WO2021258775A1 - 翅片结构及换热器 - Google Patents

翅片结构及换热器 Download PDF

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Publication number
WO2021258775A1
WO2021258775A1 PCT/CN2021/079352 CN2021079352W WO2021258775A1 WO 2021258775 A1 WO2021258775 A1 WO 2021258775A1 CN 2021079352 W CN2021079352 W CN 2021079352W WO 2021258775 A1 WO2021258775 A1 WO 2021258775A1
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WIPO (PCT)
Prior art keywords
fin
corrugated
structure according
fin structure
annular groove
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PCT/CN2021/079352
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English (en)
French (fr)
Inventor
向武
马屈杨
玉格
夏凯
林伟雪
张仕强
Original Assignee
珠海格力电器股份有限公司
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Application filed by 珠海格力电器股份有限公司 filed Critical 珠海格力电器股份有限公司
Priority to JP2022552526A priority Critical patent/JP2023530804A/ja
Priority to EP21827997.4A priority patent/EP4102169A4/en
Priority to US17/910,597 priority patent/US20230136711A1/en
Publication of WO2021258775A1 publication Critical patent/WO2021258775A1/zh

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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
    • 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

Definitions

  • This application relates to the technical field of refrigeration equipment, and specifically to a fin structure and a heat exchanger.
  • finned tube heat exchangers are widely used in chemical, ventilation, heating, air conditioning and refrigeration industries due to their simple manufacturing and strong applicability. How to maximize heat transfer and use heat energy (enhanced heat transfer) ) Has always been the focus of research in the industry.
  • the fin structure of the finned tube heat exchanger mainly includes straight fins, corrugated fins, and corresponding slit (window) structures.
  • the traditional straight fins and corrugated fins are often replaced on the lee side of the heat exchange tube.
  • the heat is not good, and the corresponding slit structure increases the contact area on the air side.
  • the irregularity of the structure disturbs the flow field, which enhances the mixing of fluids, delays the flow separation of the boundary layer, and strengthens the overall exchange. Thermal performance.
  • the slit structure usually reduces the flow gap of the fin and increases the flow resistance.
  • corrugated fins are a more suitable form for industrial applications.
  • the traditional corrugated fins are difficult to meet the performance requirements of high-efficiency heat exchangers.
  • the embodiments of the present application provide a fin structure and a heat exchanger to improve the heat exchange effect of the fin and enhance the heat exchange performance of the heat exchanger.
  • the present application provides a fin structure, including: a fin base body, the fin base body has a tube hole structure for piercing heat exchange tubes, the fin base body is a corrugated fin; and a plurality of protrusions The raised part, the raised part is arranged on the fin base, and a plurality of raised parts surround the outer circumference of the tube hole structure.
  • the fin base includes a plurality of first corrugated surfaces and a plurality of second corrugated surfaces, a second corrugated surface is connected between the two first corrugated surfaces, and the corresponding node length L1 of the first corrugated surface is greater than that of the second corrugated surface.
  • the surface corresponds to the node length L2.
  • the ratio h1/S of the corrugation height h1 of the fin base to the fin pitch S is 0.58-0.62, and L1/L2 is 1.5-1.7.
  • the plurality of protrusions includes: a ring protrusion, which is protrudingly arranged on the first corrugated surface; and a side protrusion, which is protrudingly arranged on the second corrugated surface.
  • the ring convex portion is an annular convex structure, the number of the ring convex portion is multiple, and the multiple ring convex portions are symmetrically distributed on the outer circumference of the tube hole structure.
  • the side protrusions have a boss structure, the number of side protrusions is multiple, and the plurality of side protrusions are symmetrically distributed on the outer circumference of the tube hole structure.
  • the ratio h3/S of the protrusion height h3 of the annular protrusion to the fin spacing S is 0.35 to 0.4.
  • the ratio h2/S of the protrusion height h2 of the side protrusion to the fin pitch S is 0.35 to 0.4.
  • the fin base is also provided with an annular groove
  • the tube hole structure is located in the annular groove
  • the annular groove and the tube hole structure are arranged concentrically
  • the outer circumference of the annular groove is opposite to the first corrugated surface and the second corrugated surface. Then, the protrusions are all located outside the annular groove.
  • the two second corrugated surfaces there are two second corrugated surfaces between the two first corrugated surfaces, the two second corrugated surfaces are arranged adjacently, and the two second corrugated surfaces intersect to form a trough line; the annular groove and the two first corrugated surfaces Two arc-shaped surfaces symmetrical with respect to the pipe hole structure are formed at the junction, and four planes symmetrical with respect to the pipe hole structure are formed at the junction of the annular groove and the two second corrugated surfaces.
  • the groove bottom of the annular groove is tangent to the trough line in the vertical incoming flow direction; the angle ⁇ between the generatrix of the arc-shaped surface and the central axis of the heat exchange tube is 45°.
  • the ratio d1/D of the bottom diameter d1 of the annular groove to the outer diameter D of the heat exchange tube is 1.6 to 1.7.
  • first corrugated surfaces are arranged symmetrically with respect to the tube hole structure
  • second corrugated surfaces are arranged symmetrically with respect to the tube hole structure.
  • the ratio D1/D of the inner diameter D1 of the tube hole structure to the outer diameter D of the heat exchange tube is 1.025 to 1.035.
  • a heat exchanger including the above-mentioned fin structure.
  • This application improves the structure of the corrugated fin.
  • the function of the protrusions can strengthen the airflow disturbance near the tube hole structure (installed heat exchanger), and make the local area
  • the increase in the flow rate of the heat exchanger enhances the mixing of hot and cold fluids and increases the effective heat exchange area of the fins, thereby enhancing the heat exchange performance of the heat exchanger.
  • the fin structure of the present application is less prone to frost on the surface of the fin under wet conditions, and can effectively reduce the occurrence of flow channel blockage.
  • the fin structure of the present application can effectively increase the heat exchange area and further improve the heat exchange effect.
  • Figure 1 is a schematic plan view of the fin structure of an embodiment of the present application.
  • FIG. 2 is a schematic diagram of the three-dimensional structure of the fin structure of the embodiment of the present application.
  • Figure 3 is an A-A sectional view of the fin structure of Figure 1;
  • Figure 4 is a B-B cross-sectional view of the fin structure of Figure 1;
  • Figure 5 is a data comparison chart of the change of the heat exchange amount Q with the inlet wind speed
  • Figure 6 is a data comparison diagram of the Nusselt number Nu changing with the inlet wind speed
  • Figure 7 is a data comparison chart of the change of thermal resistance R with inlet wind speed
  • Figure 8 is a schematic diagram of the comparison of flow field characteristics in the flow channel when the inlet wind speed is 2m/s;
  • Figure 9 is a schematic diagram showing the comparison of flow field characteristics in the flow channel when the inlet wind speed is 4m/s;
  • Figure 10 is a schematic diagram of the comparison of flow field characteristics in the flow channel when the inlet wind speed is 6m/s.
  • a fin structure is provided.
  • the fin structure includes a fin base 10 and a plurality of protrusions.
  • the fin base 10 is a corrugated fin; the protrusions are arranged on the fin base 10, and a plurality of protrusions surround the outer circumference of the tube hole structure 20. 2 ⁇
  • This application improves the structure of the corrugated fin.
  • the function of the protrusions can strengthen the airflow disturbance near the tube hole structure (installed heat exchanger), and make the local area
  • the increase in the flow rate of the heat exchanger enhances the mixing of hot and cold fluids and increases the effective heat exchange area of the fins, thereby enhancing the heat exchange performance of the heat exchanger.
  • the fin structure of the present application is less prone to frost on the surface of the fin under wet conditions, and can effectively reduce the occurrence of flow channel blockage.
  • the fin structure of the present application can effectively increase the heat exchange area and further improve the heat exchange effect.
  • the fin base 10 includes a plurality of first corrugated surfaces 11 and a plurality of second corrugated surfaces 12, the second corrugated surface 12 is connected between the two first corrugated surfaces 11, the first corrugated surface 11
  • the corresponding node length L1 is greater than the corresponding node length L2 of the second corrugated surface 12. That is to say, the surface of the fin base 10 is divided into a large corrugated surface and a small corrugated surface.
  • the first corrugated surface is a large corrugated surface
  • the second corrugated surface is a small corrugated surface, and it expands in an M shape along the airflow direction.
  • the "plurality" here means two or more.
  • first corrugated surfaces 11 and the second corrugated surfaces 12 are arranged adjacent to each other.
  • the two first corrugated surfaces 11 are arranged symmetrically with respect to the tube hole structure 20
  • the two second corrugated surfaces 12 are arranged symmetrically with respect to the tube hole structure 20, and the two second corrugated surfaces 12 intersect to form a trough line.
  • the first corrugated surface 11 and the second corrugated surface 12 are arranged so that the surface of the entire fin is expanded in an M-shape along the airflow direction.
  • the ratio h1/S of the corrugation height h1 of the fin base 10 to the fin pitch S is 0.58-0.62, and L1/L2 is 1.5-1.7.
  • the relationship between the height of the corrugation and the pitch of the fins, as well as the relationship between the node length L1 corresponding to the first corrugated surface 11 and the node length L2 corresponding to the second corrugated surface 12, can improve the heat exchange capacity of the fin itself.
  • the plurality of protrusions include ring protrusions 31 and side protrusions 32.
  • the ring protrusions 31 are protrudingly provided on the first corrugated surface 11; the side protrusions 32 are protrudingly provided on the second corrugated surface 12. Both the annular convex portion 31 and the side convex portion 32 strengthen the fluid disturbance.
  • the two structures are arranged on different corrugated surfaces to delay the phenomenon of boundary layer flow separation and improve the heat exchange performance of the fins.
  • the ring protrusion 31 is an annular protrusion structure, the number of the ring protrusion 31 is multiple, and the plurality of ring protrusions 31 are symmetrically distributed on the outer circumference of the tube hole structure 20.
  • the plurality of annular protrusions 31 is a four-stage annular protrusion structure symmetrically arranged on the first corrugated surface 11.
  • the side convex portion 32 is a boss structure, the number of the side convex portion 32 is multiple, and the multiple side convex portions 32 are symmetrically distributed on the outer circumference of the tube hole structure 20.
  • the plurality of side protrusions 32 is a four-section square protrusion structure symmetrically arranged on the second corrugated surface 12.
  • the side convex portion 32 has a rectangular block shape. The arrangement of the side convex portion 32 and the annular convex portion 31 strengthens the airflow disturbance near the heat exchange tube, increases the flow velocity in the local area, enhances the mixing of hot and cold fluids, reduces the thickness of the boundary layer, and makes the wake area behind the tube Significantly reduced, increasing the effective heat exchange area of the fin.
  • the ratio h3/S of the protrusion height h3 of the annular protrusion 31 to the fin pitch S is 0.35 to 0.4.
  • the ratio h2/S of the protrusion height h2 of the side protrusions 32 to the fin pitch S is 0.35 to 0.4.
  • the fin base 10 is further provided with an annular groove 40, the tube hole structure 20 is located in the annular groove 40, the annular groove 40 and the tube hole structure 20 are arranged concentrically, and the outer circumference of the annular groove 40 is A corrugated surface 11 and a second corrugated surface 12 are connected, and the protrusions are both located outside the annular groove 40.
  • the structure of the annular groove 40 facilitates the stamping and forming of the peripheral side convex portion 32 and the annular convex portion 31, and improves the practicability of the process.
  • the structure of the annular groove 40 can simplify the processing difficulty and reduce the processing cost of the fin structure. High industrial value.
  • the annular groove 40 and each first corrugated surface 11 are connected to form an arc surface.
  • Two planes are formed at the junction of the annular groove 40 and each second corrugated surface 12.
  • the two arc-shaped surfaces formed at the junction of the annular groove 40 and the two first corrugated surfaces 11 are symmetrical with respect to the tube hole structure 20.
  • the four planes formed at the junction of the annular groove 40 and the two second corrugated surfaces 12 are symmetrical with respect to the tube hole structure 20.
  • the groove bottom of the annular groove 40 is a round surface and is tangent to the valley line in the direction of the vertical incoming flow.
  • the angle ⁇ between the bus bar of the arc-shaped surface and the central axis of the heat exchange tube is 45°.
  • the ratio d1/D of the bottom diameter d1 of the annular groove 40 to the outer diameter D of the heat exchange tube is 1.6 to 1.7.
  • the ratio D1/D of the inner diameter D1 of the tube hole structure 20 to the outer diameter D of the heat exchange tube is 1.025-1.035.
  • the present application also provides an embodiment of a heat exchanger, which includes the fin structure of the foregoing embodiment.
  • h is the convective heat transfer coefficient, the unit is w/(m 2 ⁇ K); De is the equivalent diameter of the air circulation surface, the unit is m; ⁇ is the thermal conductivity of air, the unit is w/(m ⁇ K).
  • S is the fin heat transfer surface area, the unit is m 2 ; ⁇ Tm is the logarithmic average temperature difference, the unit is K.
  • T wall is the average temperature of the fin surface in K.
  • the heat transfer amount Q, Nusselt number Nu, and thermal resistance R can all be calculated by extracting simulation data. The larger the heat transfer amount Q, Nusselt number Nu, or the smaller the thermal resistance R, the better the heat transfer performance. good.
  • the change of the heat exchange amount Q with the inlet wind speed is shown in Figure 5. As the inlet wind speed increases, the increase in the heat exchange amount will increase. At 6m/s, the increase in the heat exchange amount is the largest compared to the original fin. It is 4.37%.
  • the new fin in FIG. 5 refers to the fin structure of the present application, and the original fin refers to the fin structure of the prior art.
  • the variation of the Nusselt number Nu with the inlet wind speed is shown in Figure 6. As the inlet wind speed increases, the Nusselt number gradually increases. At 2m/s, the Nusselt number increases the most compared to the original fin. Is 11.16%.
  • the new fin in FIG. 6 refers to the fin structure of the present application, and the original fin refers to the fin structure of the prior art.
  • the change of the thermal resistance R with the inlet wind speed is shown in Figure 7. As the inlet wind speed increases, the thermal resistance gradually decreases. At 2m/s, the thermal resistance decreases the most compared to the original fin, which is 14.52%.
  • the new fin in FIG. 7 refers to the fin structure of the present application, and the original fin refers to the fin structure of the prior art.
  • This application also provides comparisons of flow field characteristics in the flow channel before and after the side protrusions 32 and the ring protrusions 31 are set, and the inlet wind speed is 2m/s, 4m/s, and 6m/s, as shown in Figs. 8-10.
  • Figure 8 shows the comparison of the flow field characteristics in the flow channel when the inlet wind speed is 2m/s
  • Figure 9 shows the comparison of the flow field characteristics in the flow channel when the inlet wind speed is 4m/s
  • Figure 10 shows the inlet wind speed of 6m /s, the comparison of the flow field characteristics in the flow channel.
  • the comparison between the fin structure of the prior art and the fin structure of the present application shows the same difference in flow field characteristics, which mainly reflects that the arrangement of the side protrusions 32 and the ring protrusions 31 enhances the change
  • the airflow turbulence near the heat pipe increases the flow velocity in the local area, enhances the mixing of hot and cold fluids, reduces the thickness of the boundary layer, reduces the wake area behind the pipe significantly, and increases the effective heat exchange area of the fins , Thereby enhancing the heat exchange performance of the heat exchanger.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

本申请公开了一种翅片结构及换热器，其中，翅片结构包括：翅片基体，翅片基体上具有用于穿设换热管的管孔结构，翅片基体为波纹翅片；多个凸起部，凸起部设置在翅片基体上，多个凸起部环绕在管孔结构的外周。本申请的翅片结构及换热器能够有效地提升翅片换热效果，强化换热器换热性能。

Description

翅片结构及换热器
相关申请的交叉引用
本申请是以申请号为202010588660.1，申请日为2020年6月24日的中国申请为基础，并主张其优先权，该中国申请的公开内容在此作为整体引入本申请中。
技术领域
本申请涉及制冷设备技术领域，具体而言，涉及一种翅片结构及换热器。
背景技术
现有技术中，翅片管换热器由于制造简单、适用性强等特点而广泛应用于化工、通风、供热、空调及制冷等行业，如何最大限度地传递热量和利用热能(强化传热)一直是行业内研究的重点。
翅片管换热器的翅片结构主要有平直翅片、波纹翅片以及相应的开缝(开窗)结构等，传统的平直翅片、波纹翅片在换热管背风侧经常换热不佳，而相应开缝结构由于增大了空气侧的接触面积，同时结构的不规则性对流场产生扰动，增强了流体间的混合，延缓了边界层的流动分离，从而强化整体换热性能。但是开缝结构通常会使翅片的通流间隙变小、流动阻力增大，在湿工况下容易结霜堵塞，缩短翅片使用寿命，同时降低了有效换热面积，影响翅片的实际换热效果。综合阻力、换热性能以及加工性的考量，波纹翅片是一种较为合适工业应用的一种形式。然而，随着换热器散热要求的进一步提高，传统的波纹翅片难以满足高效换热器的性能要求。
发明内容
本申请实施例中提供一种翅片结构及换热器，以提升翅片换热效果，强化换热器换热性能。
为实现上述目的，本申请提供了一种翅片结构，包括：翅片基体，翅片基体上具有用于穿设换热管的管孔结构，翅片基体为波纹翅片；和多个凸起部，凸起部设置在翅片基体上，多个凸起部环绕在管孔结构的外周。
进一步地，翅片基体包括多个第一波纹面和多个第二波纹面，两个第一波纹面之间连接有第二波纹面，第一波纹面对应波节长度L1大于第二波纹面对应波节长度L2。
进一步地，两个第一波纹面之间具有两个第二波纹面，两个第二波纹面相邻设置。
进一步地，翅片基体的波纹高度h1与翅片间距S的比值h1/S为0.58～0.62，L1/L2为1.5～1.7。
进一步地，多个凸起部包括：环凸部，环凸部凸出设置在第一波纹面上；侧凸部，侧凸部凸出设置在第二波纹面上。
进一步地，环凸部为环形凸起结构，环凸部的数量为多个，多个环凸部对称分布在管孔结构的外周。
进一步地，侧凸部为凸台结构，侧凸部的数量为多个，多个侧凸部的对称分布在管孔结构的外周。
进一步地，环凸部的凸起高度h3与翅片间距S的比值h3/S为0.35～0.4。
进一步地，侧凸部的凸起高度h2与翅片间距S的比值h2/S为0.35～0.4。
进一步地，翅片基体上还设置有：环形凹槽，管孔结构位于环形凹槽内，环形凹槽与管孔结构同心设置，环形凹槽的外周与第一波纹面和第二波纹面相接，凸起部均位于环形凹槽外部。
进一步地，两个第一波纹面之间具有两个第二波纹面，两个第二波纹面相邻设置，两个第二波纹面相交形成波谷线；环形凹槽与两个第一波纹面相接处形成关于管孔结构对称的两个弧形面，环形凹槽与两个第二波纹面相接处形成关于管孔结构对称的四个平面。
进一步地，环形凹槽的槽底在垂直来流方向与波谷线相切；弧形面的母线与换热管的中轴线夹角θ为45°。
进一步地，环形凹槽的槽底直径d1与换热管外径D的比值d1/D为1.6～1.7。
进一步地，两个第一波纹面相对于管孔结构对称设置，两个第二波纹面相对于管孔结构对称设置。
进一步地，管孔结构的内径D1与换热管外径D的比值D1/D为1.025～1.035。
根据本申请的另一个方面，提供了一种换热器，包括上述的翅片结构。
本申请对波纹翅片进行结构改进，通过在管孔结构的外周设置了多个凸起部，凸起部的作用可以加强管孔结构(安装的换热器)附近的气流扰动，使局部区域的流速提高，增强了冷热流体的混合，增大了翅片的有效换热面积，从而强化了换热器的换热性能。本申请的翅片结构相比于开窗翅片来说，在湿工况下翅片表面不易结霜，可以有效减少发生流道堵塞的情况。本申请的翅片结构相比于普通的波纹翅片，能够有 效增加换热面积，进一步提高了换热效果。
附图说明
图1是本申请实施例的翅片结构的平面示意图；
图2是是本申请实施例的翅片结构的立体结构示意图；
图3是图1的翅片结构的A-A剖面图；
图4是图1的翅片结构的B-B剖面图；
图5是换热量Q随入口风速的变化情况数据对比图；
图6是努赛尔数Nu随入口风速的变化情况数据对比图；
图7是热阻R随入口风速的变化情况数据对比图；
图8是入口风速为2m/s时流道内的流场特征对比示意图；
图9是入口风速为4m/s时流道内的流场特征对比示意图；
图10是入口风速为6m/s时流道内的流场特征对比示意图。
具体实施方式
下面结合附图和具体实施例对本申请作进一步详细描述，但不作为对本申请的限定。
参见图1至图4所示，根据本申请的实施例，提供了一种翅片结构，翅片结构包括翅片基体10和多个凸起部，翅片基体10上具有用于穿设换热管的管孔结构20，翅片基体10为波纹翅片；凸起部设置在翅片基体10上，多个凸起部环绕在管孔结构20的外周。2θ
本申请对波纹翅片进行结构改进，通过在管孔结构的外周设置了多个凸起部，凸起部的作用可以加强管孔结构(安装的换热器)附近的气流扰动，使局部区域的流速提高，增强了冷热流体的混合，增大了翅片的有效换热面积，从而强化了换热器的换热性能。本申请的翅片结构相比于开窗翅片来说，在湿工况下翅片表面不易结霜，可以有效减少发生流道堵塞的情况。本申请的翅片结构相比于普通的波纹翅片，能够有效增加换热面积，进一步提高了换热效果。
结合图1和图2，翅片基体10包括多个第一波纹面11和多个第二波纹面12，两个第一波纹面11之间连接有第二波纹面12，第一波纹面11对应波节长度L1大于第二波纹面12对应波节长度L2。也就是说翅片基体10的片表面分为大波纹面和小波纹 面，第一波纹面是大波纹面，第二波纹面是小波纹面，而且沿气流方向呈M型展开。此处的“多个”是指两个或两个以上。
两个第一波纹面11之间具有两个第二波纹面12，两个第二波纹面12相邻设置。在一些实施例中，两个第一波纹面11相对于管孔结构20对称设置，两个第二波纹面12相对于管孔结构20对称设置，两个第二波纹面12相交形成波谷线。本实施例的翅片基体10中，第一波纹面11和第二波纹面12的结构排布使整体片表面沿气流方向呈M型展开。
在一些实施例中，翅片基体10的波纹高度h1与翅片间距S的比值h1/S为0.58～0.62，L1/L2为1.5～1.7。波纹高度和翅片间距的关系，以及第一波纹面11对应波节长度L1和第二波纹面12对应波节长度L2的关系，可以提升翅片自身的换热能力。
参见图2，多个凸起部包括环凸部31和侧凸部32，环凸部31凸出设置在第一波纹面11上；侧凸部32凸出设置在第二波纹面12上。环凸部31和侧凸部32都是对流体扰动加强的，两个结构设置在不同的波纹面上，以延缓边界层流动分离的现象，提高翅片的换热性能。
环凸部31为环形凸起结构，环凸部31的数量为多个，多个环凸部31对称分布在管孔结构20的外周。在本实施例中，多个环凸部31为对称布置于第一波纹面11上的四段环形凸起结构。
侧凸部32为凸台结构，侧凸部32的数量为多个，多个侧凸部32对称分布在管孔结构20的外周。多个侧凸部32为对称布置于第二波纹面12上的四段方台凸起结构。侧凸部32呈矩形方台块形状。侧凸部32和环凸部31的设置加强了换热管附近的气流扰动，使其局部区域的流速提高，增强了冷热流体的混合，减薄了边界层的厚度，使管后尾迹区域明显减小，增大了翅片的有效换热面积。
为了考虑气流和环凸部31高度的平衡关系，环凸部31的凸起高度h3与翅片间距S的比值h3/S为0.35～0.4。
为了考虑气流和侧凸部32高度的平衡关系，侧凸部32的凸起高度h2与翅片间距S的比值h2/S为0.35～0.4。
在一些实施例中，翅片基体10上还设置有环形凹槽40，管孔结构20位于环形凹槽40内，环形凹槽40与管孔结构20同心设置，环形凹槽40的外周与第一波纹面11和第二波纹面12相接，凸起部均位于环形凹槽40外部。环形凹槽40的结构设置便于周边侧凸部32和环凸部31的冲压成型，提升了工艺实用性，环形凹槽40的结构能够 简化加工难度，降低了翅片结构的加工成本，具备非常高的工业价值。
两个第一波纹面11之间具有两个第二波纹面12，两个第二波纹面12相邻设置，两个第二波纹面12相交形成波谷线。环形凹槽40与每个第一波纹面11相接处均形成弧形面。环形凹槽40与每个第二波纹面12相接处均形成两个平面。环形凹槽40与两个第一波纹面11相接处所形成的两个弧形面关于管孔结构20对称。环形凹槽40与两个第二波纹面12相接处形成的四个平面关于管孔结构20对称。环形凹槽40的槽底为圆面，并在垂直来流方向与波谷线相切。弧形面的母线与换热管的中轴线夹角θ为45°。
环形凹槽40槽底直径d1与换热管外径D的比值d1/D为1.6～1.7。管孔结构20的内径D1与换热管外径D的比值D1/D为1.025～1.035。
本申请还提供了一种换热器的实施例，换热器包括上述实施例的翅片结构。
本实施例通过ANSYS Fluent进行仿真验证，仿真时入口空气流速分别为2m/s、3m/s、4m/s、5m/s、6m/s，进风温度为35℃，管壁温度为50.62℃，对比在同等流量情况下有无设置侧凸部32和环凸部31前后换热量Q、努赛尔数Nu、热阻R的变化情况以及流道内的流场特征，其中，换热量Q、努赛尔数Nu、热阻R的定义如下：
Q＝mC p(T out-T in)
m为质量流量，单位是kg/s；Cp为定压比热容，单位是j/(kg·K)；T out为空气流道出口平均温度，单位是K；T in为空气流道入口平均温度，单位是K。
Figure PCTCN2021079352-appb-000001
h为对流换热系数，单位是w/(m 2·K)；De为空气流通面当量直径，单位是m；λ为空气的导热系数，单位是w/(m·K)。
Figure PCTCN2021079352-appb-000002
S为翅片换热表面积，单位是m 2；ΔTm为对数平均温差，单位是K。
Figure PCTCN2021079352-appb-000003
ΔT max＝T wall-T inΔT min＝T wall-T out
T wall为翅片表面的平均温度，单位是K。
Figure PCTCN2021079352-appb-000004
换热量Q、努赛尔数Nu、热阻R均可以通过提取仿真数据计算求得，且换热量Q、努赛尔数Nu越大，或热阻R越小，则换热性能越好。
换热量Q随入口风速的变化情况如图5所示，随着入口风速增大，换热量的提升量会增大，在6m/s时，相对原翅片，换热量提升最大，为4.37％。图5中新翅片是指本申请的翅片结构，原翅片是指现有技术的翅片结构。
努赛尔数Nu随入口风速的变化情况如图6所示，随着入口风速增大，努赛尔数逐渐增大，在2m/s时，相对原翅片，努赛尔数提升最大，为11.16％。图6中新翅片是指本申请的翅片结构，原翅片是指现有技术的翅片结构。
热阻R随入口风速的变化情况如图7所示，随着入口风速增大，热阻逐渐减小，在2m/s时，相对原翅片，热阻降低最大，为14.52％。图7中新翅片是指本申请的翅片结构，原翅片是指现有技术的翅片结构。
本申请还给出了设置侧凸部32和环凸部31前后，入口风速为2m/s、4m/s、6m/s时流道内的流场特征对比情况，如图8-10所示。其中，图8示出了入口风速2m/s时流道内的流场特征对比情况；图9示出了入口风速4m/s时流道内的流场特征对比情况；图10示出了入口风速6m/s时流道内的流场特征对比情况。
不同入口风速下，现有技术的翅片结构和本申请翅片结构的对比，表现出相同的流场特征差异性，其主要体现出，侧凸部32和环凸部31的设置加强了换热管附近的气流扰动，使当地局部区域的流速提高，增强了冷热流体的混合，减薄了边界层的厚度，使管后尾迹区域明显减小，增大了翅片的有效换热面积，从而强化了换热器的换热性能。
需要注意的是，这里所使用的术语仅是为了描述具体实施方式，而非意图限制根据本申请的示例性实施方式。如在这里所使用的，除非上下文另外明确指出，否则单数形式也意图包括复数形式，此外，还应当理解的是，当在本说明书中使用术语“包含”和/或“包括”时，其指明存在特征、步骤、工作、器件、组件和/或它们的组合。
需要说明的是，本申请的说明书和权利要求书及上述附图中的术语“第一”、“第二”等是用于区别类似的对象，而不必用于描述特定的顺序或先后次序。应该理解这样使用的数据在适当情况下可以互换，以便这里描述的本申请的实施方式能够以除了在这里图示或描述的那些以外的顺序实施。
当然，以上是本申请的优选实施方式。应当指出，对于本技术领域的普通技术人员来说，在不脱离本申请基本原理的前提下，还可以做出若干改进和润饰，这些改进和润饰也视为本申请的保护范围。

Claims (16)

  1. 一种翅片结构，包括：
    翅片基体(10)，所述翅片基体(10)上具有用于穿设换热管的管孔结构(20)，所述翅片基体(10)为波纹翅片；和
    多个凸起部，所述凸起部设置在所述翅片基体(10)上，多个所述凸起部环绕在所述管孔结构(20)的外周。
  2. 根据权利要求1所述的翅片结构，其中，所述翅片基体(10)包括多个第一波纹面(11)和多个第二波纹面(12)，两个所述第一波纹面(11)之间连接有所述第二波纹面(12)，所述第一波纹面(11)对应波节长度L1大于所述第二波纹面(12)对应波节长度L2。
  3. 根据权利要求2所述的翅片结构，其中，两个所述第一波纹面(11)之间具有两个所述第二波纹面(12)，两个所述第二波纹面(12)相邻设置。
  4. 根据权利要求2或3所述的翅片结构，其中，所述翅片基体(10)的波纹高度h1与翅片间距S的比值h1/S为0.58～0.62，L1/L2为1.5～1.7。
  5. 根据权利要求2-4任一所述的翅片结构，其中，所述多个凸起部包括：
    环凸部(31)，所述环凸部(31)凸出设置在所述第一波纹面(11)上；和
    侧凸部(32)，所述侧凸部(32)凸出设置在所述第二波纹面(12)上。
  6. 根据权利要求5所述的翅片结构，其中，所述环凸部(31)为环形凸起结构，所述环凸部(31)的数量为多个，多个所述环凸部(31)对称分布在所述管孔结构(20)的外周。
  7. 根据权利要求5或6所述的翅片结构，其中，所述侧凸部(32)为凸台结构，所述侧凸部(32)的数量为多个，多个所述侧凸部(32)对称分布在所述管孔结构(20)的外周。
  8. 根据权利要求5-7任一所述的翅片结构，其中，所述环凸部(31)的凸起高度h3与翅片间距S的比值h3/S为0.35～0.4。
  9. 根据权利要求5-8任一所述的翅片结构，其中，所述侧凸部(32)的凸起高度h2与翅片间距S的比值h2/S为0.35～0.4。
  10. 根据权利要求2-9任一所述的翅片结构，其中，所述翅片基体(10)上还设置有：
    环形凹槽(40)，所述管孔结构(20)位于所述环形凹槽(40)内，所述环形凹槽(40)与所述管孔结构(20)同心设置，所述环形凹槽(40)的外周与所述第一波纹面(11)和所述第二波纹面(12)相接，所述凸起部均位于所述环形凹槽(40)外部。
  11. 根据权利要求10所述的翅片结构，其中，
    两个所述第一波纹面(11)之间具有两个所述第二波纹面(12)，两个所述第二波纹面(12)相邻设置，两个所述第二波纹面(12)相交形成波谷线；
    所述环形凹槽(40)与所述两个第一波纹面(11)相接处形成关于所述管孔结构(20)对称的两个弧形面，所述环形凹槽(40)与所述两个所述第二波纹面(12)相接处形成关于所述管孔结构(20)对称的四个平面。
  12. 根据权利要求11所述的翅片结构，其中，
    所述环形凹槽(40)的槽底在垂直来流方向与波谷线相切；所述弧形面的母线与所述换热管的中轴线夹角θ为45°。
  13. 根据权利要求10-12任一所述的翅片结构，其中，所述环形凹槽(40)的槽底直径d1与所述换热管外径D的比值d1/D为1.6～1.7。
  14. 根据权利要求3-13任一所述的翅片结构，其特征在于，两个所述第一波纹面(11)相对于所述管孔结构(20)对称设置，两个所述第二波纹面(12)相对于所述管孔结构(20)对称设置。
  15. 根据权利要求1-14任一所述的翅片结构，其特征在于，所述管孔结构(20)的内径D1与所述换热管外径D的比值D1/D为1.025～1.035。
  16. 一种换热器，其特征在于，包括权利要求1-15中任一项所述的翅片结构。
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