Prior art keywords
fin
cut
heat transfer
air flow
heat exchanger
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Application number
PCT/JP2013/002312
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English (en)
French (fr)
Japanese (ja)
Inventor
由樹 山岡
治 青柳
安藤　智朗
一貴 小石原
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 EP13781555.1A priority Critical patent/EP2843345B1/en
Priority to CN201380022277.8A priority patent/CN104272053B/zh
Priority to JP2014512319A priority patent/JP6021081B2/ja
Publication of WO2013161193A1 publication Critical patent/WO2013161193A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—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
    • 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 particularly relates to a finned tube heat exchanger used for heat exchange of a refrigerant.
  • this kind of fin tube heat exchanger as shown in FIG. 17, it comprises a plurality of fins 1 arranged at a predetermined interval Fp and a heat transfer tube 2 inserted substantially at right angles to these fins 1 It is done.
  • FIG. 18 (a) is a cross-sectional view when the fins constituting the conventional fin tube heat exchanger are stacked
  • FIG. 18 (b) is a partial plan view of the fins constituting the conventional fin tube heat exchanger.
  • a fin collar 3 raised from the surface of the fin 1 is formed on the fin 1, and the heat transfer tube 2 is inserted into the fin collar 3.
  • the fin collar 3 has the end surface 30 in contact with the adjacent fins 1 and plays a role of holding the distance between the fins 1 at a predetermined distance.
  • An air flow 100 (for example, air) is introduced into the finned tube heat exchanger by a blower (not shown) or the like.
  • the air flow 100 exchanges heat with a fluid (for example, R410a, a refrigerant such as carbon dioxide) flowing through the inside of the heat transfer tube 2 through the fins 1 while flowing through the gaps between the stacked fins 1.
  • a fluid for example, R410a, a refrigerant such as carbon dioxide
  • the fluid flowing through the inside of the heat transfer tube 2 is generally in a two-phase state of a liquid phase and a gas phase.
  • the fluid exchanges heat with the air flow 100 to evaporate the liquid phase, and becomes superheated gas and flows out of the finned-tube heat exchanger.
  • FIG. 19 (a) is a cross-sectional view when the fins constituting the finned tube heat exchanger described in Patent Document 1 are stacked, and FIG. 19 (b) configures the finned tube heat exchanger described in Patent Document 1. It is a partial top view of a fin.
  • the cut-and-raised part 4 shown in FIG. 19 is a louver shape in which a part of the fin 1 is bent in a substantially vertical direction with respect to the fin flat portion 1 c.
  • the cut-and-raised portions 4 are formed on the fins 1 so as to be aligned in a straight line from the upstream side to the downstream side of the air flow 100, and the dead water area generated in the wake of the heat transfer tube 2 is reduced.
  • FIG. 20 (a) is a cross-sectional view when the fins constituting the fin-tube heat exchanger described in Patent Document 2 are stacked, and FIG. 20 (b) configures the fin-tube heat exchanger described in Patent Document 2. It is a partial top view of the fin to be
  • the cut-and-raised 4 shown in FIG. 20 is offset so that the plane of the cut-and-raised 4 is substantially parallel to the fin flat portion 1c, and both ends of the cut and raised 4 are connected with the fin flat portion 1c to form a slit. ing.
  • the cut and raised portions 4 are formed on both the upstream side and the downstream side of the air flow 100 with respect to the heat transfer tube 2.
  • the height of the cut-and-raise 4 is set to a predetermined range.
  • the finned-tube heat exchanger described in Patent Document 2 is intended to suppress a significant decrease in transmission performance that occurs at the time of frost formation by providing the cut-and-raise 4 shown in FIG.
  • FIG.21 (a) is sectional drawing at the time of laminating
  • FIG.21 (b) is a fin which comprises the finned-tube heat exchanger of patent document 3.
  • FIG.21 (b) is a fin which comprises the finned-tube heat exchanger of patent document 3.
  • the cut-and-raised part 4 shown in FIG. 21 has a louver shape in which a part of the fin 1 is bent in a direction substantially perpendicular to the fin flat portion 1 c.
  • the cut-and-raised portion 4 formed by bending the fin 1 is cut and raised toward the adjacent fin 1 to form an opening 4 c.
  • the cut-and-raised portions 4 are disposed on the fins 1 so as to be inclined with respect to the flow direction of the air flow 100, and are disposed so as to intersect with each other when viewed from the direction perpendicular to the fin flat portion 1c. As a result, the collision of the air flow 100 generated by passing through the opening 4 c promotes the turbulent flow and promotes the heat transfer of the finned-tube heat exchanger.
  • the water which precipitates with the fin 1 has the subject that it does not flow down smoothly by cutting and rising and staying in 4, and heat transfer performance will fall.
  • An object of the present invention is to solve the conventional problems, and it is an object of the present invention to provide a finned-tube heat exchanger excellent in heat transfer performance, which reduces frost formation on fins and improves drainage performance.
  • the finned tube heat exchanger of the present invention has a cut and raised portion, and a plurality of fins through which an air flow passes and a plurality of the fins are passed and fluid flows inside. And a plurality of heat transfer tubes, wherein the cut-and-raised portion is disposed only on the downstream side of the air flow with respect to the center of the heat transfer tubes closest to the heat transfer tube, and is formed inclined with respect to the air flow.
  • frost formation can be reduced by providing a cut-off only on the downstream side of the air flow which is hard to frost-form. Moreover, since the water on a fin is smoothly made to flow down by the cutting and raising which inclined with respect to the airflow direction, drainage property can be improved.
  • FIG. 8 A partial plan view of another fin of the finned-tube heat exchanger.
  • the partial top view of the fin of the finned-tube heat exchanger in Embodiment 8 of this invention Configuration of conventional finned tube heat exchanger (A) A cross-sectional view of the conventional fin tube heat exchanger when the fins are stacked, (b) a partial plan view of the fin of the fin tube heat exchanger (A) A cross-sectional view of another fin of the conventional fin-tube heat exchanger when stacked, (b) a partial plan view of another fin of the fin-tube heat exchanger (A) A cross-sectional view of another fin of the conventional fin-tube heat exchanger when stacked, (b) a partial plan view of another fin of the fin-tube heat exchanger (A) A cross-sectional view of another fin of the conventional fin-tube heat exchanger when stacked, (b) a partial plan view of another fin of the fin-tube heat exchanger (A) A cross-sectional view of another fin of the conventional fin
  • a plurality of fins through which an air flow passes and a plurality of heat transfer tubes through which the flow of fluid flows, and the plurality of fins through which an air flow passes.
  • the device is characterized in that it is disposed only on the downstream side of the air flow with respect to the center of the heat transfer tube closest to the heat transfer tube, and is formed to be inclined with respect to the air flow.
  • frost formation can be reduced by providing a cut-off only on the downstream side of the air flow which is hard to frost-form.
  • the drainage performance is improved by smoothly flowing the water on the fins by cutting and raising in an inclined direction with respect to the air flow direction, so it is possible to improve the heat transfer performance.
  • the fin is formed by a flat seat formed around the heat transfer tube and a fin end on the downstream side of the air flow from the seat.
  • a fin flat portion to be formed; and a corrugated portion formed around the seat portion and around the fin flat portion and having peaks and valleys alternately formed, and the cut and raised portion is the fin It is characterized in that it is disposed on a flat portion.
  • the heat transfer area of the fins is increased by having the corrugated portion.
  • water can be guided by the fin flat portion formed from the seat portion around the heat transfer tube to the fin end portion on the downstream side of the air flow, and the drainage performance can be improved.
  • the cut-and-raised is formed in a bridge shape by a pair of rising sides connected to the fins and a pair of cut-off sides separated from the fins.
  • a slit is formed between the cut and raised side and the fin, and the rising side is formed in the vertical direction.
  • the rising and falling sides located upstream of the air flow are positioned higher than the rising and falling sides located downstream of the air flow. It is characterized by As a result, the precipitated water is guided to the lower end portion side of the fin wind by its own weight and the air flow, so that the drainage performance is improved.
  • the rising and falling sides located upstream of the air flow are positioned lower than the rising and falling sides located downstream of the air flow. It is characterized by As a result, the precipitated water is guided to the valleys of the wave-shaped portion to smoothly flow down, thereby improving the drainage performance.
  • the cut and raised portion is formed in a direction perpendicular to a straight line passing through the center of the heat transfer tube closest to the heat transfer tube.
  • the cut-and-raised portion is formed parallel to a straight line passing through the center of the heat transfer tube.
  • the heat exchange performance can be maintained without inhibiting the heat conduction to the cut-up and the downwind side.
  • the fin has a fin collar into which the heat transfer tube is inserted, and the height dimension is in the order of the cut-and-raised portion, the corrugated portion, and the fin collar. Is characterized by the fact that This can facilitate the stacking of the fins.
  • the fins located at least on the upstream side and the fins located on the downstream side are disposed in the air flow direction, and the fins on the upstream side are disposed
  • the height of the heat transfer tube of the present invention and the heat transfer tube of the fin on the downstream side are made different.
  • Embodiment 1 The finned-tube heat exchanger according to the first embodiment of the present invention has a plurality of fins 1 arranged at a predetermined interval Fp and substantially perpendicular to the fins 1 as in the conventional finned-tube heat exchanger shown in FIG. And a heat transfer pipe 2 inserted into the
  • a finned-tube heat exchanger is used as an evaporator is demonstrated as an example below.
  • FIG.1 (a) is sectional drawing of the fin which comprises the finned-tube heat exchanger in this Embodiment
  • FIG.1 (b) shows the partial plan view of the fin of a finned-tube heat exchanger.
  • the fin 1 has a flat seat 6, a fin flat portion 1 c, and a corrugated portion 5.
  • the wave-shaped portion 5 is generally called a corrugate, a waffle or the like.
  • the seat 6 is formed around the heat transfer tube 2 and guides the air flow 100 around the fin collar 3.
  • the fin flat portion 1 c is formed from the seat 6 to the fin end 1 d on the downstream side of the air flow 100.
  • the wave-shaped portion 5 is formed around the seat portion 6 and around the fin flat portion 1 c, and peaks and valleys are alternately formed.
  • the cut and raised portion 4 is disposed on the fin flat portion 1c.
  • the cut-and-raised portion 4 offsets a part of the fin 1 from the fin flat portion 1 c in a slit shape.
  • the cut-and-raised portion 4 is formed in a bridge shape by a pair of rising sides 4b connected to the fin flat surface portion 1c and a pair of cut-and-raised sides 4a separated from the fin flat surface portion 1c.
  • a cut-and-raised opening (slit) 4c is formed between itself and the portion 1c.
  • the rising side 4b is formed in the vertical direction.
  • the cut-and-raised portion 4 is disposed only on the downstream side of the air flow 100 with respect to the center of the heat transfer tube 2 closest to the heat transfer tube 2 and is formed inclined with respect to the air flow 100.
  • the rising side 4 b located on the upstream side of the air flow 100 is positioned higher than the rising side 4 b located on the downstream side of the air flow 100.
  • the upper and lower boundary lines are formed to be inclined in the same direction as the cut and raised portion 4.
  • An opening 4 c is formed in the upper and lower portions of the cut-and-raise 4.
  • the condensed drain water flows down and the air flow 100 passes through the opening 4 c. Further, since the rising side 4 b is formed in the vertical direction, the condensed drain water tends to flow down along the rising side 4 b by gravity.
  • the cut-and-raise 4 is a fin wind It is disposed only in the lower part 1b.
  • the corrugated portion 5 is disposed in the fin upper portion 1a and the fin lower portion 1b.
  • the cut and raised portion 4 is disposed on the fin flat surface portion 1 c outside the seat portion 6.
  • the cut-and-raised portions 4 are formed in a direction (longitudinal imaginary line M) perpendicular to the radial imaginary line N passing through the center of the heat transfer tube 2 closest to it. That is, the cut-and-raised portion 4 is disposed such that the straight cut-and-raised side 4 a perpendicularly intersects with the imaginary line N in the radial direction of the heat transfer tube 2 closest to the cut-and-raised portion 4.
  • the height of the fin collar 3 is Hc (for example, 1.5 mm)
  • the height of the cut and raised portion 4 is Hs (for example, 0.75 mm)
  • the corrugated portion 5 When the height of Hw is Hw (for example, 1 mm), it is formed to satisfy the relation of Hc> Hw> Hs. Furthermore, the cut and raised portions 4 are all raised in the same direction with respect to the fin flat portion 1c.
  • the air flow 100 passing through the gap between the fins 1 meanders, thereby promoting turbulent flow. Furthermore, in the fin lower portion 1b, a temperature boundary layer is formed by the cut-and-raised side 4a by passing the air flow 100 through the cut-and-raise 4.
  • the upset 4 promotes heat transfer. Therefore, by arranging the wave-shaped portion 5 and the cut and raised portion 4, heat transfer of the fin lower portion 1b having a low heat flow rate is further promoted, and the heat flow rates of the fin upper portion 1a and the fin lower portion 1b are compared. Become uniform. In particular, under operating conditions where the temperature of the fin 1 becomes less than 0 ° C. and frost formation on the fin-tube heat exchanger occurs, frost formation on the fin lower portion 1b is cut off and promoted by 4, and the fin upper portion 1a and The frost on the lower part of the fin wind 1b is relatively uniform.
  • the cut-and-raise 4 is formed in the same direction as the fin collar 3 from the fin flat surface portion 1 c, the swirl of the air flow 100 is not generated in the vicinity of the cut-off 4. I will not let you. Therefore, the increase in the ventilation resistance due to the cutting and raising 4 can be suppressed.
  • the cut-and-raised portion 4 is opened upward and downward by the cut-and-raised opening 4c, and is further inclined so that the upstream side of the air flow 100 becomes high. Therefore, as shown in FIG. 5, the drain water attached to the cut-and-raised part 4 flows down by the air flow 100 in addition to its own weight. Further, of the drain water attached to the cut-and-raised part 4, the drain water flowing down to the fin flat surface portion 1 c is added to its own weight along the boundary line inclined in the same direction as the cut-and-raised part 4. Flow down. Therefore, the drain water can be smoothly flowed down against the surface tension of the fins 1 for retaining the drain water, and the retention amount of water on the fins 1 can be reduced.
  • the drainage property of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the molten water generated by melting the frost at the time of defrosting is used. Flow down smoothly. Therefore, it is possible to suppress an increase in ventilation resistance due to remelting of the molten water retained in the fins 1 at the time of restoration of defrosting.
  • the adjacent fin flat portion 1 c and the cut-and-raised portion 4 may be in contact with each other. It is possible to reduce the retention amount of drain water due to the surface tension of the fins 1. Thereby, even under the operating condition that the drain water adheres to the fins 1, the drainage property of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the cut and raised portion 4 is disposed outside the seat portion 6, a predetermined distance can be taken between the cut and raised portion 4 and the fin collar 3. Therefore, the drain water adhering to the cut-and-raised part 4 flows downward without staying in the space with the fin collar 3 due to surface tension. Therefore, even under the operating condition that the drain water adheres to the fin 1, the drainage property of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the length formed between the contact points 20 of the corrugated portion 5 and the seat portion 6 is a distance D, and the distance D is a distance D
  • a circular area having a diameter is referred to as a seat 6, and the outside thereof is referred to as a fin flat portion 1c.
  • the fin wind lower portion 1 b is provided with the cut-and-raised portion 4 inclined with respect to the air flow 100 to promote the heat transfer of the fin wind lower portion 1 b. Therefore, in addition to the frost formation on the fin wind upper portion 1a and the fin wind lower portion 1b becoming relatively uniform under the operating condition that the temperature of the fin 1 becomes less than 0 ° C., the molten water generated at the time of defrosting is fin 1 It becomes difficult to stay in Therefore, a rapid increase in ventilation resistance due to local frost formation on the cut and rise 4 and a decrease in heat exchange amount are suppressed, and heat transfer from the cut and rise 4 is promoted. Furthermore, the frost formation on the conventional fin tube heat exchanger can be significantly improved.
  • the cut-and-raise 4 and the fin collar 3 are provided in the same direction, the cut-and-raise 4 may be formed in a direction different from the fin collar 3.
  • FIG. 1 A second embodiment of the present invention is shown in FIG.
  • the components having the same functions as those of the first embodiment are given the same reference numerals, and the description thereof is omitted. Only the components different from the first embodiment will be described below.
  • the cut-and-raised portion 4 is a part of the fin 1 shown in FIGS. 6 (a) and 6 (b) with respect to the fin plane portion 1c other than a part of the fin 1 shown in FIG. It may be bent so as to be substantially vertical.
  • one side is a rising side 4b, and the other three sides are a cutting and rising side 4a separated from the fin flat surface portion 1c. Then, a part of the fin 1 is raised and bent at the side 4b to form an opening 4c.
  • FIG. 1 A third embodiment of the present invention is shown in FIG.
  • the components having the same functions as those of the first embodiment are given the same reference numerals, and the description thereof is omitted. Only the components different from the first embodiment will be described below.
  • the cut-and-raised portion 4 is disposed to be inclined such that the downstream side of the air flow 100 is at a high position. That is, in the cutting and raising 4, the rising side 4 b located on the upstream side of the air flow 100 is positioned lower than the rising side 4 b located on the downstream side of the air flow 100. Further, among the boundary lines between the fin flat surface portion 1 c and the corrugated portion 5, the upper and lower boundary lines are formed to be inclined in the same direction as the cut and raised portion 4.
  • the frost melt dissolves using the inclination of the cutting and raising 4 and the generated molten water is made to flow down smoothly.
  • the drain water which flowed down to the fin plane part 1c among the drain water attached to the cutting and raising 4 flows down along the boundary line inclined in the same direction as the cutting and raising 4.
  • the molten water is allowed to flow downward in the direction of gravity by the peaks and valleys formed by the corrugated portion 5. Therefore, the retention of the water to the fin 1 can be reduced, and the increase in the draft resistance by re-icing of the molten water after the defrost return can be suppressed.
  • the temperature boundary layer on the surface of the fins 1 is disturbed to promote heat transfer. While maintaining it, heat exchange capacity can be further enhanced.
  • the heat transfer tube 2 is described as a round tube, but may be, for example, a flat tube.
  • the cut-up 4 described in the second embodiment may be applied to the third embodiment.
  • FIG. 8 is a partial plan view of a fin that constitutes a finned-tube heat exchanger according to Embodiment 4 of the present invention.
  • the same parts as in the first to third embodiments are assigned the same reference numerals and detailed explanations thereof will be omitted.
  • a plurality of fins 1 are arranged in parallel in the direction of air flow 100. That is, in the finned tube heat exchanger according to the fourth embodiment, at least the first row of fins 1 located on the upstream side and the second row of fins 1 located on the downstream side are disposed. Then, the heights of the heat transfer pipe 2 of the first row of fins 1 on the upstream side and the heat transfer tube 2 of the second row of fins 1 on the downstream side are made different. It is preferable to arrange the heat transfer tube 2 of the fin 1 of the second row between the two heat transfer tubes 2 of the fins 1 of the first row.
  • the finned-tube heat exchanger in the present embodiment facilitates heat exchange between the air flow 100 passing through the fins 1 of the first row and the heat transfer tubes 2 of the fins 1 of the second row.
  • the air flow 100 passes through one of the cut-and-raised portions 4 provided in the first row of fins 1 or the second row of fins 1.
  • the air flow 100 can form a temperature boundary layer relatively uniformly by the first row or the second row of cuts 4 to promote heat transfer.
  • the cut-and-raised portion 4 inclined to the air flow 100 is provided in the fin lower portion 1b, and the fins 1 are arranged in two rows in the direction of the air flow 100.
  • the heights of the heat transfer tubes 2 of the fins 1 and the heat transfer tubes 2 of the fins 1 of the second row on the downstream side are made different.
  • the air flow 100 passing through any position of the finned-tube heat exchanger can be relatively uniformly cut and raised 4 to promote heat transfer, and heat exchange capacity can be increased.
  • the fin wind upper portion 1a and the fin wind lower portion 1b are relatively uniformly frosted to prevent refreezing of the molten water at the time of defrosting.
  • the frost formation on the finned tube heat exchanger provided with the conventional cut and raised part 4 can also be greatly improved.
  • the finned-tube heat exchanger according to the fifth embodiment of the present invention has a plurality of fins 1 arranged at a predetermined interval Fp and substantially perpendicular to these fins 1 as in the conventional finned-tube heat exchanger shown in FIG. And a heat transfer pipe 2 inserted into the
  • a finned-tube heat exchanger is used as an evaporator is demonstrated as an example below.
  • FIG.9 (a) is sectional drawing of the fin which comprises the finned-tube heat exchanger in this Embodiment
  • FIG.9 (b) shows the partial top view of the fin of a finned-tube heat exchanger.
  • the fin 1 has a flat seat 6, a fin flat portion 1 c, and a corrugated portion 5.
  • the wave-shaped portion 5 is generally called a corrugate, a waffle or the like.
  • the seat 6 is formed around the heat transfer tube 2 and guides the air flow 100 around the fin collar 3.
  • the fin flat portion 1 c is formed from the seat 6 to the fin end 1 d on the downstream side of the air flow 100.
  • the wave-shaped portion 5 is formed around the seat portion 6 and around the fin flat portion 1 c, and peaks and valleys are alternately formed.
  • the cut and raised portion 4 is disposed on the fin flat portion 1c.
  • the cut-and-raised portion 4 offsets a part of the fin flat surface portion 1 c from the fin flat surface portion 1 c in a slit shape.
  • the cut-and-raised portion 4 is formed in a bridge shape by a pair of rising sides 4b connected to the fin flat surface portion 1c and a pair of cut-and-raised sides 4a separated from the fin flat surface portion 1c.
  • a cut-and-raised opening (slit) 4c is formed between itself and the portion 1c.
  • the rising side 4b is formed in the vertical direction.
  • the cut-and-raised portion 4 is disposed only on the downstream side of the air flow 100 with respect to the center of the heat transfer tube 2 closest to the heat transfer tube 2 and is formed inclined with respect to the air flow 100.
  • the rising side 4 b located on the upstream side of the air flow 100 is positioned higher than the rising side 4 b located on the downstream side of the air flow 100.
  • the upper and lower boundary lines are formed to be inclined in the same direction as the cut and raised portion 4.
  • the cut and raised portions 4 are formed in parallel to a radial imaginary line N passing through the center of the heat transfer tube 2.
  • the two cut and raised portions 4 according to the present embodiment are disposed on both sides of the imaginary radial line N passing through the center of the heat transfer tube 2 such that the upstream side of the air flow 100 is upward.
  • An opening 4 c is formed in the upper and lower portions of the cut-and-raise 4.
  • condensed drain water flows down and the air flow 100 passes. Further, since the rising side 4 b is formed in the vertical direction, the condensed drain water tends to flow down along the rising side 4 b by gravity.
  • the cut-and-raise 4 is a fin wind It is disposed only in the lower part 1b.
  • the corrugated portion 5 is disposed in the fin upper portion 1a and the fin lower portion 1b.
  • the cut and raised portion 4 is disposed on the fin flat surface portion 1 c outside the seat portion 6 formed in a circular shape around the fin collar 3.
  • the height of the fin collar 3 is Hc (for example, 1.5 mm)
  • the height of the cut-and-raised part 4 is Hs (for example, 0.75 mm)
  • Hw for example, 1 mm
  • the cut and raised portions 4 are all raised in the same direction with respect to the fin flat portion 1c.
  • the air flow 100 passing through the gap of the fins 1 meanders, thereby promoting turbulent flow. Furthermore, in the fin lower portion 1b, the air flow 100 is cut and raised 4 to form a temperature boundary layer at the cut and raised side 4a.
  • the heat transfer of the fin lower portion 1b having a low heat flow rate is further promoted by arranging the wave-shaped portion 5 and the cut-and-raise 4;
  • the heat flow rates of the fin upper portion 1a and the fin lower portion 1b become relatively uniform.
  • frost formation on the fin lower portion 1b is cut off and promoted by 4, and the fin upper portion 1a and The frost on the lower part of the fin wind 1b is relatively uniform.
  • the cut-and-raised portions 4 are disposed substantially in parallel with the radial imaginary line N of the heat transfer tube 2.
  • the cut-and-raised portion 4 disposed substantially in parallel with the radial imaginary line N may interrupt the heat transfer between the fin 1 and the heat transfer tube 2 while forming a discontinuous surface on the fin 1. It does not act as a thermal resistance between the fins 1 and the heat transfer tubes 2.
  • the cut-and-raised portion 4 disposed substantially parallel to the radial imaginary line N of the heat transfer tube 2 promotes heat transfer between the end portion of the fin 1 having a large distance to the heat transfer tube 2 and the heat transfer tube 2. Thereby, the heat flow velocity in the vicinity of the heat transfer tube 2 and the heat flow velocity around the end of the fin 1 become relatively uniform.
  • the air flow 100 guided by the corrugated portion 5 is cut and raised 4 by cutting the height Hw of the corrugated portion 5 higher than the height Hs of the raised portion 4.
  • the heat transfer can be promoted by passing through more reliably and cutting and raising 4.
  • the cut-and-raise 4 is formed in the same direction as the fin collar 3 from the fin flat surface portion 1 c, the swirl of the air flow 100 is not generated in the vicinity of the cut-off 4. I will not let you. Therefore, the increase in the ventilation resistance due to the cutting and raising 4 can be suppressed.
  • the cut-and-raised portion 4 is opened upward and downward by the cut-and-raised opening 4c, and is further inclined so that the upstream side of the air flow 100 becomes high. Therefore, as shown in FIG. 13, the drain water attached to the cut-and-raised part 4 flows down by the air flow 100 in addition to its own weight. Further, of the drain water attached to the cut-and-raised part 4, the drain water flowing down to the fin flat surface portion 1 c is added to its own weight along the boundary line inclined in the same direction as the cut-and-raised part 4. Flow down. Therefore, the drain water can be smoothly flowed down against the surface tension of the fins 1 for retaining the drain water, and the retention amount of water on the fins 1 can be reduced.
  • the drainage property of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the molten water generated by melting the frost at the time of defrosting is used. Flow down smoothly. Therefore, it is possible to suppress an increase in ventilation resistance due to remelting of the molten water retained in the fins 1 at the time of restoration of defrosting.
  • the adjacent fin flat portion 1 c and the cut-and-raise 4 may be in contact with each other. Instead, the drain water retained by the surface tension of the fins 1 can be reduced between the fins 1 to be stacked. Thereby, even under the operating condition that the drain water adheres to the fins 1, the drainage property of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the cut-and-raised portion 4 is disposed outside the circular seat portion 6 formed around the fin collar 3, a predetermined distance is taken between the cut-and-raised portion 4 and the fin collar 3 be able to. Therefore, the drain water adhering to the cut-and-raised part 4 flows downward without staying in the space with the fin collar 3 due to surface tension. Therefore, even under the operating condition that the drain water adheres to the fins 1, the drainage performance of the drain water is improved, and the ventilation resistance of the finned tube heat exchanger can be reduced.
  • the length formed between the contact points 20 of the corrugated portion 5 and the seat portion 6 is a distance D, and the distance D is a distance D
  • a circular area having a diameter is referred to as a seat 6, and the outside thereof is referred to as a fin flat portion 1c.
  • the fin wind lower portion 1 b is provided with the cut-and-raised portion 4 inclined with respect to the air flow 100 to promote the heat transfer of the fin wind lower portion 1 b. Therefore, in addition to the frost formation on the fin wind upper portion 1a and the fin wind lower portion 1b becoming relatively uniform under the operating condition that the temperature of the fin 1 becomes less than 0 ° C., the molten water generated at the time of defrosting is fin 1 It becomes difficult to stay in Therefore, a rapid increase in ventilation resistance due to local frost formation on the cut-up 4 and a decrease in heat exchange amount are suppressed, and heat transfer is promoted by the cut-up 4. Furthermore, the frost formation on the conventional fin tube heat exchanger can be significantly improved.
  • the cut-and-raise 4 and the fin collar 3 are provided in the same direction, the cut-and-raise 4 may be formed in a direction different from the fin collar 3.
  • FIG. 14 shows a sixth embodiment of the present invention.
  • the components having the same functions as those of the fifth embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only the configuration different from the fifth embodiment will be described below.
  • the cut-and-raised portion 4 is a part of the fin 1 shown in FIGS. 14 (a) and 14 (b) with respect to the fin plane portion 1c other than a part of the fin 1 shown in FIG. It may be bent so as to be substantially vertical.
  • one side is a rising side 4b, and the other three sides are a cutting and rising side 4a separated from the fin flat surface portion 1c. Then, a part of the fin 1 is raised and bent at the side 4b to form an opening 4c.
  • FIG. 15 shows a seventh embodiment of the present invention.
  • the components having the same functions as those of the fifth embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only the configuration different from the fifth embodiment will be described below.
  • the cut-and-raised portion 4 is disposed to be inclined such that the downstream side of the air flow 100 is at a high position. That is, in the cutting and raising 4, the rising side 4 b located on the upstream side of the air flow 100 is positioned lower than the rising side 4 b located on the downstream side of the air flow 100. Further, among the boundary lines between the fin flat surface portion 1 c and the corrugated portion 5, the upper and lower boundary lines are formed to be inclined in the same direction as the cut and raised portion 4.
  • the frost melt dissolves using the inclination of the cutting and raising 4 and the generated molten water is made to flow down smoothly.
  • the drain water which flowed down to the fin plane part 1c among the drain water attached to the cutting and raising 4 flows down along the boundary line inclined in the same direction as the cutting and raising 4.
  • the molten water is allowed to flow downward in the direction of gravity by the peaks and valleys formed by the corrugated portion 5. Therefore, the retention of the water to the fin 1 can be reduced, and the increase in the draft resistance by re-icing of the molten water after the defrost return can be suppressed.
  • the temperature boundary layer on the surface of the fins 1 is disturbed to promote heat transfer. While maintaining it, the heat exchange capacity can be further improved.
  • the heat transfer tube 2 is described as a round tube, but may be, for example, a flat tube. Further, the cut-up 4 described in the sixth embodiment may be applied to the seventh embodiment.
  • FIG. 16 is a partial plan view of a fin constituting a finned-tube heat exchanger according to an eighth embodiment of the present invention.
  • the same parts as in the first to seventh embodiments will be assigned the same reference numerals and detailed explanations thereof will be omitted.
  • a plurality of fins 1 are arranged in parallel in the direction of air flow 100. That is, in the finned tube heat exchanger according to the seventh embodiment, at least the first row of fins 1 located on the upstream side and the second row of fins 1 located on the downstream side are disposed. Then, the heights of the heat transfer pipe 2 of the first row of fins 1 on the upstream side and the heat transfer tube 2 of the second row of fins 1 on the downstream side are made different. It is preferable to arrange the heat transfer tube 2 of the fin 1 of the second row between the two heat transfer tubes 2 of the fins 1 of the first row.
  • the finned-tube heat exchanger in the present embodiment facilitates heat exchange between the air flow 100 passing through the fins 1 of the first row and the heat transfer tubes 2 of the fins 1 of the second row. Further, the air flow 100 passes through any one of the cut-and-raised portions 4 provided in the first row of fins 1 or the second row of fins 1. Therefore, the air flow 100 is cut and raised 4 to form a temperature boundary layer, which can promote heat transfer.
  • the cut-and-raised portion 4 inclined to the air flow 100 is provided in the fin lower portion 1b, and the fins 1 are arranged in two rows in the direction of the air flow 100.
  • the heights of the heat transfer tubes 2 of the fins 1 and the heat transfer tubes 2 of the fins 1 of the second row on the downstream side are made different.
  • the air flow 100 passing through any position of the finned tube heat exchanger can be improved by promoting heat transfer by cutting and raising 4 to improve the heat exchange performance.
  • the fin wind upper portion 1a and the fin wind lower portion 1b are relatively uniformly frosted to prevent refreezing of the molten water at the time of defrosting.
  • the frost formation on the finned tube heat exchanger provided with the conventional cut and raised part 4 can also be greatly improved.
  • the finned-tube heat exchanger according to the present invention is formed only on the downstream side of the fins with respect to the air flow direction, and reduces frost formation by cutting and raising with respect to the air flow direction. Since drainage property can be improved, it can apply to the heat exchanger of the refrigeration cycle device used for an air conditioning apparatus, a hot-water supply apparatus, a heating apparatus, etc.

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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/JP2013/002312 2012-04-27 2013-04-03 フィンチューブ熱交換器及びそれを備えた冷凍サイクル装置 WO2013161193A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP13781555.1A EP2843345B1 (en) 2012-04-27 2013-04-03 Fin-tube heat exchanger and refrigeration cycle device using same
CN201380022277.8A CN104272053B (zh) 2012-04-27 2013-04-03 翅片管热交换器和具备其的制冷循环装置
JP2014512319A JP6021081B2 (ja) 2012-04-27 2013-04-03 フィンチューブ熱交換器及びそれを備えた冷凍サイクル装置

Applications Claiming Priority (8)

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JP2012-102211 2012-04-27
JP2012102211 2012-04-27
JP2012105714 2012-05-07
JP2012-105714 2012-05-07
JP2012250915 2012-11-15
JP2012-250915 2012-11-15
JP2012250916 2012-11-15
JP2012-250916 2012-11-15

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JP (1) JP6021081B2 (zh)
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Publication number Priority date Publication date Assignee Title
JP6548729B2 (ja) * 2015-07-10 2019-07-24 三菱電機株式会社 熱交換器および空気調和装置
JP2020016418A (ja) * 2018-07-27 2020-01-30 株式会社ノーリツ 熱交換器およびこれを備えた温水装置
CN109186307B (zh) * 2018-09-30 2020-01-17 珠海格力电器股份有限公司 一种翅片及具有其的热交换器
CN110425904A (zh) * 2019-08-13 2019-11-08 青岛海信日立空调系统有限公司 一种平板翅片以及微通道换热器、空调

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JP2001091101A (ja) * 1999-09-20 2001-04-06 Fujitsu General Ltd 空気調和機の熱交換器
WO2003014649A1 (fr) * 2001-08-10 2003-02-20 Yokohama Tlo Company Ltd. Dispositif de transfert de chaleur
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WO2007004456A1 (ja) * 2005-07-01 2007-01-11 Daikin Industries, Ltd. フィンチューブ型熱交換器
JP2007309533A (ja) 2006-05-16 2007-11-29 Matsushita Electric Ind Co Ltd フィンチューブ熱交換器
JP2008089237A (ja) 2006-10-02 2008-04-17 Daikin Ind Ltd フィンチューブ型熱交換器

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JPS51137743U (zh) * 1975-04-28 1976-11-06
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JPH09189492A (ja) * 1996-01-10 1997-07-22 Hitachi Ltd 伝熱フィン
JPH10339595A (ja) * 1997-06-10 1998-12-22 Mitsubishi Heavy Ind Ltd 熱交換器
JPH11118379A (ja) * 1997-10-15 1999-04-30 Sanden Corp 多管式熱交換器
JP2001091101A (ja) * 1999-09-20 2001-04-06 Fujitsu General Ltd 空気調和機の熱交換器
WO2003014649A1 (fr) * 2001-08-10 2003-02-20 Yokohama Tlo Company Ltd. Dispositif de transfert de chaleur
JP2006138504A (ja) * 2004-11-10 2006-06-01 Mitsubishi Heavy Ind Ltd 熱交換器および空気調和機
WO2007004456A1 (ja) * 2005-07-01 2007-01-11 Daikin Industries, Ltd. フィンチューブ型熱交換器
JP2007309533A (ja) 2006-05-16 2007-11-29 Matsushita Electric Ind Co Ltd フィンチューブ熱交換器
JP2008089237A (ja) 2006-10-02 2008-04-17 Daikin Ind Ltd フィンチューブ型熱交換器

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Publication number Publication date
CN104272053A (zh) 2015-01-07
CN104272053B (zh) 2016-10-12
EP2843345B1 (en) 2017-01-11
JPWO2013161193A1 (ja) 2015-12-21
JP6021081B2 (ja) 2016-11-02
EP2843345A1 (en) 2015-03-04
EP2843345A4 (en) 2015-06-24

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