WO2017209323A1 - Three-dimensional wave-shaped fin and heat exchanger comprising same - Google Patents

Three-dimensional wave-shaped fin and heat exchanger comprising same Download PDF

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Publication number
WO2017209323A1
WO2017209323A1 PCT/KR2016/005765 KR2016005765W WO2017209323A1 WO 2017209323 A1 WO2017209323 A1 WO 2017209323A1 KR 2016005765 W KR2016005765 W KR 2016005765W WO 2017209323 A1 WO2017209323 A1 WO 2017209323A1
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WIPO (PCT)
Prior art keywords
tube
waveform
dimensional
pin
fluid
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PCT/KR2016/005765
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French (fr)
Korean (ko)
Inventor
강희찬
Original Assignee
군산대학교산학협력단
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Publication of WO2017209323A1 publication Critical patent/WO2017209323A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F1/26—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 being integral with the element
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F1/30—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 being attachable to the element
    • 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
    • F28F1/34—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 obliquely
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples

Definitions

  • the present invention relates to a three-dimensional corrugated fin and a heat exchanger including the same, and more particularly, to a three-dimensional corrugated fin and a heat exchanger including the same in accordance with the speed of the fluid flowing along the three-dimensional corrugated fin.
  • FIG. 1 is a view showing a two-dimensional waveform pin according to the prior art.
  • a corrugated fin heat exchanger according to the prior art includes a plurality of circular or elliptical tubes and a plurality of corrugated fins bonded to the tubes.
  • the corrugated fin according to the prior art forms a corrugated structure on the heat dissipation surface in order to maximize the heat exchange efficiency.
  • a relatively easy heat transfer fluid flows in one direction in the tube, and a poor heat transfer fluid flows in one direction in the corrugated fin, and heat exchange is performed between the fluid passing through the tube and the fluid passing through the corrugated fin.
  • water or refrigerant flows in the tube, and a gas such as air flows between the corrugated fins.
  • a joint formed in such a way as expansion, brazing, welding, or bonding.
  • Corrugated fins are generally made of materials with high thermal conductivity and high ductility, such as aluminum or copper.
  • the tube is joined to the corrugated fins and exposed to the flow of gas.
  • the gas is relatively dense and viscous, so the arrangement of the tubes is generally staggered.
  • products related to the joining and processing of tubes and tubes are standardized so that the arrangement of the tubes is a fixed factor.
  • Corrugated fin heat exchangers are widely used in air-cooled condensers, evaporators for air conditioners, desalination plants, radiators, and hydrogen coolers in generators.
  • Fins with thin strips have good heat transfer over the same area.
  • the corrugated fin heat exchanger has advantages in terms of productivity and safety of operation compared to a heat exchanger having a cutout portion of a fin, such as a louver fin heat exchanger and an offset fin heat exchanger.
  • a shear mold for shearing a fin in a manufacturing process is essential.
  • the shear surface requires the management of precise tolerances within several percent of the pin thickness.
  • the corrugated fin heat exchanger It is essential for the corrugated fins to flow gas between the corrugated fins in the device that operates the heat exchanger.
  • the higher the velocity of the gas the more advantages in terms of heat transfer.
  • the corrugated fin heat exchanger has a small pressure loss and excellent heat transfer performance, which is an important criterion for determining the superiority of the corrugated fin heat exchanger.
  • Figure 2 is a side cross-sectional schematic diagram showing the flow of fluid flowing through the two-dimensional waveform pin according to the prior art when installed and operated.
  • a number of vortices occur between two-dimensional corrugated fins according to the prior art. These vortices are very nonlinear depending on the pitch, amplitude (or crest), and Reynolds number of the waveform.
  • the shape of the vortex shown in FIG. 2 is only two-dimensionally expressed, and the shape of the actual vortex is a three-dimensional shape. Therefore, the corrugated fin structure is also preferably formed in a three-dimensional structure.
  • Figure 3 is a diagram showing the analysis by analyzing the shear stress distribution generated when the fluid flows in the plate pin according to the prior art.
  • Figure 4 is a diagram showing the analysis of the shear stress distribution generated when the fluid flows in the two-dimensional corrugated fins according to the prior art.
  • Figure 4 shows a very improved aspect than the case of the flat plate. Specifically, it can be seen that the change of the shear stress is somewhat improved in the direction perpendicular to the flow direction of the fluid. However, it can be seen that the size and strength of the vortex is still large in the wake of the tube.
  • Still another object of the present invention is to provide a three-dimensional corrugated fin having a low pressure drop and a heat exchanger including the same.
  • Still another object of the present invention is to provide a heat exchanger including a corrugated fin that can fundamentally block a related device failure caused by scattering of an incision by providing a structure in which an incision is omitted.
  • Three-dimensional corrugated fins and a heat exchanger including the same for achieving the above object: a three-dimensional corrugated fins for heat exchangers formed so that a plurality of tube binding spheres have a staggered arrangement at regular intervals, the three-dimensional corrugation A plurality of wave structures are formed on the surface of the fin, and the wave structures are line symmetrical structures of the upstream portion and the downstream portion based on the imaginary line passing through the center of the tube binding port and orthogonal to the flow direction of the fluid.
  • the pitch of the waveform in the portion where the velocity of the fluid flowing along the 3D corrugation pin is high may be longer than that of the adjacent waveform.
  • the portion of the fast velocity of the fluid flowing along the three-dimensional corrugated pin, the two tube binding sphere adjacent to each other located in the center on an imaginary line in the direction orthogonal to the flow direction of the fluid May be between.
  • the waveform amplitude of the portion adjacent to the tube binding sphere may be larger than the waveform amplitude of the center portion between the tube binding spheres.
  • the amplitude of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin may be greater than the amplitude of the adjacent waveform.
  • the pitch of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin may be shorter than the pitch of the adjacent waveform.
  • the inner portion of the virtual circle having a diameter of 101% to 130% of the diameter of the tube binding hole is not formed with a wavy structure It may be a flat structure.
  • the portion adjacent to the front end of the tube which is perpendicularly opposed to the flow direction of the fluid, and the rear end and adjacent to the rear end of the tube located 180 degrees opposite to the front end At the portion, dimples may be formed.
  • the protruding direction of the dimple formed in the portion adjacent to the front end of the tube may be opposite to the protruding direction of the dimple formed in the portion adjacent to the rear end of the tube.
  • the size of the dimple formed at the portion adjacent to the rear end of the tube may be 1 to 50% larger than the size of the dimple formed at the portion adjacent to the front end of the tube.
  • the dimple has an elliptical structure on the side cross-section, the long diameter of the elliptical structure may be in a direction parallel to the flow direction of the fluid.
  • the width (W dimple ) of the dimple is 20 to 30% of the radius of the tube binding sphere
  • the length of the dimple (L dimple ) is 21 to 60% of the radius of the tube binding sphere
  • the formation height of the dimple ( H dimple ) may be 20 to 30% of the radius of the tube tie.
  • a projection in the corrugated fin, may be formed at 130 degrees to 160 degrees clockwise in the planar direction from the tip of the tube which is perpendicular to the flow direction of the fluid.
  • the protrusion may be formed at a position spaced apart from the center position of the tube binding sphere by a distance 1.5 to 1.7 times the radius of the tube binding sphere.
  • the protrusion may be formed in a width of 20 to 30% of the radius of the tube binding sphere.
  • the amplitude of the waveform in the portion adjacent to the tip of the tube that is perpendicular to the flow direction of the fluid may be smaller than the amplitude of the waveform of the peripheral portion have.
  • the three-dimensional corrugated pin further comprises a corrugated pin connecting portion for fixing the adjacent pins arranged to be spaced apart by a predetermined distance, the tube pins can be formed in the corrugated pin connecting portion have.
  • the tube fasteners are arranged in a plurality of rows and columns based on the flow direction of the fluid of the three-dimensional corrugated fin, the cut may be formed between the columns formed by the plurality of tube fasteners.
  • an even number of waveforms may be formed between the cut portion and another adjacent cut portion.
  • the present invention can also provide a heat exchanger comprising the three-dimensional corrugated fins.
  • FIG. 1 is a view showing a two-dimensional waveform pin according to the prior art.
  • Figure 2 is a side cross-sectional view showing the flow of the fluid flowing through when a plurality of two-dimensional corrugated fins according to the prior art is installed and operated.
  • Figure 3 is a view showing the analysis of the shear stress distribution generated when the fluid flows in the plate pin according to the prior art.
  • Figure 4 is a diagram showing the analysis of the shear stress distribution generated when the fluid flows in the two-dimensional corrugated fins according to the prior art.
  • Figure 5 is a perspective view showing a three-dimensional waveform pin in accordance with an embodiment of the present invention.
  • FIG. 6 is a partial plan view illustrating a portion of the 3D corrugated pin shown in FIG. 5.
  • FIG. 7 is a cross-sectional view taken along a line A1-A1 of FIG. 6.
  • FIG. 8 is a cross-sectional view taken along the line A2-A2 of FIG. 6.
  • FIG. 9 is a cross-sectional view taken along line A3-A3 in FIG. 6.
  • FIG. 10 is a cross-sectional view taken along the line B1-B1 of FIG. 6.
  • FIG. 11 is a cross-sectional view taken along the line B2-B2 in FIG. 6.
  • FIG. 12 is a cross-sectional view taken along the line B3-B3 in FIG. 6.
  • FIG. 13 is a schematic plan view showing a state in which a portion adjacent to a tube binding hole of a three-dimensional corrugated fin according to an embodiment of the present invention is partitioned by an imaginary line.
  • FIG. 14 is an enlarged view of a portion C of FIG. 13.
  • 15 is a perspective view showing a three-dimensional corrugated pin according to another embodiment of the present invention.
  • FIG. 16 is a partially enlarged view illustrating a portion of the 3D waveform pin illustrated in FIG. 15.
  • FIG. 17 is a plan view illustrating the tube fastener and the dimple illustrated in FIG. 16.
  • 19 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated fin according to an embodiment of the present invention.
  • 20 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated pin according to another embodiment of the present invention.
  • Figure 5 is a perspective view showing a three-dimensional waveform pin in accordance with an embodiment of the present invention.
  • the three-dimensional corrugated fin 100 is a fin for a heat exchanger, in which a plurality of tube binding holes 101 are staggered at regular intervals, and includes a flow of fluid flowing between the tubes. It is characterized in that the amplitude (or crest) and the pitch (pitch) of the curved surface of the waveform is adjusted so that the shape of the corrugated pin is balanced.
  • the three-dimensional waveform pin 100 may be configured to include a waveform pin connecting portion 130 for fixing the waveform pin 100 disposed adjacent to be spaced apart by a predetermined distance.
  • the tube binding hole 101 may be formed in the corrugated pin connecting portion 130.
  • the waveform structure is formed It may be a flat structure that is not.
  • FIG. 6 is a partial plan view showing a portion of the three-dimensional corrugated pin shown in FIG. 5, and a cutaway view of FIG. 6 is shown in FIGS. 7 to 12.
  • FIG. 13 is a schematic plan view showing a state in which a portion adjacent to the tube binding hole of the three-dimensional corrugated fin according to the embodiment of the present invention is divided by a virtual line, and FIG. 14 is enlarged in part C of FIG. 13. The figure is shown.
  • the width of the flow path is narrowest between the tube and the tubes (regions a5, a6, a7), and the flow velocity is fastest at this portion. While heat transfer is good in this area, friction is also very high.
  • the free-flow cross-sectional area is greatest in the areas a1, a2, a3, a8, a9, a10, passing through this stream and reaching the next tube, at which point the flow velocity is the slowest. Fluid flowing around the tube forms a vortex at the rear end (a8 region) of the tube.
  • the heat transfer efficiency is low in the region a8 in which this vortex is formed.
  • Vortex generated in the tube located upstream at normal flow velocity affects the tip region a1 of the tube immediately after the tube. Therefore, the region from the rear end region a8 of the tube to the front end region a1 of the next tube is a region with poor heat transfer.
  • the three-dimensional corrugated fin 100 significantly improves the heat transfer effect by adjusting the amplitude (or crest) and the pitch of the waveform in a region where heat transfer is weak.
  • the pitch of the waveform in the portion where the velocity of the fluid flowing along the three-dimensional corrugated fin 100 is high may be longer than the pitch of the adjacent waveform. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
  • the above-mentioned high speed portion of the fluid may be between two adjacent tube binding holes 102 and 103 which are centered on the imaginary line L1 in the direction orthogonal to the flow direction of the fluid. . If this part is confirmed in FIG. 14, it is a5, a6, a7 area
  • the waveform amplitudes of the tube binding ports 102 and 103 and the adjacent portions a5 and a7 are the center portions between the tube binding holes 102 and 103. It is preferable that it is larger than the waveform amplitude of (a6). In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
  • the pitch of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin 100 may be shorter than the pitch of the adjacent waveform. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
  • the above-mentioned slow velocity portion of the fluid is adjacent to the tip portion of the tube which is perpendicularly opposed to the flow direction of the fluid, and adjacent to the rear end portion of the tube located 180 degrees opposite to the tip portion of the tube. It may be part. If this part is confirmed in FIG. 14, it is a2 and a9 area
  • the amplitude of the waveform formed in the portion where the velocity of the fluid is slow is larger than the amplitude of the adjacent waveform. That is, it is preferable that the amplitude of the waveform formed in the a3 and a10 areas is smaller than the amplitude of the waveform formed in the a2 and a9 areas. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
  • the three-dimensional corrugated fin 100 according to the present embodiment has a waveform having a different structure from each other according to the velocity of the fluid.
  • Such a configuration can reduce shear stress evenly to all regions in a direction perpendicular to the flow direction of the fluid by adjusting the amplitude (or crest) or pitch of the waveform according to the velocity of the fluid, and the tube
  • the pressure drop in the wake can be significantly reduced, and the size and strength of the vortex formed in the wake of the tube can be significantly reduced.
  • the three-dimensional corrugated fin 100 according to the present embodiment may have a waveform having a different structure depending on the velocity of the fluid, thereby significantly improving heat transfer performance.
  • the upstream portion and the downstream portion are line-symmetrical based on the virtual line L1 in the direction orthogonal to the flow direction of the fluid passing through the center of the tube binding port 101. Structure can be achieved. In this case, it is possible to simplify the mold design to produce the three-dimensional corrugated pin 100.
  • the tube binding holes 101 are arranged in a plurality of rows and columns based on the flow direction of the fluid, and between the columns formed by the plurality of tube binding holes 101.
  • a cutout 104 may be formed at the.
  • an even number of waveforms may be formed between the cutout 104 and another adjacent cutout 105.
  • the three-dimensional corrugated pin 100 can simplify the mold design in manufacturing the three-dimensional corrugated pin, and at the same time, the manufacturing process can be simplified, resulting in a great advantage in quality control and productivity. And the manufacturing cost can be significantly reduced.
  • the projection 120 may be formed at a portion 130 to 160 degrees clockwise in a planar direction from the tip of the tube which is perpendicular to the flow direction of the fluid.
  • the protrusion 120 is preferably formed at a position spaced apart from the center position of the tube binding port 101 by a distance 1.5 to 1.7 times the radius (R) of the tube binding port 101.
  • the fluid surrounding the tube generates a vortex in the rear end region (a8 region) of the tube.
  • the flow of the fluid may be guided to the rear end region (a8 region) of the tube.
  • the above-mentioned protrusion 120 is preferably formed to have a width of 20 to 30% of the radius R of the tube binding port 101 so as to effectively guide the flow of the fluid.
  • the amplitude of the waveform in the portion (a1 region) adjacent to the tip of the tube which is perpendicular to the flow direction of the fluid can be made smaller than the amplitude of the waveform of the peripheral portion. In this case too, it is possible to reduce the size and strength of the vortices that can be produced at the leading and trailing ends of the tube.
  • FIG. 15 is a perspective view illustrating a three-dimensional corrugated pin according to another embodiment of the present invention
  • FIG. 16 is a partially enlarged view illustrating a portion of the three-dimensional corrugated pin shown in FIG. 15.
  • FIG. 17 is a plan view showing the tube fasteners and the dimples shown in FIG. 16, and
  • FIG. 18 is a cross-sectional view taken along the line D1-D1 shown in FIG.
  • the 3D waveform pin 100 may have a configuration further including a dimple 110.
  • the region adjacent to the front end of the tube (a1 region) and the region adjacent to the rear end of the tube (a8 region) are regions of low fluid flow rate and poor heat transfer.
  • the three-dimensional corrugated fin 100 according to the present embodiment forms the dimple 110 in an area (a1 and a8 area) where heat transfer is weak.
  • the dimple 110 as shown in Figs. 16 to 17, the portion adjacent to the front end of the tube to be perpendicularly opposed to the flow direction of the fluid, and in a direction opposite to the front end 180 degrees It may be formed in a portion adjacent to the rear end of the tube located.
  • the protruding direction of the dimple 111 formed at the portion adjacent to the front end of the tube is opposite to the protruding direction of the dimple 112 formed at the portion adjacent to the rear end of the tube. Can be.
  • the dimple 110 is an elliptical structure on the side cross-section, the long diameter of the elliptical structure is preferably a direction parallel to the flow direction of the fluid.
  • the size of the dimple 110 may be variously designed according to the flow rate of the fluid and the diameter of the tube binding port 101.
  • Width (W dimple) is the length (L dimple) of the radius (R) and by 20 to 30%
  • the dimple 110 of the tube coupling opening (101) of the dimples (110) according to the embodiment preferably present example is nine tubes bundled It may be 21 to 60% relative to the radius (R) of (101).
  • forming height (H dimple) of the dimple 110 may be 20 to 30% of the radius (R) of the tube coupling opening (101).
  • the dimples downstream of the tube form a larger size than the dimples upstream.
  • the size of the dimples 112 formed at the portion adjacent to the rear end of the tube may be 1 to 50% larger than the size of the dimples 111 formed at the portion adjacent to the front end of the tube.
  • Three-dimensional corrugated fin 100 including such a configuration, by forming a dimple (dimple) at a specific position where the flow rate is low and heat transfer is weak, to locally promote the mixing of the fluid to achieve the heat transfer enhancement effect Can be.
  • 19 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated pin according to an embodiment of the present invention.
  • the three-dimensional waveform pin shown in FIG. 19 is an analysis diagram when the dimple is not formed.
  • the distribution of the shear stress is relatively uniform except for some hot spots, and the entire fin surface area is uniformly utilized.
  • 20 is a diagram illustrating an analysis of the shear stress distribution generated when the fluid flows to the three-dimensional corrugated pin according to another embodiment of the present invention.
  • the three-dimensional waveform pin shown in FIG. 20 is an analysis diagram for the case where the dimple is formed.
  • the effective heat transfer length of the fluid is increased and consequently the heat transfer performance is significantly increased. Can be improved.
  • the three-dimensional corrugated fin of the present invention by forming a waveform formed in the portion located between the tube in a specific structure, it is possible to significantly reduce the pressure drop in the wake of the fluid relative to the tube, resulting in a heat transfer effect Can be improved.
  • the three-dimensional corrugation pin of the present invention by forming a projection at a specific position, it is possible to easily guide the flow of fluid to the wake of the tube, reduce the size and strength of the vortex formed in the wake of the tube, resulting This can achieve the effect of reducing the pressure drop and promoting heat transfer.
  • the three-dimensional corrugated fin of the present invention by forming a dimple at a specific position where the flow rate is low and the heat transfer is weak, it is possible to locally promote the mixing of the fluid to achieve a heat transfer increase effect.
  • the upstream portion and the downstream portion have a line symmetrical structure based on the imaginary line passing through the center of the tube binding sphere and orthogonal to the flow direction of the fluid, thereby producing a three-dimensional corrugated fin. Therefore, the mold design can be simplified, and at the same time, the manufacturing process can be simplified, and as a result, it is greatly advantageous for quality control and productivity, and can significantly reduce the manufacturing cost.
  • the three-dimensional corrugated fin of the present invention by forming a cut between the rows formed by a plurality of tube binding spheres, it is possible to simplify the mold design in the production of three-dimensional corrugated fins, and at the same time to simplify the manufacturing process As a result, it is greatly advantageous for quality control and productivity, and can significantly reduce the production cost.
  • the three-dimensional corrugated fin of the present invention by providing a structure in which the incision is omitted, it is possible to provide a corrugated fin and a heat exchanger including the same, which can fundamentally block the failure of the associated device due to scattering of the incision, the incision is omitted
  • the structure can greatly reduce the cost of production equipment, mold and quality control of the heat exchanger.

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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

Disclosed are a three-dimensional wave-shaped fin and a heat exchanger comprising the same. A three-dimensional wave-shaped fin (100) according to an embodiment of the present invention is a three-dimensional wave-shaped fin (100) for a heat exchanger, which is formed to have a plurality of tube binding holes (101) alternately arranged at regular intervals. The constitution of the fin is characterized in that: the three-dimensional wave-shaped fin (100) has a plurality of wave structures formed on a surface thereof; the wave structures have an upstream portion and a downstream portion which are axisymmetric to each other with respect to an imaginary line (L1) passing through a center of the tube binding hole (101) in a direction perpendicular to a flow direction; and the wave structures have a longer wave pitch at a portion in which a fluid flows fast along the three-dimensional wave-shaped fin (100), compared to an adjacent portion. A three-dimensional wave-shaped fin according to the present invention enables an effective heat transfer length of fluid to be increased, and consequently can noticeably improve heat transfer performance.

Description

3차원 파형핀 및 이를 포함하는 열교환기 3D corrugated fin and heat exchanger including the same
본 발명은 3차원 파형핀 및 이를 포함하는 열교환기에 관한 것으로서, 보다 상세하게는 3차원 파형핀을 따라 흐르는 유체의 속도에 따라 파형 구조를 달리한 3차원 파형핀 및 이를 포함하는 열교환기에 관한 것이다.The present invention relates to a three-dimensional corrugated fin and a heat exchanger including the same, and more particularly, to a three-dimensional corrugated fin and a heat exchanger including the same in accordance with the speed of the fluid flowing along the three-dimensional corrugated fin.
도 1에는 종래 기술에 따른 2차원 파형핀을 나타내는 그림이 도시되어 있다.1 is a view showing a two-dimensional waveform pin according to the prior art.
도 1을 참조하면, 종래 기술에 따른 파형핀 열교환기의 경우, 다수의 원형 또는 타원형 튜브와, 튜브와 접합된 다수의 파형핀을 구비한다.Referring to FIG. 1, a corrugated fin heat exchanger according to the prior art includes a plurality of circular or elliptical tubes and a plurality of corrugated fins bonded to the tubes.
도 1에 도시된 바와 같이, 종래 기술에 따른 파형핀은 열교환 효율을 극대화하기 위하여 방열면에 파형 구조를 형성하고 있다.As shown in Figure 1, the corrugated fin according to the prior art forms a corrugated structure on the heat dissipation surface in order to maximize the heat exchange efficiency.
일반적으로 튜브에는 상대적으로 열전달이 용이한 유체가 일측 방향으로 흐르며, 파형핀에는 열전달이 잘 되지 않는 유체가 일측 방향으로 흐르면서, 튜브를 지나는 유체와 파형핀을 지나는 유체 사이에 열교환이 이루어진다. 일반적으로 튜브 내에는 물이나 냉매가 흐르며 파형핀 사이에는 공기와 같은 기체가 흐른다.In general, a relatively easy heat transfer fluid flows in one direction in the tube, and a poor heat transfer fluid flows in one direction in the corrugated fin, and heat exchange is performed between the fluid passing through the tube and the fluid passing through the corrugated fin. Generally, water or refrigerant flows in the tube, and a gas such as air flows between the corrugated fins.
튜브와 파형핀 사이에는 확관, 브레이징, 용접, 접착과 같은 방식으로 형성된 접합부가 마련된다. Between the tube and the corrugated fin is provided a joint formed in such a way as expansion, brazing, welding, or bonding.
튜브의 경우 통상적으로 철, 구리 또는 알루미늄 재질이 사용된다. 파형핀은 알루미늄이나 구리와 같이 열전도율이 높고 연성이 큰 재질이 사용되는 것이 일반적이다.For tubes, iron, copper or aluminum materials are typically used. Corrugated fins are generally made of materials with high thermal conductivity and high ductility, such as aluminum or copper.
튜브는 파형핀과 접합되어 기체의 흐름에 노출된다. 기체는 상대적으로 밀도와 점성이 낮아 튜브의 배열은 엇갈림 배열이 일반적이다. 또한 파형핀 열교환기에서 튜브 그리고 튜브의 접합과 가공에 관련한 제품은 표준화되어서 튜브의 배열은 고정인자이다.The tube is joined to the corrugated fins and exposed to the flow of gas. The gas is relatively dense and viscous, so the arrangement of the tubes is generally staggered. Also, in corrugated fin heat exchangers, products related to the joining and processing of tubes and tubes are standardized so that the arrangement of the tubes is a fixed factor.
파형핀 열교환기는 공기냉각 응축기, 공조기용 증발기, 담수설비, 방열기, 발전기의 수소냉각기 등에서는 널리 사용된다.Corrugated fin heat exchangers are widely used in air-cooled condensers, evaporators for air conditioners, desalination plants, radiators, and hydrogen coolers in generators.
루우버핀 옵셋핀과 같이 얇은 스트립을 포함한 핀은 동일 면적에 대하여 열전달 성능은 우수하다. 그러나 파형핀 열교환기는 루버핀 열교환기 옵셋핀 열교환기와 같이 핀의 절개부를 갖는 열교환기에 비하여 생산성과 운전의 안전성 측면에 장점이 있다. 즉, 절개부를 갖는 열교환기의 경우에 제조 공정에서 핀을 전단하는 전단금형이 필수적이다. 핀의 전단면에서 버(bur)와 같이 제품에 결정적인 저해요소를 방지하기 위하여 전단면은 핀 두께의 수 퍼센트 이내의 정교한 공차의 관리가 필요하다. 또한 전단 공구의 주기적인 교체, 이로 인한 비용의 증가 및 금형의 교체에 따른 생산 기간의 단축과 같은 문제가 야기된다. 또한 발전기 냉각기와 같이 수십 년간 매우 안정적인 운전환경이 요구되는 경우에는 얇은 스트립의 비산으로 인한 사고로 인하여 발전소 전체가 중단되는 사태가 발생할 수 있다.Fins with thin strips, such as louver fin offset fins, have good heat transfer over the same area. However, the corrugated fin heat exchanger has advantages in terms of productivity and safety of operation compared to a heat exchanger having a cutout portion of a fin, such as a louver fin heat exchanger and an offset fin heat exchanger. In other words, in the case of a heat exchanger having a cutout, a shear mold for shearing a fin in a manufacturing process is essential. In order to prevent critical determinants, such as burs, on the shear surface of the pin, the shear surface requires the management of precise tolerances within several percent of the pin thickness. Problems also arise such as the periodic replacement of shear tools, the resulting increase in costs and the shortening of production periods due to the replacement of molds. In addition, if a very stable operating environment is required for decades such as a generator cooler, the entire power plant may be shut down due to an accident due to the scattering of thin strips.
파형핀을 열교환기를 운용하는 장치에서 파형핀 사이에 기체를 흐르게 하는 것은 필수적이며 기체의 속도가 클수록 열전달 측면에서 장점이 많다. 그러나 속도가 증가하면 기체의 흐름을 유지하는데 압력손실이 증가하게 되고 휀의 운전비용이 증가한다. 따라서 파형핀 열교환기에서는 압력손실은 작고 열전달 성능은 우수한 파형구조는 파형핀 열교환기의 제품의 우수성을 판별하는 중요한 기준이 된다.It is essential for the corrugated fins to flow gas between the corrugated fins in the device that operates the heat exchanger. The higher the velocity of the gas, the more advantages in terms of heat transfer. However, as the speed increases, the pressure loss increases to maintain the flow of gas and the operating cost of the fan increases. Therefore, the corrugated fin heat exchanger has a small pressure loss and excellent heat transfer performance, which is an important criterion for determining the superiority of the corrugated fin heat exchanger.
도 2에는 종래 기술에 따른 2차원 파형핀이 복수개 설치되어 운용될 경우, 이를 통해 흐르는 유체의 흐름을 나타내는 측단면 모식도가 도시되어 있다.Figure 2 is a side cross-sectional schematic diagram showing the flow of fluid flowing through the two-dimensional waveform pin according to the prior art when installed and operated.
도 2에 도시된 바와 같이, 종래 기술에 따른 2차원 파형핀 사이에는 다수의 와류가 발생한다. 이러한 와류는 파형의 피치, 진폭(또는 파고) 및 Reynolds수에 따라 매우 비선형성이 크다.As shown in FIG. 2, a number of vortices occur between two-dimensional corrugated fins according to the prior art. These vortices are very nonlinear depending on the pitch, amplitude (or crest), and Reynolds number of the waveform.
도 2에 도시된 와류의 형상은 이차원적으로 표현된 것일 뿐, 실제 와류의 형상은 3차원 형상이다. 따라서, 파형핀 구조 역시 3차원 구조로 형성함이 바람직하다.The shape of the vortex shown in FIG. 2 is only two-dimensionally expressed, and the shape of the actual vortex is a three-dimensional shape. Therefore, the corrugated fin structure is also preferably formed in a three-dimensional structure.
도 3에는 종래 기술에 따른 평판핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이 도시되어 있다.Figure 3 is a diagram showing the analysis by analyzing the shear stress distribution generated when the fluid flows in the plate pin according to the prior art.
도 3에서 확인할 수 있는 바와 같이, 평판핀의 경우 튜브 후류에서 와류의 크기와 강도가 매우 큼을 알 수 있다. 또한, 유체의 흐름 방향과 수직을 이루는 방향으로 마찰(shear stress)의 변화가 매우 큼을 알 수 있다.As can be seen in Figure 3, in the case of the plate pin can be seen that the size and strength of the vortex is very large in the wake of the tube. In addition, it can be seen that the change of the shear stress is very large in the direction perpendicular to the flow direction of the fluid.
따라서, 이러한 양상을 보이는 평판핀의 경우, 열교환 효율이 매우 낮다는 문제점을 가지고 있다.Therefore, in the case of the plate fins exhibiting this aspect, there is a problem that the heat exchange efficiency is very low.
이러한 문제점을 해결하기 위해, 평판핀에 파형 구조를 형성시킨 2차원 파형핀이 개발되었다.In order to solve this problem, a two-dimensional waveform pin has been developed to form a waveform structure on the flat plate pin.
도 4에는 종래 기술에 따른 2차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이 도시되어 있다.Figure 4 is a diagram showing the analysis of the shear stress distribution generated when the fluid flows in the two-dimensional corrugated fins according to the prior art.
도 4에서 확인할 수 있는 바와 같이, 평판핀의 경우보다 매우 호전된 양상을 보이고 있다. 구체적으로, 유체의 흐름 방향과 수직을 이루는 방향으로 마찰(shear stress)의 변화가 다소 개선된 것을 확인할 수 있다. 그러나, 튜브 후류에서 와류의 크기와 강도가 여전히 큼을 확인할 수 있다.As can be seen in Figure 4, it shows a very improved aspect than the case of the flat plate. Specifically, it can be seen that the change of the shear stress is somewhat improved in the direction perpendicular to the flow direction of the fluid. However, it can be seen that the size and strength of the vortex is still large in the wake of the tube.
따라서, 상기 언급한 바와 같이, 종래 기술에 따른 열교환기용 핀에 대한 여러 문제점을 해결할 수 있는 기술이 필요한 실정이다.Therefore, as mentioned above, there is a need for a technique capable of solving various problems of the fin for a heat exchanger according to the prior art.
본 발명의 목적은, 열전달 성능이 높은 3차원 파형핀 및 이를 포함하는 열교환기를 제공하는 것이다.It is an object of the present invention to provide a three-dimensional corrugated fin having a high heat transfer performance and a heat exchanger including the same.
본 발명의 또 다른 목적은, 압력강하가 낮은 3차원 파형핀 및 이를 포함하는 열교환기를 제공하는 것이다.Still another object of the present invention is to provide a three-dimensional corrugated fin having a low pressure drop and a heat exchanger including the same.
본 발명의 또 다른 목적은, 절개부가 생략된 구조를 구비함으로써 절개부 비산에 따른 관련 장치 고장을 원천적으로 차단할 수 있는 파형핀 및 이를 포함하는 열교환기를 제공하는 것이다.Still another object of the present invention is to provide a heat exchanger including a corrugated fin that can fundamentally block a related device failure caused by scattering of an incision by providing a structure in which an incision is omitted.
이러한 목적을 달성하기 위한 본 발명의 일 측면에 따른 3차원 파형핀 및 이를 포함하는 열교환기는: 다수의 튜브 결속구가 일정한 간격으로 엇갈림 배열을 갖도록 형성된 열교환기용 3차원 파형핀으로서, 상기 3차원 파형핀의 표면에는 다수의 파형(wave) 구조가 형성되어 있고, 상기 파형 구조는, 튜브 결속구의 중심을 지나고 유체의 흐름방향과 직교하는 방향의 가상 선을 기준으로 상류 부분과 하류 부분이 선대칭구조이며, 상기 3차원 파형핀을 따라 흐르는 유체의 속도가 빠른 부분에서의 파형의 피치는, 인접하는 파형의 피치보다 긴 구조일 수 있다.Three-dimensional corrugated fins and a heat exchanger including the same according to an aspect of the present invention for achieving the above object: a three-dimensional corrugated fins for heat exchangers formed so that a plurality of tube binding spheres have a staggered arrangement at regular intervals, the three-dimensional corrugation A plurality of wave structures are formed on the surface of the fin, and the wave structures are line symmetrical structures of the upstream portion and the downstream portion based on the imaginary line passing through the center of the tube binding port and orthogonal to the flow direction of the fluid. The pitch of the waveform in the portion where the velocity of the fluid flowing along the 3D corrugation pin is high may be longer than that of the adjacent waveform.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀을 따라 흐르는 유체의 속도가 빠른 부분은, 유체의 흐름방향과 직교하는 방향의 가상 선 상에 중심이 위치하는 서로 인접하는 두 개의 튜브 결속구 사이일 수 있다.In one embodiment of the present invention, the portion of the fast velocity of the fluid flowing along the three-dimensional corrugated pin, the two tube binding sphere adjacent to each other located in the center on an imaginary line in the direction orthogonal to the flow direction of the fluid May be between.
이 경우, 상기 두 개의 튜브 결속구 사이에 있어서, 튜브 결속구와 인접하는 부분의 파형 진폭은, 튜브 결속구 사이의 정중앙 부분의 파형 진폭보다 큰 것일 수 있다.In this case, between the two tube binding spheres, the waveform amplitude of the portion adjacent to the tube binding sphere may be larger than the waveform amplitude of the center portion between the tube binding spheres.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀을 따라 흐르는 유체의 속도가 느린 부분에서의 파형의 진폭은 인접하는 파형의 진폭보다 큰 것일 수 있다.In one embodiment of the present invention, the amplitude of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin may be greater than the amplitude of the adjacent waveform.
또한, 상기 3차원 파형핀을 따라 흐르는 유체의 속도가 느린 부분에서의 파형의 피치는 인접하는 파형의 피치보다 짧은 것일 수 있다.In addition, the pitch of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin may be shorter than the pitch of the adjacent waveform.
이때, 상기 3차원 파형핀을 따라 흐르는 유체의 속도가 느린 부분은, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 상기 튜브의 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분일 수 있다.At this time, the portion of the slow velocity of the fluid flowing along the three-dimensional corrugated fin, the portion adjacent to the front end of the tube which is perpendicularly opposed to the flow direction of the fluid, and the tube located in a direction opposite to the front end of the tube 180 degrees It may be a portion adjacent to the rear end.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀의 튜브 결속구와 인접하는 부분에 있어서, 튜브 결속구의 직경 대비 101 % 내지 130 % 의 직경을 가지는 가상 원 내측 부분은 파형 구조가 형성되어 있지 않은 평평한 구조일 수 있다.In one embodiment of the present invention, in the portion adjacent to the tube binding hole of the three-dimensional corrugated fin, the inner portion of the virtual circle having a diameter of 101% to 130% of the diameter of the tube binding hole is not formed with a wavy structure It may be a flat structure.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분에, 딤플(dimple)이 형성될 수 있다.In one embodiment of the present invention, in the three-dimensional corrugated fin, the portion adjacent to the front end of the tube which is perpendicularly opposed to the flow direction of the fluid, and the rear end and adjacent to the rear end of the tube located 180 degrees opposite to the front end At the portion, dimples may be formed.
이 경우, 상기 튜브의 선단부와 인접하는 부분에 형성된 딤플의 돌출방향은, 튜브의 후단부와 인접하는 부분에 형성된 딤플의 돌출방향과 서로 정반대방향일 수 있다.In this case, the protruding direction of the dimple formed in the portion adjacent to the front end of the tube may be opposite to the protruding direction of the dimple formed in the portion adjacent to the rear end of the tube.
또한, 상기 튜브의 후단부와 인접하는 부분에 형성된 딤플의 크기는, 튜브의 선단부와 인접하는 부분에 형성된 딤플의 크기 대비 1 내지 50 % 더 큰 것일 수 있다.In addition, the size of the dimple formed at the portion adjacent to the rear end of the tube may be 1 to 50% larger than the size of the dimple formed at the portion adjacent to the front end of the tube.
또한, 상기 딤플은 측단면상 타원형 구조이고, 상기 타원형 구조의 장경은 유체의 흐름방향과 평행한 방향일 수 있다.In addition, the dimple has an elliptical structure on the side cross-section, the long diameter of the elliptical structure may be in a direction parallel to the flow direction of the fluid.
이때, 상기 딤플의 폭(Wdimple)은, 튜브 결속구의 반경 대비 20 내지 30 %이고, 상기 딤플의 길이(Ldimple)는, 튜브 결속구의 반경 대비 21 내지 60 %이고, 상기 딤플의 형성 높이(Hdimple)는, 튜브 결속구의 반경 대비 20 내지 30 %일 수 있다.At this time, the width (W dimple ) of the dimple is 20 to 30% of the radius of the tube binding sphere, the length of the dimple (L dimple ) is 21 to 60% of the radius of the tube binding sphere, the formation height of the dimple ( H dimple ) may be 20 to 30% of the radius of the tube tie.
본 발명의 일 실시예에 있어서, 상기 파형핀에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부로부터 평면상 시계방향으로 130도 내지 160도 부분에는, 돌기가 형성될 수 있다.In one embodiment of the present invention, in the corrugated fin, a projection may be formed at 130 degrees to 160 degrees clockwise in the planar direction from the tip of the tube which is perpendicular to the flow direction of the fluid.
이 경우, 상기 돌기는, 튜브 결속구의 반경 대비 1.5 배 내지 1.7 배의 거리만큼 튜브 결속구의 중심 위치로부터 이격된 위치에 형성될 수 있다.In this case, the protrusion may be formed at a position spaced apart from the center position of the tube binding sphere by a distance 1.5 to 1.7 times the radius of the tube binding sphere.
또한, 상기 돌기는 튜브 결속구의 반경 대비 20 내지 30 %의 폭으로 형성될 수 있다.In addition, the protrusion may be formed in a width of 20 to 30% of the radius of the tube binding sphere.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분에서의 파형의 진폭은, 주변 부분의 파형의 진폭보다 작은 것일 수 있다.In one embodiment of the present invention, in the three-dimensional corrugated fin, the amplitude of the waveform in the portion adjacent to the tip of the tube that is perpendicular to the flow direction of the fluid, may be smaller than the amplitude of the waveform of the peripheral portion have.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀은, 인접하여 배치된 파형핀을 소정 거리만큼 이격되도록 고정시키는 파형핀 연결부를 더 포함하고, 상기 파형핀 연결부에 튜브 결속구가 형성될 수 있다.In one embodiment of the present invention, the three-dimensional corrugated pin further comprises a corrugated pin connecting portion for fixing the adjacent pins arranged to be spaced apart by a predetermined distance, the tube pins can be formed in the corrugated pin connecting portion have.
본 발명의 일 실시예에 있어서, 상기 3차원 파형핀의 유체의 흐름방향을 기준으로 튜브 결속구는 다수의 행과 열로 배열되고, 다수의 튜브 결속구가 형성하는 열 사이에 절단부가 형성될 수 있다.In one embodiment of the present invention, the tube fasteners are arranged in a plurality of rows and columns based on the flow direction of the fluid of the three-dimensional corrugated fin, the cut may be formed between the columns formed by the plurality of tube fasteners. .
이 경우, 상기 절단부와 인접하는 또 다른 절단부 사이에는 짝수 개수의 파형이 형성될 수 있다.In this case, an even number of waveforms may be formed between the cut portion and another adjacent cut portion.
본 발명은 또한, 상기 3차원 파형핀을 포함하는 것을 특징으로 하는 열교환기를 제공할 수 있다.The present invention can also provide a heat exchanger comprising the three-dimensional corrugated fins.
도 1은 종래 기술에 따른 2차원 파형핀을 나타내는 그림이다.1 is a view showing a two-dimensional waveform pin according to the prior art.
도 2는 종래 기술에 따른 2차원 파형핀이 복수개 설치되어 운용될 경우, 이를 통해 흐르는 유체의 흐름을 나타내는 측단면 모식도이다.Figure 2 is a side cross-sectional view showing the flow of the fluid flowing through when a plurality of two-dimensional corrugated fins according to the prior art is installed and operated.
도 3은 종래 기술에 따른 평판핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이다.Figure 3 is a view showing the analysis of the shear stress distribution generated when the fluid flows in the plate pin according to the prior art.
도 4는 종래 기술에 따른 2차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이다.Figure 4 is a diagram showing the analysis of the shear stress distribution generated when the fluid flows in the two-dimensional corrugated fins according to the prior art.
도 5는 본 발명의 일 실시예에 따른 3차원 파형핀을 나타내는 사시도이다.Figure 5 is a perspective view showing a three-dimensional waveform pin in accordance with an embodiment of the present invention.
도 6은 도 5에 도시된 3차원 파형핀의 일부분을 나타내는 부분 평면도이다.FIG. 6 is a partial plan view illustrating a portion of the 3D corrugated pin shown in FIG. 5.
도 7은 도 6의 A1-A1선 절단면도이다.FIG. 7 is a cross-sectional view taken along a line A1-A1 of FIG. 6.
도 8은 도 6의 A2-A2선 절단면도이다.FIG. 8 is a cross-sectional view taken along the line A2-A2 of FIG. 6.
도 9는 도 6의 A3-A3선 절단면도이다.9 is a cross-sectional view taken along line A3-A3 in FIG. 6.
도 10은 도 6의 B1-B1선 절단면도이다.FIG. 10 is a cross-sectional view taken along the line B1-B1 of FIG. 6.
도 11은 도 6의 B2-B2선 절단면도이다.FIG. 11 is a cross-sectional view taken along the line B2-B2 in FIG. 6.
도 12는 도 6의 B3-B3선 절단면도이다.12 is a cross-sectional view taken along the line B3-B3 in FIG. 6.
도 13은 본 발명의 일 실시예에 따른 3차원 파형핀의 튜브 결속구와 인접하는 부분을 가상의 선으로 구획한 모습을 나타내는 평면 모식도이다.FIG. 13 is a schematic plan view showing a state in which a portion adjacent to a tube binding hole of a three-dimensional corrugated fin according to an embodiment of the present invention is partitioned by an imaginary line.
도 14는 도 13의 C 부분 확대도이다.14 is an enlarged view of a portion C of FIG. 13.
도 15는 본 발명의 또 다른 실시예에 따른 3차원 파형핀을 나타내는 사시도이다.15 is a perspective view showing a three-dimensional corrugated pin according to another embodiment of the present invention.
도 16은 도 15에 도시된 3차원 파형핀의 일부분을 나타내는 부분 확대도이다.FIG. 16 is a partially enlarged view illustrating a portion of the 3D waveform pin illustrated in FIG. 15.
도 17은 도 16에 도시된 튜브 결속구와 딤플을 나타내는 평면도이다.FIG. 17 is a plan view illustrating the tube fastener and the dimple illustrated in FIG. 16.
도 18은 도 17에 도시된 D1-D1선 절단면도이다.18 is a cross-sectional view taken along the line D1-D1 shown in FIG. 17.
도 19는 본 발명의 일 실시예에 따른 3차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이다.19 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated fin according to an embodiment of the present invention.
도 20은 본 발명의 또 다른 실시예에 따른 3차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이다.20 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated pin according to another embodiment of the present invention.
이하 도면을 참조하여 본 발명의 바람직한 실시예를 상세히 설명하기로 한다. 이에 앞서, 본 명세서 및 청구범위에 사용된 용어나 단어는 통상적이거나 사전적인 의미로 한정하여 해석되어서는 아니되며, 본 발명의 기술적 사상에 부합하는 의미와 개념으로 해석되어야 한다.Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings. Prior to this, the terms or words used in the present specification and claims should not be construed as being limited to ordinary or dictionary meanings, but should be construed as meanings and concepts consistent with the technical spirit of the present invention.
본 명세서 전체에서, 어떤 부재가 다른 부재 "상에" 위치하고 있다고 할 때, 이는 어떤 부재가 다른 부재에 접해 있는 경우뿐 아니라 두 부재 사이에 또 다른 부재가 존재하는 경우도 포함한다. 본 명세서 전체에서, 어떤 부분이 어떤 구성요소를 "포함" 한다고 할 때, 이는 특별히 반대되는 기재가 없는 한 다른 구성요소를 제외하는 것이 아니라 다른 구성 요소를 더 포함할 수 있는 것을 의미한다.Throughout this specification, when a member is located "on" another member, this includes not only when one member is in contact with another member but also when another member exists between the two members. Throughout this specification, when a part is said to "include" a certain component, it means that it can further include other components, without excluding other components unless otherwise stated.
도 5에는 본 발명의 일 실시예에 따른 3차원 파형핀을 나타내는 사시도가 도시되어 있다.Figure 5 is a perspective view showing a three-dimensional waveform pin in accordance with an embodiment of the present invention.
도 5를 참조하면, 본 실시예에 따른 3차원 파형핀(100)은, 다수의 튜브 결속구(101)가 일정한 간격으로 엇갈림 배열을 갖도록 형성된 열교환기용 핀으로서, 튜브 사이를 흐르는 유체의 흐름과 파형핀의 형상이 조화를 이루도록 파형의 굴곡면의 진폭(또는 파고)과 피치(pitch)를 조정한 것을 특징으로 한다.Referring to FIG. 5, the three-dimensional corrugated fin 100 according to the present embodiment is a fin for a heat exchanger, in which a plurality of tube binding holes 101 are staggered at regular intervals, and includes a flow of fluid flowing between the tubes. It is characterized in that the amplitude (or crest) and the pitch (pitch) of the curved surface of the waveform is adjusted so that the shape of the corrugated pin is balanced.
또한, 본 실시예에 따른 3차원 파형핀(100)은, 인접하여 배치된 파형핀(100)을 소정 거리만큼 이격되도록 고정시키는 파형핀 연결부(130)를 포함하는 구성일 수 있다. 이때, 파형핀 연결부(130)에 튜브 결속구(101)가 형성될 수 있다.In addition, the three-dimensional waveform pin 100 according to the present embodiment may be configured to include a waveform pin connecting portion 130 for fixing the waveform pin 100 disposed adjacent to be spaced apart by a predetermined distance. In this case, the tube binding hole 101 may be formed in the corrugated pin connecting portion 130.
또한, 3차원 파형핀(100)의 튜브 결속구(101)와 인접하는 부분에 있어서, 튜브 결속구(101)의 직경 대비 101 % 내지 130 % 의 직경을 가지는 가상 원 내측 부분은 파형 구조가 형성되어 있지 않은 평평한 구조일 수 있다.In addition, in the portion adjacent to the tube binding hole 101 of the three-dimensional corrugated fin 100, the inner portion of the virtual circle having a diameter of 101% to 130% of the diameter of the tube binding hole 101, the waveform structure is formed It may be a flat structure that is not.
이하에서는 도 6 내지 도 14를 참고하여, 본 실시예에 따른 3차원 파형핀(100)의 구조에 대해 상세히 설명하기로 한다.Hereinafter, the structure of the 3D waveform pin 100 according to the present embodiment will be described in detail with reference to FIGS. 6 to 14.
도 6에는 도 5에 도시된 3차원 파형핀의 일부분을 나타내는 부분 평면도가 도시되어 있으며, 도 7내지 도 12에는 도 6의 절단면도가 도시되어 있다. 또한, 도 13에는 본 발명의 일 실시예에 따른 3차원 파형핀의 튜브 결속구와 인접하는 부분을 가상의 선으로 구획한 모습을 나타내는 평면 모식도가 도시되어 있고, 도 14에는 도 13의 C 부분 확대도가 도시되어 있다.FIG. 6 is a partial plan view showing a portion of the three-dimensional corrugated pin shown in FIG. 5, and a cutaway view of FIG. 6 is shown in FIGS. 7 to 12. FIG. 13 is a schematic plan view showing a state in which a portion adjacent to the tube binding hole of the three-dimensional corrugated fin according to the embodiment of the present invention is divided by a virtual line, and FIG. 14 is enlarged in part C of FIG. 13. The figure is shown.
우선, 도 13 및 도 14를 참조하면, 튜브와 튜브 사이(a5, a6, a7 영역)에서 유로의 폭이 가장 좁으며, 이 부분에서 유속이 가장 빠르다. 이 영역에서는 열전달이 잘 이루어지는 반면, 마찰도 매우 크다. 이 흐름을 지나 다음 튜브에 도달하는 a1, a2, a3, a8, a9, a10 영역에서 자유흐름 단면적이 가장 크며, 이 지점에서 유속이 가장 느리다. 튜브를 감싸고 흐르는 유체는 튜브의 후단부(a8 영역)에서 와류를 형성한다. 이 와류가 형성되는 영역(a8)에서 열전달 효율이 낮다. 통상의 유속에서 상류에 위치한 튜브에서 발생한 와류는 튜브 바로 다음 튜브의 선단부 영역(a1)까지 영향을 미친다. 따라서, 튜브의 후단부 영역(a8)부터 다음 튜브의 선단부 영역(a1)까지의 영역은 열전달이 취약한 영역이다.First, referring to FIG. 13 and FIG. 14, the width of the flow path is narrowest between the tube and the tubes (regions a5, a6, a7), and the flow velocity is fastest at this portion. While heat transfer is good in this area, friction is also very high. The free-flow cross-sectional area is greatest in the areas a1, a2, a3, a8, a9, a10, passing through this stream and reaching the next tube, at which point the flow velocity is the slowest. Fluid flowing around the tube forms a vortex at the rear end (a8 region) of the tube. The heat transfer efficiency is low in the region a8 in which this vortex is formed. Vortex generated in the tube located upstream at normal flow velocity affects the tip region a1 of the tube immediately after the tube. Therefore, the region from the rear end region a8 of the tube to the front end region a1 of the next tube is a region with poor heat transfer.
본 실시예에 따른 3차원 파형핀(100)은 열전달이 취약한 영역에 대한 파형의 진폭(또는 파고)과 피치를 조절함으로써, 열전달 효과를 현저히 향상시키고 있다.The three-dimensional corrugated fin 100 according to the present embodiment significantly improves the heat transfer effect by adjusting the amplitude (or crest) and the pitch of the waveform in a region where heat transfer is weak.
구체적으로, 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 빠른 부분에서의 파형의 피치는, 인접하는 파형의 피치보다 길 수 있다. 이 경우, 후류에서의 압력강하를 줄이고 열전달을 촉진할 수 있다.Specifically, the pitch of the waveform in the portion where the velocity of the fluid flowing along the three-dimensional corrugated fin 100 is high may be longer than the pitch of the adjacent waveform. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
이때, 상기 언급한 유체의 속도가 빠른 부분은, 유체의 흐름방향과 직교하는 방향의 가상 선(L1) 상에 중심이 위치하는 서로 인접하는 두 개의 튜브 결속구(102, 103) 사이일 수 있다. 이 부분을 도 14에서 확인하면, a5, a6, a7 영역이다.In this case, the above-mentioned high speed portion of the fluid may be between two adjacent tube binding holes 102 and 103 which are centered on the imaginary line L1 in the direction orthogonal to the flow direction of the fluid. . If this part is confirmed in FIG. 14, it is a5, a6, a7 area | region.
또한, 두 개의 튜브 결속구(102, 103) 사이에 있어서, 튜브 결속구(102, 103)와 인접하는 부분(a5, a7)의 파형 진폭은, 튜브 결속구(102, 103) 사이의 정중앙 부분(a6)의 파형 진폭보다 큼이 바람직하다. 이 경우, 후류에서의 압력강하를 줄이고 열전달을 촉진할 수 있다.In addition, between the two tube binding ports 102 and 103, the waveform amplitudes of the tube binding ports 102 and 103 and the adjacent portions a5 and a7 are the center portions between the tube binding holes 102 and 103. It is preferable that it is larger than the waveform amplitude of (a6). In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
반면, 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 느린 부분에서의 파형의 피치는, 인접하는 파형의 피치보다 짧을 수 있다. 이 경우, 후류에서의 압력강하를 줄이고 열전달을 촉진할 수 있다.On the other hand, the pitch of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin 100 may be shorter than the pitch of the adjacent waveform. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
이때, 상기 언급한 유체의 속도가 느린 부분은, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 상기 튜브의 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분일 수 있다. 이 부분을 도 14에서 확인하면, a2, a9 영역이다.At this time, the above-mentioned slow velocity portion of the fluid is adjacent to the tip portion of the tube which is perpendicularly opposed to the flow direction of the fluid, and adjacent to the rear end portion of the tube located 180 degrees opposite to the tip portion of the tube. It may be part. If this part is confirmed in FIG. 14, it is a2 and a9 area | regions.
또한, 유체의 속도가 느린 부분 즉, a2, a9 영역에 형성된 파형의 진폭은 인접하는 파형의 진폭보다 큼이 바람직하다. 즉, a3, a10 영역에 형성된 파형의 진폭은 a2, a9 영역에 형성된 파형의 진폭보다 작음이 바람직하다. 이 경우, 후류에서의 압력강하를 줄이고 열전달을 촉진할 수 있다.In addition, it is preferable that the amplitude of the waveform formed in the portion where the velocity of the fluid is slow, that is, the regions a2 and a9, is larger than the amplitude of the adjacent waveform. That is, it is preferable that the amplitude of the waveform formed in the a3 and a10 areas is smaller than the amplitude of the waveform formed in the a2 and a9 areas. In this case, it is possible to reduce the pressure drop in the wake and promote heat transfer.
이상에서 설명한 바와 같이, 본 실시예에 따른 3차원 파형핀(100)은 유체의 속도에 따라 서로 상이한 구조의 파형을 가지고 있다. 이러한, 구성은, 유체의 속도에 따라 파형의 진폭(또는 파고) 내지 피치를 조절함으로써, 유체의 흐름 방향과 수직을 이루는 방향으로 마찰(shear stress)을 모든 영역에 대해서 균등하게 줄일 수 있고, 튜브 후류에서의 압력강하를 현저히 줄일 수 있으며, 튜브 후류에서 형성되는 와류의 크기와 강도를 현저히 저감시킬 수 있다. 결과적으로 본 실시예에 따른 3차원 파형핀(100)은 유체의 속도에 따라 서로 상이한 구조의 파형을 가지도록 함으로써, 열전달 성능을 현저히 향상시킬 수 있다.As described above, the three-dimensional corrugated fin 100 according to the present embodiment has a waveform having a different structure from each other according to the velocity of the fluid. Such a configuration can reduce shear stress evenly to all regions in a direction perpendicular to the flow direction of the fluid by adjusting the amplitude (or crest) or pitch of the waveform according to the velocity of the fluid, and the tube The pressure drop in the wake can be significantly reduced, and the size and strength of the vortex formed in the wake of the tube can be significantly reduced. As a result, the three-dimensional corrugated fin 100 according to the present embodiment may have a waveform having a different structure depending on the velocity of the fluid, thereby significantly improving heat transfer performance.
한편, 본 실시예에 따른 3차원 파형핀(100)은, 튜브 결속구(101)의 중심을 지나고 유체의 흐름방향과 직교하는 방향의 가상 선(L1)을 기준으로 상류 부분과 하류 부분이 선대칭구조를 이룰 수 있다. 이 경우, 3차원 파형핀(100)을 제작할 수 있는 금형설계를 단순화 할 수 있다.On the other hand, the three-dimensional corrugated fin 100 according to the present embodiment, the upstream portion and the downstream portion are line-symmetrical based on the virtual line L1 in the direction orthogonal to the flow direction of the fluid passing through the center of the tube binding port 101. Structure can be achieved. In this case, it is possible to simplify the mold design to produce the three-dimensional corrugated pin 100.
또한, 본 실시예에 따른 3차원 파형핀(100)은 유체의 흐름방향을 기준으로 튜브 결속구(101)는 다수의 행과 열로 배열되고, 다수의 튜브 결속구(101)가 형성하는 열 사이에 절단부(104)가 형성될 수 있다.In addition, the three-dimensional corrugated fin 100 according to the present embodiment, the tube binding holes 101 are arranged in a plurality of rows and columns based on the flow direction of the fluid, and between the columns formed by the plurality of tube binding holes 101. A cutout 104 may be formed at the.
이때, 절단부(104)와 인접하는 또 다른 절단부(105) 사이에는 짝수 개수의 파형이 형성됨이 바람직하다. 이 경우, 3차원 파형핀(100)을 제작할 수 있는 금형설계를 단순화 할 수 있다.In this case, an even number of waveforms may be formed between the cutout 104 and another adjacent cutout 105. In this case, it is possible to simplify the mold design to produce the three-dimensional corrugated pin 100.
따라서, 본 실시예에 따른 3차원 파형핀(100)은, 3차원 파형핀 제작에 있어서 금형설계를 단순화 할 수 있고, 이와 동시에 제작공정 역시 간소화 할 수 있어, 결과적으로 품질관리와 생산성에 크게 유리하며, 제작 비용을 현저히 절감시킬 수 있다.Therefore, the three-dimensional corrugated pin 100 according to the present embodiment can simplify the mold design in manufacturing the three-dimensional corrugated pin, and at the same time, the manufacturing process can be simplified, resulting in a great advantage in quality control and productivity. And the manufacturing cost can be significantly reduced.
또 다른 실시예에 따른 3차원 파형핀(100)의 경우, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부로부터 평면상 시계방향으로 130도 내지 160도 부분에 돌기(120)가 형성될 수 있다. 이때, 돌기(120)는, 튜브 결속구(101)의 반경(R) 대비 1.5 배 내지 1.7 배의 거리만큼 튜브 결속구(101)의 중심 위치로부터 이격된 위치에 형성됨이 바람직하다.In the case of the three-dimensional corrugated fin 100 according to another embodiment, the projection 120 may be formed at a portion 130 to 160 degrees clockwise in a planar direction from the tip of the tube which is perpendicular to the flow direction of the fluid. . At this time, the protrusion 120 is preferably formed at a position spaced apart from the center position of the tube binding port 101 by a distance 1.5 to 1.7 times the radius (R) of the tube binding port 101.
도 13 및 도 14와 함께 참조하면, 튜브를 감싸고 흐르는 유체는 튜브의 후단부 영역(a8 영역)에서 와류를 발생시킨다. 이때, a11 영역에 돌기(120)를 형성시키게 되면, 유체의 흐름을 튜브의 후단부 영역(a8 영역)으로 안내할 수 있다. 결과적으로, 튜브 후단부 영역(a8 영역)에서 발생되는 와류의 크기와 강도를 감소시킬 수 있으며, 와류의 감소에 따라서 압력강하의 저감과 열전달 촉진 효과를 달성할 수 있다.Referring to FIGS. 13 and 14, the fluid surrounding the tube generates a vortex in the rear end region (a8 region) of the tube. In this case, when the protrusion 120 is formed in the a11 region, the flow of the fluid may be guided to the rear end region (a8 region) of the tube. As a result, it is possible to reduce the size and strength of the vortices generated in the tube rear end region (a8 region), and to reduce the pressure drop and to promote heat transfer in accordance with the reduction of the vortices.
상기 언급한 돌기(120)는, 유체의 흐름을 효과적으로 안내할 수 있도록, 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %의 폭으로 형성됨이 바람직하다.The above-mentioned protrusion 120 is preferably formed to have a width of 20 to 30% of the radius R of the tube binding port 101 so as to effectively guide the flow of the fluid.
이와 같은 원리를 적용하여, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분(a1 영역)에서의 파형의 진폭은, 주변 부분의 파형의 진폭보다 작도록 할 수 있다. 이 경우 역시, 튜브의 선단부와 후단부에 생성될 수 있는 와류의 크기와 강도를 감소시킬 수 있다.By applying such a principle, the amplitude of the waveform in the portion (a1 region) adjacent to the tip of the tube which is perpendicular to the flow direction of the fluid can be made smaller than the amplitude of the waveform of the peripheral portion. In this case too, it is possible to reduce the size and strength of the vortices that can be produced at the leading and trailing ends of the tube.
도 15에는 본 발명의 또 다른 실시예에 따른 3차원 파형핀을 나타내는 사시도가 도시되어 있고, 도 16에는 도 15에 도시된 3차원 파형핀의 일부분을 나타내는 부분 확대도가 도시되어 있다. 또한, 도 17에는 도 16에 도시된 튜브 결속구와 딤플을 나타내는 평면도가 도시되어 있고, 도 18에는 도 17에 도시된 D1-D1선 절단면도가 도시되어 있다.FIG. 15 is a perspective view illustrating a three-dimensional corrugated pin according to another embodiment of the present invention, and FIG. 16 is a partially enlarged view illustrating a portion of the three-dimensional corrugated pin shown in FIG. 15. FIG. 17 is a plan view showing the tube fasteners and the dimples shown in FIG. 16, and FIG. 18 is a cross-sectional view taken along the line D1-D1 shown in FIG.
이들 도면을 참조하면, 본 실시예에 따른 3차원 파형핀(100)은, 딤플(dimple, 110)을 더 포함하는 구성일 수 있다.Referring to these drawings, the 3D waveform pin 100 according to the present embodiment may have a configuration further including a dimple 110.
앞서 설명한 바와 같이, 튜브의 선단부와 인접한 영역(a1 영역)과 튜브의 후단부와 인접한 영역(a8 영역)은, 유체의 유속이 낮고 열전달이 취약한 영역이다. 본 실시예에 따른 3차원 파형핀(100)은 이러한 열전달이 취약한 영역(a1, a8 영역)에 딤플(110)을 형성하고 있다.As described above, the region adjacent to the front end of the tube (a1 region) and the region adjacent to the rear end of the tube (a8 region) are regions of low fluid flow rate and poor heat transfer. The three-dimensional corrugated fin 100 according to the present embodiment forms the dimple 110 in an area (a1 and a8 area) where heat transfer is weak.
구체적으로, 본 실시예에 따른 딤플(110)은, 도 16 내지 도 17에 도시된 바와 같이, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분에 형성될 수 있다.Specifically, the dimple 110 according to the present embodiment, as shown in Figs. 16 to 17, the portion adjacent to the front end of the tube to be perpendicularly opposed to the flow direction of the fluid, and in a direction opposite to the front end 180 degrees It may be formed in a portion adjacent to the rear end of the tube located.
또한, 유속이 낮거나 핀 피치가 작은 경우에는, 유체의 난류 강도가 낮으므로, 딤플의 돌출방향을 달리하여 열전달 효율을 향상시킬 수 있다. 구체적으로, 도 16에 도시된 바와 같이, 튜브의 선단부와 인접하는 부분에 형성된 딤플(111)의 돌출방향은, 튜브의 후단부와 인접하는 부분에 형성된 딤플(112)의 돌출방향과 서로 정반대방향일 수 있다.In addition, when the flow velocity is low or the fin pitch is small, the turbulence intensity of the fluid is low, so that the heat transfer efficiency can be improved by changing the projecting direction of the dimple. Specifically, as shown in FIG. 16, the protruding direction of the dimple 111 formed at the portion adjacent to the front end of the tube is opposite to the protruding direction of the dimple 112 formed at the portion adjacent to the rear end of the tube. Can be.
이때 딤플(110)은 측단면상 타원형 구조이고, 타원형 구조의 장경은 유체의 흐름방향과 평행한 방향임이 바람직하다.At this time, the dimple 110 is an elliptical structure on the side cross-section, the long diameter of the elliptical structure is preferably a direction parallel to the flow direction of the fluid.
더욱 구체적으로, 딤플(110)의 형성 크기는 유체의 유속과 튜브 결속구(101)의 직경에 따라 다양하게 설계될 수 있다.More specifically, the size of the dimple 110 may be variously designed according to the flow rate of the fluid and the diameter of the tube binding port 101.
바람직하게 본 실시예에 따른 딤플(110)의 폭(Wdimple)은 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %이고, 딤플(110)의 길이(Ldimple)는 튜브 결속구(101)의 반경(R) 대비 21 내지 60 %일 수 있다. 또한, 딤플(110)의 형성 높이(Hdimple)는 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %일 수 있다.Width (W dimple) is the length (L dimple) of the radius (R) and by 20 to 30%, the dimple 110 of the tube coupling opening (101) of the dimples (110) according to the embodiment preferably present example is nine tubes bundled It may be 21 to 60% relative to the radius (R) of (101). In addition, forming height (H dimple) of the dimple 110 may be 20 to 30% of the radius (R) of the tube coupling opening (101).
또한, 튜브 하류의 딤플이 상류의 딤플보다 큰 크기로 형성함이 바람직하다. 구체적으로, 튜브의 후단부와 인접하는 부분에 형성된 딤플(112)의 크기는, 튜브의 선단부와 인접하는 부분에 형성된 딤플(111)의 크기 대비 1 내지 50 % 더 크게 할 수 있다.It is also desirable that the dimples downstream of the tube form a larger size than the dimples upstream. Specifically, the size of the dimples 112 formed at the portion adjacent to the rear end of the tube may be 1 to 50% larger than the size of the dimples 111 formed at the portion adjacent to the front end of the tube.
이러한 구성을 포함하는 본 실시예에 따른 3차원 파형핀(100)은, 유속이 낮고 열전달이 취약한 특정 위치에 딤플(dimple)을 형성시킴으로써, 국부적으로 유체의 혼합을 촉진하여 열전달 증대 효과를 달성할 수 있다.Three-dimensional corrugated fin 100 according to the present embodiment including such a configuration, by forming a dimple (dimple) at a specific position where the flow rate is low and heat transfer is weak, to locally promote the mixing of the fluid to achieve the heat transfer enhancement effect Can be.
도 19에는 본 발명의 일 실시예에 따른 3차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이 도시되어 있다.19 is a diagram illustrating an analysis of shear stress distribution generated when a fluid flows through a three-dimensional corrugated pin according to an embodiment of the present invention.
도 19에 도시된 3차원 파형핀은 딤플이 형성되어 있지 않은 경우에 대한 분석 그림이다.The three-dimensional waveform pin shown in FIG. 19 is an analysis diagram when the dimple is not formed.
도 4 및 도 19에서 확인할 수 있는 바와 같이, 튜브 후류에 생성되는 와류가 크기와 강도가 종래 기술 대비 현저히 저감된 것을 확인할 수 있다.As can be seen in Figures 4 and 19, it can be seen that the size and strength of the vortex generated in the wake of the tube is significantly reduced compared to the prior art.
또한, 일부 국소위치(hot spot)을 제외하고 마찰(shear stress)의 분포가 비교적 균일하며, 전체 핀 표면적을 골고루 활용함을 확인할 수 있다.In addition, the distribution of the shear stress is relatively uniform except for some hot spots, and the entire fin surface area is uniformly utilized.
도 20에는 본 발명의 또 다른 실시예에 따른 3차원 파형핀에 유체를 유동시킬 경우 발생되는 전단응력 분포를 분석하여 나타낸 그림이 도시되어 있다.20 is a diagram illustrating an analysis of the shear stress distribution generated when the fluid flows to the three-dimensional corrugated pin according to another embodiment of the present invention.
도 20에 도시된 3차원 파형핀은 딤플이 형성된 경우에 대한 분석 그림이다.The three-dimensional waveform pin shown in FIG. 20 is an analysis diagram for the case where the dimple is formed.
도 4 및 도 20에서 확인할 수 있는 바와 같이, 튜브 후류에 생성되는 와류가 크기와 강도가 종래 기술 대비 현저히 저감된 것을 확인할 수 있다.As can be seen in Figures 4 and 20, it can be seen that the size and strength of the vortex generated in the wake of the tube is significantly reduced compared to the prior art.
이상의 본 발명의 상세한 설명에서는 그에 따른 특별한 실시예에 대해서만 기술하였다. 하지만 본 발명은 상세한 설명에서 언급되는 특별한 형태로 한정되는 것이 아닌 것으로 이해되어야 하며, 오히려 첨부된 청구범위에 의해 정의되는 본 발명의 정신과 범위 내에 있는 모든 변형물과 균등물 및 대체물을 포함하는 것으로 이해되어야 한다.In the foregoing detailed description of the invention, only specific embodiments thereof have been described. It is to be understood, however, that the present invention is not limited to the specific forms referred to in the description, but rather includes all modifications, equivalents, and substitutions within the spirit and scope of the invention as defined by the appended claims. Should be.
즉, 본 발명은 상술한 특정의 실시예 및 설명에 한정되지 아니하며, 청구범위에서 청구하는 본 발명의 요지를 벗어남이 없이 본 발명이 속하는 기술 분야에서 통상의 지식을 가진 자라면 누구든지 다양한 변형 실시가 가능하며, 그와 같은 변형은 본 발명의 보호 범위 내에 있게 된다.That is, the present invention is not limited to the above specific embodiments and descriptions, and various modifications can be made by those skilled in the art without departing from the gist of the present invention as claimed in the claims. It is possible for such modifications to fall within the protection scope of the present invention.
이상에서 설명한 바와 같이, 본 발명의 3차원 파형핀에 따르면, 3차원 파형핀을 따라 흐르는 유체의 속도에 따라 파형의 구조를 서로 달리함으로써, 유체의 유효 열전달 길이를 증가하고 결과적으로 열전달 성능을 현저히 향상시킬 수 있다.As described above, according to the three-dimensional corrugated fin of the present invention, by varying the structure of the waveform according to the velocity of the fluid flowing along the three-dimensional corrugated fin, the effective heat transfer length of the fluid is increased and consequently the heat transfer performance is significantly increased. Can be improved.
또한, 본 발명의 3차원 파형핀에 따르면, 튜브 사이에 위치하는 부분에 형성된 파형을 특정 구조로 형성시킴으로써, 튜브를 기준으로 유체의 후류에서의 압력강하를 현저히 줄일 수 있고, 결과적으로 열전달 효과를 향상시킬 수 있다.In addition, according to the three-dimensional corrugated fin of the present invention, by forming a waveform formed in the portion located between the tube in a specific structure, it is possible to significantly reduce the pressure drop in the wake of the fluid relative to the tube, resulting in a heat transfer effect Can be improved.
또한, 본 발명의 3차원 파형핀에 따르면, 특정 위치에 돌기를 형성시킴으로써, 유체의 흐름을 튜브 후류로 손쉽게 안내할 수 있고, 튜브 후류에서 형성되는 와류의 크기와 강도를 감소시킬 수 있으며, 결과적으로 압력강하의 저감과 열전달 촉진 효과를 달성할 수 있다.In addition, according to the three-dimensional corrugation pin of the present invention, by forming a projection at a specific position, it is possible to easily guide the flow of fluid to the wake of the tube, reduce the size and strength of the vortex formed in the wake of the tube, resulting This can achieve the effect of reducing the pressure drop and promoting heat transfer.
또한, 본 발명의 3차원 파형핀에 따르면, 유속이 낮고 열전달이 취약한 특정 위치에 딤플(dimple)을 형성시킴으로써, 국부적으로 유체의 혼합을 촉진하여 열전달 증대 효과를 달성할 수 있다.In addition, according to the three-dimensional corrugated fin of the present invention, by forming a dimple at a specific position where the flow rate is low and the heat transfer is weak, it is possible to locally promote the mixing of the fluid to achieve a heat transfer increase effect.
또한, 본 발명의 3차원 파형핀에 따르면, 튜브 결속구의 중심을 지나고 유체의 흐름방향과 직교하는 방향의 가상 선을 기준으로 상류 부분과 하류부분이 선대칭구조를 구비함으로써, 3차원 파형핀 제작에 있어서 금형설계를 단순화 할 수 있고, 이와 동시에 제작공정 역시 간소화 할 수 있어, 결과적으로 품질관리와 생산성에 크게 유리하며, 제작 비용을 현저히 절감시킬 수 있다.Further, according to the three-dimensional corrugated fin of the present invention, the upstream portion and the downstream portion have a line symmetrical structure based on the imaginary line passing through the center of the tube binding sphere and orthogonal to the flow direction of the fluid, thereby producing a three-dimensional corrugated fin. Therefore, the mold design can be simplified, and at the same time, the manufacturing process can be simplified, and as a result, it is greatly advantageous for quality control and productivity, and can significantly reduce the manufacturing cost.
또한, 본 발명의 3차원 파형핀에 따르면, 다수의 튜브 결속구가 형성하는 열 사이에 절단부를 형성함으로써, 3차원 파형핀 제작에 있어서 금형설계를 단순화 할 수 있고, 이와 동시에 제작공정 역시 간소화 할 수 있어, 결과적으로 품질관리와 생산성에 크게 유리하며, 제작 비용을 현저히 절감시킬 수 있다.In addition, according to the three-dimensional corrugated fin of the present invention, by forming a cut between the rows formed by a plurality of tube binding spheres, it is possible to simplify the mold design in the production of three-dimensional corrugated fins, and at the same time to simplify the manufacturing process As a result, it is greatly advantageous for quality control and productivity, and can significantly reduce the production cost.
또한, 본 발명의 3차원 파형핀에 따르면, 절개부가 생략된 구조를 구비함으로써 절개부 비산에 따른 관련 장치 고장을 원천적으로 차단할 수 있는 파형핀 및 이를 포함하는 열교환기를 제공할 수 있으며, 절개부가 생략된 구조는 열교환기의 생산 설비, 금형 그리고 품질관리의 비용을 크게 절감할 수 있다.In addition, according to the three-dimensional corrugated fin of the present invention, by providing a structure in which the incision is omitted, it is possible to provide a corrugated fin and a heat exchanger including the same, which can fundamentally block the failure of the associated device due to scattering of the incision, the incision is omitted The structure can greatly reduce the cost of production equipment, mold and quality control of the heat exchanger.

Claims (20)

  1. 다수의 튜브 결속구(101)가 일정한 간격으로 엇갈림 배열을 갖도록 형성된 열교환기용 3차원 파형핀(100)으로서,As the three-dimensional corrugated fin 100 for the heat exchanger formed so that a plurality of tube binding holes 101 have a staggered arrangement at regular intervals,
    상기 3차원 파형핀(100)의 표면에는 다수의 파형(wave) 구조가 형성되어 있고,A plurality of wave structures are formed on the surface of the three-dimensional waveform pin 100,
    상기 파형 구조는, 튜브 결속구(101)의 중심을 지나고 유체의 흐름방향과 직교하는 방향의 가상 선(L1)을 기준으로 상류 부분와 하류 부분이 선대칭구조이며,The corrugated structure is a line symmetrical structure of the upstream and downstream portions based on the imaginary line L1 in the direction passing through the center of the tube binding port 101 and orthogonal to the flow direction of the fluid.
    상기 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 빠른 부분에서의 파형의 피치는, 인접하는 파형의 피치보다 긴 것을 특징으로 하는 3차원 파형핀(100).The pitch of the waveform in the portion where the speed of the fluid flowing along the three-dimensional waveform pin 100 is faster than the pitch of the adjacent waveform, characterized in that the three-dimensional waveform pin (100).
  2. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 빠른 부분은,The fast portion of the fluid flowing along the three-dimensional waveform pin 100,
    유체의 흐름방향과 직교하는 방향의 가상 선(L1) 상에 중심이 위치하는 서로 인접하는 두 개의 튜브 결속구(102, 103) 사이인 것을 특징으로 하는 3차원 파형핀.3D corrugated fins, characterized in that between two adjacent tube binding spheres (102, 103) centered on an imaginary line (L1) in a direction perpendicular to the flow direction of the fluid.
  3. 제 2 항에 있어서,The method of claim 2,
    상기 두 개의 튜브 결속구(102, 103) 사이에 있어서,Between the two tube engagement holes 102, 103,
    튜브 결속구(102, 103)와 인접하는 부분의 파형 진폭은, 튜브 결속구(102, 103) 사이의 정중앙 부분의 파형 진폭보다 큰 것을 특징으로 하는 3차원 파형핀.The waveform amplitude of the part adjacent to the tube binding port (102, 103) is larger than the waveform amplitude of the center part between the tube binding ports (102, 103).
  4. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 느린 부분에서의 파형의 진폭은 인접하는 파형의 진폭보다 큰 것을 특징으로 하는 3차원 파형핀.3D waveform pin, characterized in that the amplitude of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin 100 is larger than the amplitude of the adjacent waveform.
  5. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀을 따라 흐르는 유체의 속도가 느린 부분에서의 파형의 피치는 인접하는 파형의 피치보다 짧은 것을 특징으로 하는 3차원 파형핀.3D waveform pins, characterized in that the pitch of the waveform in the slow portion of the fluid flowing along the three-dimensional waveform pin is shorter than the pitch of the adjacent waveform.
  6. 제 4 항 또는 제 5 항에 있어서,The method according to claim 4 or 5,
    상기 3차원 파형핀(100)을 따라 흐르는 유체의 속도가 느린 부분은,The slow portion of the fluid flowing along the three-dimensional waveform pin 100,
    유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 상기 튜브의 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분인 것을 특징으로 하는 3차원 파형핀.And a portion adjacent to the front end of the tube facing perpendicular to the flow direction of the fluid, and a portion adjacent to the rear end of the tube located 180 degrees opposite to the front end of the tube.
  7. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)의 튜브 결속구(101)와 인접하는 부분에 있어서,In the portion adjacent to the tube binding hole 101 of the three-dimensional corrugated fin 100,
    튜브 결속구(101)의 직경 대비 101 % 내지 130 % 의 직경을 가지는 가상 원 내측 부분은 파형 구조가 형성되어 있지 않은 평평한 구조인 것을 특징으로 하는 3차원 파형핀.Three-dimensional corrugated fins, characterized in that the inner portion of the virtual circle having a diameter of 101% to 130% of the diameter of the tube binding port 101 is a flat structure is not formed.
  8. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분, 및 선단부와 180도 반대방향에 위치하는 튜브의 후단부와 인접하는 부분에, 딤플(dimple, 110)이 형성되어 있는 것을 특징으로 하는 3차원 파형핀.In the three-dimensional corrugated fin 100, a dimple (a portion adjacent to the front end portion of the tube which is perpendicularly opposed to the flow direction of the fluid and a portion adjacent to the rear end portion of the tube located 180 degrees opposite to the tip portion) 3d waveform pin, characterized in that the dimple, 110 is formed.
  9. 제 8 항에 있어서,The method of claim 8,
    상기 튜브의 선단부와 인접하는 부분에 형성된 딤플(111)의 돌출방향은, 튜브의 후단부와 인접하는 부분에 형성된 딤플(112)의 돌출방향과 서로 정반대방향인 것을 특징으로 하는 3차원 파형핀.Protruding direction of the dimple (111) formed in the portion adjacent to the front end of the tube, the three-dimensional corrugated pin, characterized in that the opposite direction to the protruding direction of the dimple (112) formed in the portion adjacent to the rear end of the tube.
  10. 제 8 항에 있어서,The method of claim 8,
    상기 튜브의 후단부와 인접하는 부분에 형성된 딤플(112)의 크기는, 튜브의 선단부와 인접하는 부분에 형성된 딤플(111)의 크기 대비 1 내지 50 % 더 큰 것을 특징으로 하는 3차원 파형핀.The size of the dimple (112) formed in the portion adjacent to the rear end of the tube, characterized in that 1 to 50% larger than the size of the dimple (111) formed in the portion adjacent to the front end of the tube.
  11. 제 8 항에 있어서,The method of claim 8,
    상기 딤플(110)은 측단면상 타원형 구조이고,The dimple 110 is an elliptical structure in the side cross section,
    상기 타원형 구조의 장경은 유체의 흐름방향과 평행한 방향인 것을 특징으로 하는 3차원 파형핀.The long diameter of the elliptical structure is a three-dimensional waveform pin, characterized in that the direction parallel to the flow direction of the fluid.
  12. 제 11 항에 있어서,The method of claim 11,
    상기 딤플(110)의 폭(Wdimple)은, 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %이고,Width (W dimple) of the dimple 110, the tube radius (R) compared to 20 to 30% of the binding opening (101), and
    상기 딤플(110)의 길이(Ldimple)는, 튜브 결속구(101)의 반경(R) 대비 21 내지 60 %이고,Length (L dimple) of said dimples (110), the radius (R) compared to 21 to 60% of the tube coupling opening (101), and
    상기 딤플(110)의 형성 높이(Hdimple)는, 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %인 것을 특징으로 하는 3차원 파형핀.The forming height (H dimple) of the dimple 110, the tube coupling opening (101) radius (R) compared to 20 to 30% of that pin 3d waveform, characterized in.
  13. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부로부터 평면상 시계방향으로 130도 내지 160도 부분에는, 돌기(120)가 형성되어 있는 것을 특징으로 하는 3차원 파형핀.In the three-dimensional corrugated fin 100, the projection 120 is formed in the 130 degrees to 160 degrees in the clockwise direction from the tip of the tube to be perpendicular to the flow direction of the fluid 3 Dimensional waveform pins.
  14. 제 13 항에 있어서,The method of claim 13,
    상기 돌기(120)는, 튜브 결속구(101)의 반경(R) 대비 1.5 배 내지 1.7 배의 거리만큼 튜브 결속구(101)의 중심 위치로부터 이격된 위치에 형성되어 있는 것을 특징으로 하는 3차원 파형핀.The projection 120 is a three-dimensional, characterized in that formed in a position spaced apart from the center position of the tube binding port 101 by a distance 1.5 to 1.7 times the radius (R) of the tube binding port 101 Waveform pin.
  15. 제 13 항에 있어서,The method of claim 13,
    상기 돌기(120)는 튜브 결속구(101)의 반경(R) 대비 20 내지 30 %의 폭으로 형성되어 있는 것을 특징으로 하는 3차원 파형핀.The protrusion 120 is a three-dimensional corrugated pin, characterized in that formed in a width of 20 to 30% of the radius (R) of the tube binding port 101.
  16. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)에 있어서, 유체의 흐름 방향과 수직으로 맞부딪히는 튜브의 선단부와 인접하는 부분에서의 파형의 진폭은, 주변 부분의 파형의 진폭보다 작은 것을 특징으로 하는 3차원 파형핀.In the three-dimensional corrugated fin 100, the amplitude of the waveform in the portion adjacent to the tip of the tube, which is perpendicular to the flow direction of the fluid, is smaller than the amplitude of the waveform of the peripheral portion .
  17. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)은,The three-dimensional waveform pin 100,
    인접하여 배치된 파형핀(100)을 소정 거리만큼 이격되도록 고정시키는 파형핀 연결부(130)를 더 포함하고,Further comprising a waveform pin connecting portion 130 for fixing the adjacent pins 100 arranged to be spaced apart by a predetermined distance,
    상기 파형핀 연결부(130)에 튜브 결속구(101)가 형성되어 있는 것을 특징으로 하는 3차원 파형핀.Three-dimensional corrugated fins, characterized in that the tube binding hole 101 is formed in the corrugated pin connecting portion 130.
  18. 제 1 항에 있어서,The method of claim 1,
    상기 3차원 파형핀(100)의 유체의 흐름방향을 기준으로 튜브 결속구(101)는 다수의 행과 열로 배열되고,The tube binding holes 101 are arranged in a plurality of rows and columns based on the flow direction of the fluid of the three-dimensional corrugated fin 100.
    다수의 튜브 결속구(101)가 형성하는 열 사이에 절단부(104)가 형성되어 있는 것을 특징으로 하는 3차원 파형핀.Three-dimensional corrugated fins, characterized in that the cut portion 104 is formed between the rows formed by a plurality of tube binding holes (101).
  19. 제 18 항에 있어서,The method of claim 18,
    상기 절단부(104)와 인접하는 또 다른 절단부(105) 사이에는 짝수 개수의 파형이 형성되어 있는 것을 특징으로 하는 3차원 파형핀.Three-dimensional corrugated pin, characterized in that an even number of waveforms are formed between the cut portion 104 and another adjacent cut portion 105.
  20. 제 1 항 내지 제 19 항 중 어느 한 항에 따른 3차원 파형핀(100)을 포함하는 것을 특징으로 하는 열교환기.20. A heat exchanger comprising a three-dimensional corrugated fin (100) according to any one of the preceding claims.
PCT/KR2016/005765 2016-05-31 2016-05-31 Three-dimensional wave-shaped fin and heat exchanger comprising same WO2017209323A1 (en)

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CN110207529B (en) * 2019-05-24 2020-03-31 西安交通大学 High-strength heat exchange fin adopting variable-height continuous protrusions

Citations (5)

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Publication number Priority date Publication date Assignee Title
US6221463B1 (en) * 1998-07-08 2001-04-24 Eugene W. White Three-dimensional film structures and methods
JP3367353B2 (en) * 1996-11-12 2003-01-14 松下電器産業株式会社 Finned heat exchanger
JP2004036938A (en) * 2002-07-01 2004-02-05 Matsushita Electric Ind Co Ltd Heat exchanger and air conditioner comprising the same
US20090199585A1 (en) * 2006-03-23 2009-08-13 Matsushita Electric Industrial Co., Ltd. Fin-tube heat exchanger, fin for heat exchanger, and heat pump apparatus
KR20150074749A (en) * 2013-12-24 2015-07-02 엘지전자 주식회사 Heat Exchanger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3367353B2 (en) * 1996-11-12 2003-01-14 松下電器産業株式会社 Finned heat exchanger
US6221463B1 (en) * 1998-07-08 2001-04-24 Eugene W. White Three-dimensional film structures and methods
JP2004036938A (en) * 2002-07-01 2004-02-05 Matsushita Electric Ind Co Ltd Heat exchanger and air conditioner comprising the same
US20090199585A1 (en) * 2006-03-23 2009-08-13 Matsushita Electric Industrial Co., Ltd. Fin-tube heat exchanger, fin for heat exchanger, and heat pump apparatus
KR20150074749A (en) * 2013-12-24 2015-07-02 엘지전자 주식회사 Heat Exchanger

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