CN111412780B - Tube fins, heat exchangers, air conditioners - Google Patents
Tube fins, heat exchangers, air conditioners Download PDFInfo
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- CN111412780B CN111412780B CN202010210072.4A CN202010210072A CN111412780B CN 111412780 B CN111412780 B CN 111412780B CN 202010210072 A CN202010210072 A CN 202010210072A CN 111412780 B CN111412780 B CN 111412780B
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- fin
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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
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/10—Secondary fins, e.g. projections or recesses on main fins
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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
本发明提供一种管翅翅片、换热器、空调器。其中一种管翅翅片，包括翅片本体，所述翅片本体的一侧具有多个球突，所述球突的顶部具有第一凹槽，所述第一凹槽由所述翅片本体的一侧朝向所述翅片本体的另一侧延伸。根据本发明的一种管翅翅片、换热器、空调器，在对气流流体形成纵向涡提高传热系数的同时，提高对流经球突顶部附件气流的扰动，减小气流流体的流动边界层厚度，提高换热器的换热性能。
The present invention provides a tube-fin fin, a heat exchanger, and an air conditioner. One of the tube-fin fins includes a fin body, one side of the fin body has a plurality of spherical protrusions, the top of the spherical protrusions has a first groove, and the first groove extends from one side of the fin body toward the other side of the fin body. According to the tube-fin fin, heat exchanger, and air conditioner of the present invention, while forming a longitudinal vortex on the airflow fluid to improve the heat transfer coefficient, the disturbance of the airflow passing through the top of the spherical protrusion is improved, the flow boundary layer thickness of the airflow fluid is reduced, and the heat exchange performance of the heat exchanger is improved.
Description
Technical Field
The invention belongs to the technical field of heat exchanger manufacturing, and particularly relates to a tube fin, a heat exchanger and an air conditioner.
Background
Reducing air side thermal resistance and pressure drop losses is a necessary approach to improving overall heat exchanger performance, and the structural form of the fins is a major factor affecting air side thermal resistance and pressure drop losses. The existing fin structure has the forms of windowing, slotting, corrugation, adding a longitudinal vortex generator on the fin and the like, and aims to reduce the heat resistance and pressure drop loss of the air side of the heat exchanger and improve the comprehensive performance of the heat exchanger. For example, in order to enhance the heat exchange efficiency between the air flow and the fins, a spherical protrusion (for short, a knob) protruding towards one side of the fins is disclosed in the prior art, the surface of the knob is smooth, when the air flow passes through the vicinity of the surface of the knob, the vortex in the flow field can be sucked away by the pit on the back of the knob, so that larger vortex formation can be prevented, and the air flow resistance can be reduced, but the inventor finds that the surface of the protrusion side of the knob is smooth and easily forms a thicker laminar flow bottom layer (laminar boundary layer) to cause poor disturbance to the air flow, and the structure is unfavorable for improving the heat transfer efficiency on one side of the protrusion.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to provide a tube fin, a heat exchanger and an air conditioner, which can form longitudinal vortex on airflow fluid to improve heat transfer coefficient, improve disturbance on airflow passing through the accessory at the top of the knob, reduce thickness of a flowing boundary layer of the airflow fluid and improve heat exchange performance of the heat exchanger.
In order to solve the problems, the invention provides a tube fin which comprises a fin body, wherein one side of the fin body is provided with a plurality of spherical protrusions, the tops of the spherical protrusions are provided with first grooves, and the first grooves extend from one side of the fin body towards the other side of the fin body.
Preferably, the first groove has a first symmetry axis and a second symmetry axis, and the first symmetry axis is perpendicular to the second symmetry axis.
Preferably, the first groove is rectangular, the length of the rectangle is L, the width of the rectangle is W, the groove depth of the first groove is H, l=1.7w, and/or l=1.7h.
Preferably, the plurality of the knobs are formed by N knob combination units, and the N knob combination units are uniformly distributed on one side of the fin body.
Preferably, the lobe combination unit at least comprises a first lobe row, a second lobe row and a third lobe row, the first lobe row, the second lobe row and the third lobe row are arranged in parallel at intervals, the center distance between any two adjacent lobes in the second lobe row is d2, and the center distance between any two adjacent lobes in the first lobe row and the center distance between any two adjacent lobes in the third lobe row are d3,1< d3/d2<2.
Preferably, the center distance between the first and second and third bulb rows is d1, the fin body further comprises a tube hole, the center distance between the bulb and the tube hole is p, and the dimension of the bulb combination unit in the direction parallel to the direction indicated by d1 is defined as a width m, p/4< d1< (p+m)/4.
Preferably, a first flow guiding structure is arranged on the periphery of the pipe hole, the first flow guiding structure comprises a first circular arc runner, a second circular arc runner and a third circular arc runner which are sequentially connected end to end, the first circular arc runner and the second circular arc runner are externally tangent at the connecting position, and the second circular arc runner and the third circular arc runner are externally tangent at the connecting position.
Preferably, the arc radius of the first arc runner is R1, the arc radius of the second arc runner is R2, the arc radius of the third arc runner is R3, R1=R3, and 3 is more than or equal to R1/R2 is more than or equal to 2.5.
Preferably, a second flow guiding structure is further arranged on the hole periphery side of the pipe hole, the structure of the second flow guiding structure is identical to that of the first flow guiding structure, any axis which passes through the hole center of the pipe hole and is parallel to the airflow flowing direction is defined as a third symmetrical axis, the second flow guiding structure and the first flow guiding structure are symmetrical about the third symmetrical axis, a first circular arc runner in the first flow guiding structure is communicated with a first circular arc runner in the second flow guiding structure, a third circular arc runner in the first flow guiding structure is communicated with a third circular arc runner in the second flow guiding structure, and the first flow guiding structure and the second flow guiding structure form an enveloping for the pipe hole.
Preferably, the length direction of the first groove, the arrangement direction of the first knob rows and the airflow flowing direction are parallel to each other.
Preferably, the plurality of tube holes are arranged at intervals in the airflow flowing direction, the plurality of first flow guiding structures are arranged continuously along the airflow flowing direction, and the plurality of second flow guiding structures are arranged continuously along the airflow flowing direction.
The invention also provides a heat exchanger comprising the tube fin.
The invention also provides an air conditioner comprising the heat exchanger.
According to the tube fin, the heat exchanger and the air conditioner provided by the invention, as the first groove is formed in the top of the spherical protrusion, when air flows through the top area of the spherical protrusion, the structure of the first groove can disturb the air flow, so that the thickness of a flowing boundary layer of the air flow fluid is reduced, the heat exchange performance of the heat exchanger is improved, and meanwhile, the spherical protrusion can form a longitudinal vortex (namely, a vortex taking the flowing direction of the air flow as a rotating shaft and flowing along the flowing direction of the air flow) on the air flow fluid, so that the heat transfer coefficient, namely the heat transfer performance of the tube fin, is improved, and meanwhile, the phenomenon of larger resistance caused by the transverse direction of the air flow is prevented.
Drawings
FIG. 1 is a schematic view of a tube fin according to an embodiment of the present invention;
FIG. 2 is a schematic view of a partial cross-sectional structure of the knob of FIG. 1;
FIG. 3 is an enlarged view of a portion of FIG. 1 at A;
FIG. 4 is a graph showing the Nu-Re variation relationship between a windowed fin and a tube fin according to the prior art;
FIG. 5 is a graph of the f-Re variation of a windowed fin of the prior art versus a tube fin of the invention;
FIG. 6 is a graph of airflow velocity cloud modeling results for a fenestration fin of the prior art;
FIG. 7 is a graph of airflow velocity cloud simulation results for a tube fin in accordance with the present invention;
FIG. 8 is a simulation result of airflow streamline of a tube fin in the present invention.
The reference numerals are expressed as:
1. The fin comprises a fin body, 11, a knob, 12, a first groove, 13, a knob combination unit, 14, a pipe hole, 15, a first flow guiding structure, 151, a first circular arc runner, 152, a second circular arc runner, 153, a third circular arc runner, 16, a second flow guiding structure, 17 and a second groove.
Detailed Description
Referring to fig. 1 to 8 in combination, according to an embodiment of the present invention, there is provided a tube fin including a fin body 1, one side of the fin body 1 having a plurality of knobs 11, a top of the knobs 11 having a first groove 12, the first groove 12 extending from one side of the fin body 1 toward the other side of the fin body 1. In this technical scheme, because the top of the knob 11 has provided the first recess 12, when the air current flows through the top region of the knob 11, the structure of the first recess 12 can be used for disturbing the air current, thereby being favorable to reducing the thickness of the flowing boundary layer of the air current fluid and improving the heat exchange performance of the heat exchanger, meanwhile, the arrangement of the knob 11 can form a longitudinal vortex (that is, a vortex taking the air current flowing direction as a rotation axis and flowing along the air current flowing direction) on the air current fluid, thereby improving the heat transfer coefficient, that is, improving the heat transfer performance of the tube fin, and simultaneously preventing the occurrence of a phenomenon of larger resistance caused by the transverse formation of the air current. Further, a second groove 17 is provided on a side of the knob 11 opposite to the first groove 12, and the second groove 17 extends from the other side of the fin body 1 toward the one side of the fin body 1. At this time, the second grooves 17 can form disturbance to the air flow on the other side of the fin body 1, which is beneficial to reducing the thickness of the flowing boundary layer of the air flow on the other side and improving the comprehensive heat exchange performance of the heat exchanger.
Preferably, the first groove 12 has a first symmetry axis and a second symmetry axis, and the first symmetry axis is perpendicular to the second symmetry axis, that is, the first groove 12 is preferably a groove structure with a regular shape, such as a circle, a square, a rectangle, an ellipse, etc., which is convenient for processing and manufacturing the first groove 12 on one hand, and is beneficial for arranging and guiding the flow direction of the heat exchange air flow on the other hand. As a specific embodiment, for example, the first groove 12 is rectangular, the length of the rectangle is L, the width of the rectangle is W, the groove depth of the first groove 12 is H, l=1.7w, and/or l=1.7h, and in this case, the length direction of the rectangle is parallel to the flow direction (i.e., the incoming flow direction) of the air flow, so that the air flow can be guided. More specifically, the broad sides of the first groove 12 are respectively located at the inflow side and the outflow side of the air flow, the air flow flows into the first groove 12 from the inflow side and flows out of the first groove 12 from the outflow side, and the air flow forms a longitudinal vortex around the first symmetry axis (the axis parallel to the long side) during the inflow and outflow process in the first groove 12, so that the air flow is disturbed, the thickness of the flowing boundary layer of the air flow fluid is reduced, and the heat exchange performance of the heat exchanger is improved. More preferably, the wide side of the rectangle is arc-shaped, thereby improving the rectangle into the shape of an annular runway.
The heat exchange performance of the tube fin is directly related to the layout form of the plurality of the spherical protrusions 11 on the fin body 1, preferably, the plurality of the spherical protrusions 11 are formed by N spherical protrusion combination units 13, N (N is an integer not less than 2) spherical protrusion combination units 13 are uniformly distributed on one side of the fin body 1, namely, the invention tries to limit the arrangement form of each spherical protrusion 11 on the fin body 1 and periodically arrange the spherical protrusion combination units 13 on the fin body 1.
Specifically, the protrusion combination unit 13 includes at least a first protrusion row, a second protrusion row, and a third protrusion row, and it can be understood that a plurality of protrusions 11 are respectively disposed in the first protrusion row, the second protrusion row, and the third protrusion row, as shown in fig. 1, one protrusion combination unit 13 is framed by a dash-dot line in the drawing, and in the fin body shown in fig. 1, 4 protrusion combination units 13 are disposed thereon, the first protrusion row, the second protrusion row, and the third protrusion row are disposed in parallel and spaced apart from each other, the center distance between any two adjacent protrusions 11 in the second protrusion row is d2, and the center distance between any two adjacent protrusions 11 in the first protrusion row and the center distance between any two adjacent protrusions 11 in the third protrusion row is d3,1< d3/d 2. In the technical scheme, the correlation of d2 and d3 is limited, so that the protrusions in the first protrusion row and the protrusions in the second protrusion row are staggered, and the protrusions in the third protrusion row and the protrusions in the second protrusion row are also staggered, so that the protrusions (d 3) close to the pipe hole are separated from the protrusions (d 2) in the middle row, and the resistance close to the pipe hole can be reduced.
Preferably, the center distance between the first lobe row and the second lobe row, and the center distance between the second lobe row and the third lobe row are d1, the fin body 1 further includes a tube hole 14, the center distance between two adjacent tube holes 14 is p, the dimension of the lobe combination unit 13 in the direction parallel to the direction indicated by d3 is defined as a width m, p/4< d1< (p+m)/4, so that d1 can be ensured to be wide enough, thereby reducing the flow resistance, and limiting that it is not too wide, and further preventing the occurrence of the phenomenon that the lobe close to the tube hole 14 is difficult to process.
Preferably, a first flow guiding structure 15 is disposed on the hole periphery side of the pipe hole 14, the first flow guiding structure 15 includes a first circular arc runner 151, a second circular arc runner 152, and a third circular arc runner 153 that are sequentially connected end to end, the first circular arc runner 151 and the second circular arc runner 152 are tangent at the outside of the junction, and the second circular arc runner 152 and the third circular arc runner 153 are tangent at the outside of the junction. The second circular arc runner 152 in the first flow guiding structure 15 is respectively connected with the first circular arc runner 151 and the third circular arc runner 153 in an externally tangent manner, so that the runners of the first flow guiding structure 15 are smooth curves, no sharp corner structure exists in the runners, and the airflow can be guided to cling to the outer wall of the runner (i.e. away from the side wall of the runner of the pipe hole 14), as can be seen from an airflow streamline simulation diagram in fig. 8, the density of the cling wall streamline of the outer wall is far greater than that of the inner wall streamline, the tail fluid detachment phenomenon of a circular pipe (i.e. a circular copper pipe or a circular aluminum pipe passing through the pipe hole 14) is greatly reduced, so that the pressure drop loss around the pipe hole is reduced, and no sharp corner structure exists in the airflow runner, so that the noise of the airflow is small.
Further, the radius of the first arc runner 151 is R1, the radius of the second arc runner 152 is R2, the radius of the third arc runner 153 is R3, and r1=r3, so that the first arc runner 151 and the third arc runner 153 are symmetrical about a radial axis of the through hole 14, and 3 is greater than or equal to R1/R2 and greater than or equal to 2.5, thereby ensuring that the air flow can flow close to the flow guiding structure.
Preferably, a second flow guiding structure 16 is further disposed on the hole periphery side of the hole 14, the second flow guiding structure 16 is identical to the first flow guiding structure 15 in structure, any axis passing through the hole center of the hole 14 and parallel to the airflow flowing direction is defined as a third symmetry axis, the second flow guiding structure 16 and the first flow guiding structure 15 are symmetrical with respect to the third symmetry axis, a first circular arc runner 151 in the first flow guiding structure 15 is communicated with a first circular arc runner 151 in the second flow guiding structure 16, a third circular arc runner 153 in the first flow guiding structure 15 is communicated with a third circular arc runner 153 in the second flow guiding structure 16, and the first flow guiding structure 15 and the second flow guiding structure 16 form an envelope on the hole 14. It can be understood that the second flow guiding structure 16 also includes a first circular arc flow channel 151, a second circular arc flow channel 152, and a third circular arc flow channel 153 that are sequentially connected end to end, the tube hole 14 is provided with a plurality of first flow guiding structures 15 continuously along the airflow direction, and a plurality of second flow guiding structures 16 continuously along the airflow direction, so that the first flow guiding structures 15 and the second flow guiding structures 16 form a structure symmetrical about the third symmetry axis, and the first flow guiding structures 15 and the second flow guiding structures 16 may include a plurality of groups of first circular arc flow channels 151, second circular arc flow channels 152, and third circular arc flow channels 153 periodically recurring along the airflow direction, so that a wavy flow guiding structure is formed at two sides of the tube hole 14, which can guide the air flow to smoothly flow along the inner wall of the structure, greatly reduce the tail fluid detachment phenomenon, and reduce the pressure drop loss around the tube hole.
Preferably, the length direction of the first groove 12, the arrangement direction of the first bead rows, and the airflow flowing direction are parallel to each other, so that the first groove 12 and the first bead rows are beneficial to the generation of longitudinal vortices, thereby effectively reducing the thickness of a laminar boundary layer, improving the heat transfer coefficient and efficiency, optimizing the effect, reducing the occurrence of transverse vortices as much as possible, and ensuring the reduction of the thickness of the laminar boundary layer, the heat transfer coefficient and efficiency and reducing the atmospheric airflow resistance of the transverse vortices.
In order to further verify the comprehensive heat exchange effect of the tube-fin designed by the invention, the inventor performs a comparison test (including simulation) on the windowed fin in the prior art and the tube-fin of the invention:
The theoretical basis is:
The Reynolds number Re formula is:
The formula of the noose number Re is:
the drag factor f is given by:
In the above formulas, ρ is density, D is characteristic dimension, μ is dynamic viscosity of fluid, U is average flow velocity at minimum section, ac minimum flow area, A 0 total heat exchange area, λ is heat conductivity coefficient, ΔP is inlet-outlet air flow pressure difference, h is convective heat transfer coefficient, and each physical parameter is measured in international standard unit.
(1) Fin heat transfer performance comparative test
The test is obtained by obtaining the Reynolds number Re and the Nu of the Nu and Re of the test object (the windowing fins and the tube fin fins of the invention) and fitting the change relation between the Nu and Re, and the result is shown in figure 4. As can be seen from figure 4, in the range of 500-2500 Re, nu corresponding to the tube fin fins of the invention is larger than that of the windowing fins in the prior art (20% better than that of the existing windowing fins on average), which indicates that the tube fin fins of the invention have good heat transfer performance.
(2) Pressure loss test of air flow
The test is obtained by obtaining the Reynolds number Re and the resistance factor f of a test object (the windowing fin and the tube fin of the invention) and fitting the change relation between f and Re, and the result is shown in figure 5. As can be seen from figure 5, the resistance factors f corresponding to the tube fin of the invention are smaller than those of the windowing fin in the prior art when Re is in the range of 500-2500, which indicates that the tube fin of the invention has small resistance and smaller pressure drop loss (40% smaller than that of the prior windowing fin on average).
(3) Fin heat transfer comprehensive performance simulation test
Fig. 6 is a simulation result of airflow velocity cloud of a windowed fin in the prior art, and fig. 7 is a simulation result of airflow velocity cloud of a tube fin in the present invention, it can be seen that by designing a relief flow guiding structure around the tube hole 14, the swirl area around the tube hole (the framed parts in fig. 6 and 7) is greatly reduced, and the resistance loss is also correspondingly reduced.
According to an embodiment of the present invention, there is also provided a heat exchanger including the above tube fin.
According to an embodiment of the present invention, there is also provided an air conditioner including the above heat exchanger.
It will be readily appreciated by those skilled in the art that the above advantageous ways can be freely combined and superimposed without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention. The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (10)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202010210072.4A CN111412780B (en) | 2020-03-23 | 2020-03-23 | Tube fins, heat exchangers, air conditioners |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010210072.4A CN111412780B (en) | 2020-03-23 | 2020-03-23 | Tube fins, heat exchangers, air conditioners |
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| CN111412780A CN111412780A (en) | 2020-07-14 |
| CN111412780B true CN111412780B (en) | 2025-05-30 |
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Families Citing this family (1)
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| CN111829366A (en) * | 2020-08-17 | 2020-10-27 | 珠海格力电器股份有限公司 | Heat Exchangers and Air Conditioning Units |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011096124A1 (en) * | 2010-02-08 | 2011-08-11 | 住友軽金属工業株式会社 | Fin and tube heat exchanger |
| CN212006886U (en) * | 2020-03-23 | 2020-11-24 | 珠海格力电器股份有限公司 | Tube fin, heat exchanger and air conditioner |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08170889A (en) * | 1994-12-16 | 1996-07-02 | Daikin Ind Ltd | Cross fin heat exchanger |
| JP2001174181A (en) * | 1999-10-06 | 2001-06-29 | Mitsubishi Heavy Ind Ltd | Fin-and-tube heat exchanger and air conditioner equipped with the same |
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2020
- 2020-03-23 CN CN202010210072.4A patent/CN111412780B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011096124A1 (en) * | 2010-02-08 | 2011-08-11 | 住友軽金属工業株式会社 | Fin and tube heat exchanger |
| CN212006886U (en) * | 2020-03-23 | 2020-11-24 | 珠海格力电器股份有限公司 | Tube fin, heat exchanger and air conditioner |
Non-Patent Citations (1)
| Title |
|---|
| 矩形通道内流动与强化传热的实验与数值研究;唐新宜;《中国博士学位论文全文数据库 工程技术第Ⅱ辑》;20121115(第11期);第95-105页，图5-3 * |
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