WO2016015324A1 - 管翅式换热器流线型波纹翅片 - Google Patents

管翅式换热器流线型波纹翅片 Download PDF

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Publication number
WO2016015324A1
WO2016015324A1 PCT/CN2014/083506 CN2014083506W WO2016015324A1 WO 2016015324 A1 WO2016015324 A1 WO 2016015324A1 CN 2014083506 W CN2014083506 W CN 2014083506W WO 2016015324 A1 WO2016015324 A1 WO 2016015324A1
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WIPO (PCT)
Prior art keywords
fin
tube
heat exchanger
corrugations
concave
Prior art date
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Ceased
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PCT/CN2014/083506
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English (en)
French (fr)
Inventor
王良璧
宋克伟
胡万玲
王良成
林志敏
常立民
武祥
张昆
苏梅
张强
郭鹏
王天鹏
周文和
王烨
张永恒
王小见
刘松
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Individual
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Individual
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Priority to PCT/CN2014/083506 priority Critical patent/WO2016015324A1/zh
Priority to KR1020167015869A priority patent/KR101817553B1/ko
Priority to US15/104,926 priority patent/US10982912B2/en
Priority to EP14898379.4A priority patent/EP3104111B1/en
Priority to JP2016541683A priority patent/JP6200598B2/ja
Publication of WO2016015324A1 publication Critical patent/WO2016015324A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
    • F28F1/325—Fins with openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • 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
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/02—Streamline-shaped elements

Definitions

  • the present invention relates to fins for tube-and-fin heat exchangers, and more particularly to a streamlined corrugated fin for a tube-and-fin heat exchanger for a circular or elliptical tube.
  • Tube-and-fin heat exchangers typically flow a liquid medium within the tube and flow a gas outside the tube.
  • installing fins on the outside of the tube can increase the heat exchange area to reduce the thermal resistance. Due to the limitations of heat exchanger volume, economy and fin efficiency, the area of the fins cannot be increased indefinitely.
  • increasing the disturbance of the fluid is an effective measure to improve the heat transfer effect on the air side.
  • the fin surface is typically formed into a structural shape that facilitates increased fluid perturbations, such as louvers, lateral corrugations, vortex generators, intermittent toroidal grooves, diamond-shaped thorns, and the like.
  • the fins of the above structure can achieve the purpose of enhancing heat transfer on the surface of the fins, they also cause an increase in flow resistance. Furthermore, the existing shutters, corrugations, vortex generators, intermittent toroidal grooves, diamond-shaped thorns and the like are easy to hang dust, which increases the fin side thermal resistance and reduces the heat transfer performance.
  • the flow of fluid through the tube/oval tube is less linear, especially when the flow rate is large, the fluid flows across the tube/oval tube.
  • the loss of flow pressure caused by the removal of the body is large, and a recirculation zone which is unfavorable for heat transfer is formed at the tail of the round pipe/oval tube, and the flow heat transfer performance needs to be further improved.
  • the existing fin-enhanced heat transfer technology of tube-fin heat exchangers does not significantly improve the flow linearity of fluid flow between the tube/elliptical tube bundles, allowing fluid to flow through the tube/elliptical tube bundle and fins.
  • the pressure loss is large when the channel is formed. Therefore, it is very important to further develop a fin structure having good heat transfer performance, low pressure loss, and difficulty in ashing.
  • An object of the present invention is to provide a streamline type corrugated fin of a tube-fin heat exchanger capable of suppressing fluid release, reducing flow pressure loss, improving fin heat exchange performance, and maintaining heat dissipation stability.
  • the present invention provides a tube-and-tube heat exchanger streamline type corrugated fin, comprising a fin body, one side end of which is an air flow inlet, and the other side end is an air flow outlet,
  • the fin body is provided with a mounting hole for mounting the tube bundle, and a plurality of spaced corrugated and concave corrugations are continuously formed on the fin body according to the flow line of the airflow from the airflow inlet to the airflow outlet.
  • the peak connection and phase of the same convex corrugation The valley lines of the same concave corrugation adjacent to each other are streamlines.
  • a tube-and-fin heat exchanger streamline type corrugated fin as described above, wherein the convex corrugation and the concave corrugation are disposed in a boundary of a corrugated region set on the fin body, and the corrugated region boundary is located in the The upper and lower sides of the mounting hole, the boundary of the corrugated area is a streamline, determined by a flow function value, the spacing between the peak line of the convex corrugation and the trough line of the adjacent concave corrugation or The number of convex corrugations and the concave corrugations is determined as needed according to the value of the region boundary flow function.
  • a tube-and-fin heat exchanger streamline type corrugated fin as described above, wherein a amplitude of the convex corrugation and a wave amplitude of the concave corrugation are respectively increased away from the mounting hole, and are reduced near the mounting hole .
  • a tube-and-fin heat exchanger streamline type corrugated fin as described above, wherein an annular boss for restricting the spacing of the streamlined corrugated fins is provided along one side edge of the mounting hole, and the top of the annular boss is everted There is a cuff.
  • the singularity of the height of the annular slab is 0. 1 ⁇ 0. 9 times.
  • tube-and-fin heat exchanger streamline type corrugated fin as described above, wherein the mounting hole is a circular hole or an elliptical hole.
  • the present invention has the following features and advantages:
  • the invention continuously guides the streamlined convex corrugations and the concave corrugations on the surface of the fins, so that the fluid in the airflow passage mainly flows in the streamlined passage formed by the convex corrugations and the concave corrugations, the flow is smooth, the flow distribution is relatively uniform, and the circle is effectively suppressed.
  • the removal of the fluid from the tail of the tube/oval tube significantly reduces the flow pressure loss.
  • the convex corrugation and the concave corrugation increase the fin surface area and reduce the heat transfer resistance on the fin side, and the fluid streamline flow makes it difficult to generate the recirculation zone after the tube bundle, and the heat transfer performance of the fin at the rear of the tube is also significantly improved.
  • the above makes the invention have better flow and heat transfer performance, and makes the fins less likely to hang dust during use, and maintains the stability of heat dissipation performance.
  • FIG. 1 is a plan view showing a planar structure of a streamlined corrugated fin of a tube-and-fin heat exchanger according to the present invention
  • FIG. 2 is a cross-sectional view of the cross-sectional structure taken along line A-A of FIG.
  • Figure 3 is a schematic cross-sectional view of the cross-sectional structure taken along line B-B of Figure 1;
  • Figure 4 is a schematic cross-sectional view of the cross-sectional structure taken along line C-C of Figure 1;
  • Figure 5 is a side elevational view taken along line D of Figure 1;
  • FIG. 6 is a schematic plan view showing a second embodiment of a streamlined corrugated fin of a tube-and-fin heat exchanger according to the present invention
  • FIG. 7 is a cross-sectional view showing a cross-sectional structure of the A'-A' of FIG.
  • Figure 8 is a schematic cross-sectional view showing the cross-sectional structure taken along line B'-B' of Figure 6;
  • Figure 9 is a schematic cross-sectional view showing the cross section of the C'-C direction of Figure 6;
  • Figure 10 is a side view of Figure 6 taken along line D'.
  • FIG. 1 to 5 are schematic views showing a first embodiment of a streamlined corrugated fin of a tube-and-fin heat exchanger according to the present invention.
  • the streamline type corrugated fin of the tube-and-fin heat exchanger of the present invention comprises a fin body 1.
  • One side end of the fin body 1 is an air flow inlet 3, and the other side end is an air flow outlet 4, in the wing
  • the mounting body 2 is provided with a mounting hole 2 for mounting a heat exchanger tube bundle.
  • the mounting hole 2 is a circular tube hole, and a plurality of streamlined corrugated fins are stacked at intervals, and the circular tube penetrates each streamline in the axial direction.
  • the mounting hole 2 of the corrugated fin, the plurality of streamlined corrugated fins are sequentially fixed on the circular tube to form a heat exchanger.
  • An air flow passage is formed between adjacent two streamline type corrugated fins.
  • each fin body 1 On each fin body 1 , a plurality of spaced apart convex corrugations 11 and concave corrugations 12 are formed continuously from the air flow inlet 3 to the air flow outlet 4 according to the flow direction of the air flow, and the peaks of the same convex corrugations 11 (shown in FIG. 2 ) are connected.
  • the trough line 6 of the line 5 and the adjacent same concave corrugation 12 (shown in FIG. 7) are streamlines, so that a flow guiding channel conforming to the flow line of the airflow is formed on the surface of the fin body 1, guiding the fluid According to the preset flow line, the effect of suppressing fluid release, reducing flow pressure loss, improving fin heat exchange capacity and maintaining heat dissipation performance is achieved.
  • the flow line is a flow line of the tube-fin heat exchanger flat fin-side channel tube on the axial center section of the fin body 1 without backflow.
  • the finned fin heat exchanger flat fins of the fin body 1 refer to the heat exchanger flat fins of the present invention which are flat sheets before the convex corrugations 11 and the concave corrugations 12 are processed.
  • the flat fin side passage refers to a passage formed between adjacent two flat fins and a circular tube passing through the mounting hole.
  • the axial center section of the passage tube means a section perpendicular to the axial direction of the circular tube in the fin side passage and equal to the distance between the two formed passage fins.
  • the tail is a small area downstream of the tube relative to the direction of gas flow.
  • the streamline is related to the specific structure of the heat exchanger, and can be solved by those skilled in the art by the existing numerical methods, and will not be described in detail herein. Those skilled in the art can obtain the working condition, using the calculation method and the limited number of trial calculations to obtain the fin-fin heat exchanger of the fin body 1 and the fin-side channel tube on the axial center section. Streamlined.
  • the spacing between the peak line 5 of the convex corrugation and the trough line 6 of the adjacent concave corrugation or the number of the convex corrugations 11 and the concave corrugations 12 are determined as needed according to the boundary flow function value of the corrugated area.
  • a corrugated area boundary 8 is provided on the upper and lower sides of the mounting hole 2, and the convex corrugations 11 and the concave corrugations 12 are respectively disposed in the corrugated area boundary 8, and the upper and lower boundaries of the corrugated area boundary 8 It is also a streamline, and takes different stream function values respectively.
  • the value of the region boundary flow function is determined as needed.
  • the convex ripple is obtained as needed.
  • the calculation method of the stream function value is a prior art, and will not be described in detail herein.
  • the cross-sections of the convex corrugations 11 and the concave corrugations 12 are continuous sinusoidal waveforms, and the dashed boxes in FIGS. 2 and 7 respectively represent the convex corrugations 11 and the concave corrugations 12, respectively.
  • Corrugated shape 7 the present invention is not limited thereto, and the cross section of the convex corrugations 11 and the concave corrugations 12 may be in a zigzag shape, a parabola shape, a circular arc shape or other suitable shape as long as it is advantageous for guiding the fluid flow.
  • each of the convex corrugations 11 and the concave corrugations 12 may be a fixed value; or may be a non-fixed value, that is, the amplitudes of the convex corrugations 11 and the concave corrugations 12 are longitudinal (longitudinal, that is, the direction of the airflow inlet 3 to the airflow outlet 4) It is distributed in a waveform curve.
  • the amplitude of the convex corrugations 11 and the concave corrugations 12 can be designed to be opposite to the change of the air flow velocity during the flow of the airflow through the corrugated fins, that is, the amplitude of the airflow is reduced in a region where the flow velocity is large.
  • the amplitude of the region increases in a region where the flow velocity is small.
  • the amplitudes of the convex corrugations 11 and the concave corrugations 12 are equal or unequal in the lateral direction (i.e., perpendicular to the main flow direction). Those skilled in the art can make a selection according to actual conditions.
  • the amplitudes of the convex corrugations 11 and the concave corrugations 12 may be designed such that the amplitudes of the convex corrugations 11 and the concave corrugations 12 increase away from the mounting hole, near the installation. The hole is reduced. Thus, the fluid flow shear stress on the wall surface of the corrugated fin can be reduced, so that the flow resistance can be further reduced.
  • the streamlined convex corrugations 11 and the concave corrugations 12 are distributed between the corrugated area boundaries 8 as needed according to the flow function value, and the convex corrugations 11 and the concave corrugations 12 are along the mounting holes 2
  • the transverse center line and the longitudinal center line are symmetrically distributed, wherein the transverse center line refers to a straight line passing through the center of the mounting hole 2 from left to right in FIG. 1, and the longitudinal center line refers to the mounting hole 2 from bottom to top in FIG.
  • the straight line of the center makes the fluid flow velocity more uniform, reduces the flow pressure loss, and improves the fin heat exchange capacity.
  • a plurality of mounting holes 2 are disposed on the fin body 1 , and a plurality of mounting holes 2 may be disposed in a row, that is, the center points of the plurality of mounting holes 2 are on the same horizontal line;
  • the fork row mode is set, that is, the center points of the plurality of mounting holes 2 are not on the same horizontal line.
  • An annular boss 9 is disposed along the side of the mounting hole 2, and when the corrugated fin and the circular tube are mounted, the annular boss 9 protruding from the front portion of the latter corrugated fin abuts against the rear of the preceding corrugated fin In order to limit the spacing of the streamlined corrugated fins, the fin positioning is achieved.
  • the top of the annular boss 9 is slightly turned outward with a flange 10 to facilitate the passage of the fins and the determination of the fins. Distance.
  • the height of the annular boss 9 can be designed to different sizes according to the fin pitch variation.
  • the surfaces of the convex corrugations 11 and the concave corrugations 12 are smooth surfaces, and the streamlined structure combining the convex corrugations 11 and the concave corrugations 12 is not easy to hang dust during use, further reducing the fin side thermal resistance and improving the fin transmission. Thermal performance.
  • FIGS. 6 to 10 are schematic views of the second embodiment of the streamlined corrugated fin of the tube-and-fin heat exchanger of the present invention.
  • the structure and function of this embodiment are substantially the same as those of the first embodiment, except that the mounting hole 2 used in the embodiment is an elliptical hole to accommodate a bundle of tubes having an elliptical cross section.
  • the corrugated fins are placed on a circular tube or an elliptical tube, and the corrugated fins are positioned by an annular boss 9 with a flange 10, and the tube is tested by a tube/tube or a tube.
  • a series of processes such as pressing complete the fabrication of the entire tube-fin heat exchanger.
  • the working principle of the streamlined corrugated fin of the present invention is: when the fluid (airflow) flows in the airflow passage between the streamlined corrugated fins, the fluid continuously passes through the streamlined convex corrugations 11 and the concave corrugations 12 of the fin surface, Part of the flow in the streamlined channel formed by the convex corrugations 11 and the concave corrugations 12, so that the flow is smooth, the flow distribution is relatively uniform, and the round tube/elliptical tube tail portion is effectively suppressed (the tail portion refers to the flow of the airflow across the circular tube according to the flow direction of the airflow) At the downstream of the hour tube, the fluid is released, which significantly reduces the flow pressure loss.
  • the convex corrugations 11 and the concave corrugations 12 increase the surface area of the fins, reduce the heat transfer resistance on the fin side, and the fluid streamlined flow makes it difficult to generate a recirculation zone after the tube bundle, and the heat transfer performance of the fins at the tail of the tube is also significantly improved.
  • the above invention makes the streamlined corrugated fins have better flow and heat transfer performance, and the fins are less likely to hang dust during use, and maintain the stability of heat dissipation performance.

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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)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

一种管翅式换热器流线型波纹翅片，包括翅片本体（1），翅片本体（1）的一侧端为气流入口（3），其另一侧端为气流出口（4），在翅片本体（1）上布设有用于安装管束的安装孔（2），在翅片本体（1）上按照气流流线走向从气流入口（3）至气流出口（4）连续形成若干条间隔设置的凸波纹（11）和凹波纹（12），同一所述凸波纹（11）的波峰连线（5）与同一所述凹波纹（12）的波谷连线（6）均为流线；有效抑制了圆管尾部流体的脱体，明显减小了流动压力损失；同时，增加翅片表面积、减小翅片侧传热热阻，且流体流线型流动使得圆管后不易产生回流区，管束后部翅片的换热性能也得到明显提高，具有较好的流动与传热性能，且使翅片在使用中不易挂灰尘，保持散热性能的稳定性。

Description

管翅式换热器流线型波纹翅片
技术领域
本发明涉及管翅式换热器的翅片，特别涉及一种用于圆管或椭圆管的管翅式换热器 的流线型波纹翅片。 背景技术
管翅式换热器通常是在管内流动液体工质， 在管外侧流动气体。 为减小空气侧的热 阻， 在管外侧安装翅片可以增加换热面积达到减小热阻的目的。 由于受到换热器体积、 经济性和翅片效率的限制， 使得翅片的面积不能无限的增加。 为进一步提高管翅式换热 器的传热性能， 增加流体的扰动是改善空气侧换热效果的一种有效措施。 通常将翅片表 面做成利于增加流体扰动的结构形状， 比如百叶窗、横向波纹、涡产生器、 间断环面槽、 菱形立刺等。 虽然采用上述结构的翅片可以达到强化翅片表面传热的目的， 但同时也引 起了流动阻力的增加。 再者， 现有百叶窗、 波纹、 涡产生器、 间断环面槽、 菱形立刺等 结构易挂灰尘， 使得翅片侧热阻增加， 降低了其传热性能。
另外， 对于圆管 /椭圆管结构的管翅式换热器， 流体掠过圆管 /椭圆管流动的流线性 较差， 特别是在流速较大时， 流体掠过圆管 /椭圆管流动的脱体引起流动压力损失较大， 并且在圆管 /椭圆管尾部形成不利于传热的回流区， 流动传热性能有待进一步提高。
综上所述， 管翅式换热器现有的翅片强化传热技术没有明显的改善流体在圆管 /椭 圆管束之间流动的流线性， 使得流体流经圆管 /椭圆管束和翅片形成的通道时压力损失 较大。 因此， 进一步开发传热性能好、 压力损失小、 不易挂灰的翅片结构非常重要。 发明内容
本发明的目的是提供一种能够抑制流体脱体、 减小流动压力损失， 提高翅片换热能 力并保持散热性能稳定的管翅式换热器流线型波纹翅片。
为达到上述目的，本发明提供了一种管翅式换热器流线型波纹翅片，包括翅片本体， 所述翅片本体的一侧端为气流入口， 其另一侧端为气流出口， 在所述的翅片本体上布设 有用于安装管束的安装孔，在所述翅片本体上按照气流流线走向从所述气流入口至所述 气流出口连续形成若干条间隔设置的凸波纹和凹波纹， 同一所述凸波纹的波峰连线与相 邻的同一所述凹波纹的波谷连线均为流线。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述流线是翅片本体所对应管翅 式换热器平片翅片侧通道管轴向中心截面上管尾不出现回流的流线。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹与所述凹波纹设置于 所述翅片本体上设定的波纹区域边界内， 所述波纹区域边界位于所述安装孔的上下两 侧， 所述波纹区域边界均是流线， 以流函数值按需确定， 所述凸波纹的波峰连线与相邻 的凹波纹的波谷连线之间的间距或所述凸波纹和所述凹波纹设置数量依据区域边界流 函数值按需确定。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的横断 面呈适宜型线， 比如， 折线形、 正弦波形、 抛物线形或圆弧形等。
如上所述的管翅式换热器流线型波纹翅片， 其中， 每条所述凸波纹和每条所述凹波 纹的波幅为固定值。
如上所述的管翅式换热器流线型波纹翅片， 其中， 每条所述凸波纹和每条所述凹波 纹的波幅沿纵向呈波形曲线分布。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的波幅 在所述气流流速大的区域减小， 在所述气流流速小的区域增大。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的波幅 沿横向相等。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的波幅 沿横向不等。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹的波幅和所述凹波纹 的波幅分别在远离所述安装孔处增大， 在靠近所述安装孔处减小。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹分别以 所述安装孔的横向中心线和纵向中心线对称分布。
如上所述的管翅式换热器流线型波纹翅片， 其中， 沿所述安装孔一侧边缘设有用于 限制流线型波纹翅片间距的环状凸台， 所述环状凸台的顶部外翻有一翻边。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的最大 波幅为所述环状凸台高度的 0. 1〜0. 9倍。
如上所述的管翅式换热器流线型波纹翅片， 其中， 所述安装孔为圆孔或椭圆孔。 如上所述的管翅式换热器流线型波纹翅片， 其中， 所述凸波纹和所述凹波纹的表面 为光滑表面。
与现有技术相比， 本发明具有以下特点和优点：
本发明通过翅片表面的流线型凸波纹和凹波纹的连续不断的引导，使得气流通道内 流体主要在凸波纹和凹波纹形成的流线型通道内流动， 流动平稳， 流量分配较为均匀， 有效抑制了圆管 /椭圆管尾部流体的脱体， 明显减小了流动压力损失。 同时， 凸波纹和 凹波纹增加了翅片表面积、 减小了翅片侧传热热阻， 且流体流线型流动使得管束后不易 产生回流区， 管后部翅片的换热性能也得到明显提高。 以上使得本发明具有较好的流动 与传热性能， 且使翅片在使用中不易挂灰尘， 保持散热性能的稳定性。 附图说明
在此描述的附图仅用于解释目的， 而不意图以任何方式来限制本发明公开的范围。 另外， 图中的各部件的形状和比例尺寸等仅为示意性的， 用于帮助对本发明的理解， 并 不是具体限定本发明各部件的形状和比例尺寸。 本领域的技术人员在本发明的教导下， 可以根据具体情况选择各种可能的形状和比例尺寸来实施本发明。
图 1为本发明管翅式换热器流线型波纹翅片实施例一的平面结构示意图； 图 2为图 1的沿 A-A向截面结构示意图剖视图；
图 3为图 1的沿 B-B向截面结构示意图剖视图；
图 4为图 1的沿 C-C向截面结构示意图剖视图；
图 5为图 1的沿 D向的侧视图；
图 6为本发明管翅式换热器流线型波纹翅片实施例二的平面结构示意图； 图 7为图 6的 A' -A' 向截面结构示意图剖视图；
图 8为图 6的 B' -B' 向截面结构示意图剖视图；
图 9为图 6的 C' -C 向截面结构示意图剖视图；
图 10为图 6的沿 D' 向的侧视图。
附图标记说明：
1-翅片本体； 2-安装孔（圆管孔或椭圆孔） ； 3-气流入口； 4-气流出口； 5-凸波纹 波峰连线； 6-凹波纹波谷连线； 7-波纹形状； 8-波纹区域边界； 9-环状凸台； 10-翻边； 11-凸纹波； 12-凹纹波。 具体实施方式 结合附图和本发明具体实施方式的描述，能够更加清楚地了解本发明的细节。但是， 在此描述的本发明的具体实施方式， 仅用于解释本发明的目的， 而不能以任何方式理解 成是对本发明的限制。 在本发明的教导下， 技术人员可以构想基于本发明的任意可能的 变形， 这些都应被视为属于本发明的范围。
图 1至图 5为本发明管翅式换热器流线型波纹翅片实施例一的示意图。
如图 1所示， 本发明管翅式换热器流线型波纹翅片， 包括翅片本体 1， 翅片本体 1 的一侧端为气流入口 3， 其另一侧端为气流出口 4， 在翅片本体 1上布设有用于安装换 热器管束的安装孔 2， 在本实施例中， 安装孔 2为圆管孔， 多片流线型波纹翅片间隔地 叠放， 圆管沿轴向贯穿各流线型波纹翅片的安装孔 2， 多片流线型波纹翅片依序固定于 圆管上， 形成换热器。 相邻的两流线型波纹翅片之间形成气流通道。 在各翅片本体 1上 按照气流流线走向从气流入口 3至气流出口 4连续冲压形成若干条间隔设置的凸波纹 11 和凹波纹 12， 同一凸波纹 11 (如图 2所示） 的波峰连线 5与相邻的同一凹波纹 12 (如 图 7所示） 的波谷连线 6均为流线， 从而在翅片本体 1的表面形成了与气流流线走向一 致的导流通道， 引导流体按预设的流线流动，实现了抑制流体脱体、减小流动压力损失， 提高翅片换热能力及保持散热性能稳定的功效。
所述流线是翅片本体 1所对应管翅式换热器平片翅片侧通道管轴向中心截面上管尾 不出现回流的流线。翅片本体 1所对应管翅式换热器平片翅片是指本发明在没有加工出 凸波纹 11和凹波纹 12前， 呈平片状的换热器平片翅片。 平片翅片侧通道是指在相邻的 两平片翅片之间及和穿过安装孔的圆管形成的通道。通道管轴向中心截面是指在翅片侧 通道内垂直于圆管轴向的且和两构成通道翅片距离相等的截面。管尾是指圆管外侧相对 气体流动方向而言处于下游的小区域。
在本发明中， 流线与换热器的具体结构有关， 本领域的技术人员可通过现有的数值 方法求解得到， 在此不再详细说明。 本领域的技术人员可实际工况， 利用计算方法和有 限次的试算获得翅片本体 1所对应管翅式换热器平片翅片侧通道管轴向中心截面上管尾 不出现回流的流线。
进一步的， 凸波纹的波峰连线 5与相邻的凹波纹的波谷连线 6之间的间距或凸波纹 11和凹波纹 12设置数量依据波纹区域边界流函数值按需确定。 在本发明中， 根据安装 孔 2的位置， 在安装孔 2的上下两侧设置波纹区域边界 8， 凸波纹 11和凹波纹 12分别 设置在波纹区域边界 8内， 波纹区域边界 8的上下两边界也是流线， 且分别取不同的流 函数值， 区域边界流函数值按需确定， 根据波纹区域边界 8的流函数值按需得到凸波纹 的波峰连线 5和凹波纹的波谷连线 6的间距及设置数量。其中流函数值的计算方法为已 有技术， 在此不再详细说明。
如图 2至图 4所示， 在本实施例中， 凸波纹 11和凹波纹 12的横断面呈连续的正弦 波形， 如图 2、 图 7的虚线框中分别表示凸波纹 11和凹波纹 12的波纹形状 7。 但本发 明也不限于此， 凸波纹 11和凹波纹 12的横断面还可以呈折线形、 抛物线形、 圆弧形或 其它适宜的形状， 只要利于引导流体流动即可。
进一步的， 每条凸波纹 11和凹波纹 12的波幅可以是固定值； 也可以是非固定值， 即凸波纹 11和凹波纹 12的波幅沿纵向 （纵向即气流入口 3至气流出口 4的方向）呈波 形曲线分布。
作为本发明一种优选的实施方式， 凸波纹 11和凹波纹 12的波幅可以设计为在气流 流经波纹翅片过程中波幅变化与气流流速的变化相反， 即在气流流速大的区域波幅减 小， 在所述气流流速小的区域波幅增大。 这样， 可以减小波纹翅片壁面上的流体流动切 应力， 而该应力是引起流动阻力的主要因素， 因此可以起到减小流动阻力的作用。
进一步的， 凸波纹 11和凹波纹 12的波幅沿横向 （即垂直于气流主流方向）相等或 不等。 本领域的技术人员可根据实际情况进行选择。
作为本发明一种优选的实施方式， 凸波纹 11和凹波纹 12的波幅可以设计为所述凸 波纹 11和所述凹波纹 12的波幅在远离所述安装孔处增大， 在靠近所述安装孔处减小。 这样， 可以减小波纹翅片壁面上的流体流动切应力， 因此可以起到进一步减小流动阻力 的作用。
如图 1所示， 在确定波纹区域边界 8后， 流线型凸波纹 11与凹波纹 12按照流函数 值按需在波纹区边界 8之间相间分布，且凸波纹 11和凹波纹 12沿安装孔 2的横向中心 线和纵向中心线对称分布， 其中， 横向中心线是指图 1中由左至右穿过安装孔 2中心的 直线， 纵向中心线是指图 1中由下至上穿过安装孔 2中心的直线， 这样使得流体流动速 度较为均匀， 减小流动压力损失， 提高翅片换热能力。
如图 1所示， 安装孔 2在翅片本体 1上设置有多个， 多个安装孔 2可以采用顺排方 式设置， 即多个安装孔 2的中心点处于同一水平线上； 或者也可以采用叉排方式设置， 即多个安装孔 2的中心点不处于同一水平线上。 沿安装孔 2—侧边缘设有环状凸台 9， 在波纹翅片与圆管安装时，后一波纹翅片前部突出的的环状凸台 9顶抵于前一波纹翅片 的后部， 从而限制流线型波纹翅片间距， 达到翅片定位的作用。
如图 3所示，环状凸台 9的顶部略往外翻有一翻边 10，便于翅片穿管和确定翅片片 距。 在本发明中， 环状凸台 9的高度可以根据翅片间距变化设计成不同的尺寸， 在安装 时， 胀管或悍接后环状凸台 9与管束紧密接触， 起到固定波纹翅片， 减小热阻的作用。
进一步的，凸波纹 11和凹波纹 12的最大波幅为翅片间距（即环状凸台高度）的 0. 1〜 0. 9倍。
进一步的， 凸波纹 11和凹波纹 12的表面为光滑表面， 结合凸波纹 11和凹波纹 12 的流线型结构， 在使用中不易挂灰尘， 进一步降低了翅片侧热阻， 提高了翅片的传热性 能。
图 6至图 10为本发明管翅式换热器流线型波纹翅片实施例二的示意图。 本实施例 与实施例一的结构和作用大体相同， 不同之处在于， 本实施例中采用的安装孔 2为椭圆 孔， 以适应横截面为椭圆形的管束。
在本发明波纹翅片冲压成型后， 将波纹翅片套装在圆管或椭圆管上， 波纹翅片间通 过带有翻边 10的环状凸台 9定位， 通过胀管 /悍接、 管内试压等一系列工艺完成整个管 翅式换热器的制作。
本发明流线型波纹翅片的工作原理是： 当流体（气流）在流线型波纹翅片之间的气 流通道内流动时，流体通过翅片表面的流线型凸波纹 11和凹波纹 12的连续不断的引导， 部分在凸波纹 11和凹波纹 12形成的流线型通道内流动， 从而流动平稳， 流量分配较为 均匀， 有效抑制了圆管 /椭圆管尾部 （管尾部是指按气流流动方向当气流流动横掠圆管 时圆管下游处） 流体的脱体， 明显减小了流动压力损失。 同时， 凸波纹 11和凹波纹 12 增加了翅片表面积、 减小了翅片侧传热热阻， 且流体流线型流动使得管束后不易产生回 流区， 管尾部翅片的换热性能也得到明显提高。 以上发明使得流线型波纹翅片具有较好 的流动与传热性能， 且使翅片在使用中不易挂灰尘， 保持散热性能的稳定性。
针对上述各实施方式的详细解释， 其目的仅在于对本发明进行解释， 以便于能够更 好地理解本发明， 但是， 这些描述不能以任何理由解释成是对本发明的限制， 特别是， 在不同的实施方式中描述的各个特征也可以相互任意组合， 从而组成其他实施方式， 除 了有明确相反的描述， 这些特征应被理解为能够应用于任何一个实施方式中， 而并不仅 局限于所描述的实施方式。

Claims

权利要求书
1、 一种管翅式换热器流线型波纹翅片， 包括翅片本体， 所述翅片本体的一侧端为 气流入口，其另一侧端为气流出口，在所述的翅片本体上布设有用于安装管束的安装孔， 其特征在于，在所述翅片本体上按照气流流线走向从所述气流入口至所述气流出口连续 形成若干条间隔设置的凸波纹和凹波纹， 同一所述凸波纹的波峰连线与相邻的同一所述 凹波纹的波谷连线均为流线。
2、 如权利要求 1所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述流线是 翅片本体所对应管翅式换热器平片翅片侧通道管轴向中心截面上管尾不出现回流的流 线。
3、 如权利要求 1所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹 与所述凹波纹设置于所述翅片本体上设定的波纹区域边界内，所述波纹区域边界位于所 述安装孔的上下两侧， 所述波纹区域边界均是流线， 以其流函数值按需确定， 所述凸波 纹的波峰连线与相邻的凹波纹的波谷连线之间的间距或所述凸波纹和所述凹波纹设置 数量依据区域边界流函数值按需确定。
4、 如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹和所述凹波纹的横断面呈所需型线， 比如， 折线形、 正弦波形、 抛物线形或 圆弧形。
5、 如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片， 其特征在于， 每条所述凸波纹和每条所述凹波纹的波幅为固定值。
6、 如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片， 其特征在于， 每条所述凸波纹和每条所述凹波纹的波幅沿纵向呈波形曲线分布。
7、 如权利要求 6所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹 和所述凹波纹的波幅在所述气流流速大的区域减小， 在所述气流流速小的区域增大。
8、 如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹和所述凹波纹的波幅沿横向相等。
9、 如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹和所述凹波纹的波幅沿横向不等。
10、 如权利要求 9所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波纹 的波幅和所述凹波纹的波幅分别在远离所述安装孔处增大， 在靠近所述安装孔处减小。
11、如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片，其特征在于， 所述凸波纹和所述凹波纹分别以所述安装孔的横向中心线和纵向中心线对称分布。
12、如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片，其特征在于， 沿所述安装孔一侧边缘设有用于限制流线型波纹翅片间距的环状凸台，所述环状凸台的 顶部外翻有一翻边。
13、 如权利要求 12所述的管翅式换热器流线型波纹翅片， 其特征在于， 所述凸波 纹和所述凹波纹的最大波幅为所述环状凸台高度的 0. 1〜0. 9倍。
14、如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片，其特征在于， 所述安装孔为圆孔或椭圆孔。
15、如权利要求 1至 3中任一项所述的管翅式换热器流线型波纹翅片，其特征在于， 所述凸波纹和所述凹波纹的表面为光滑表面。
PCT/CN2014/083506 2014-08-01 2014-08-01 管翅式换热器流线型波纹翅片 Ceased WO2016015324A1 (zh)

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KR1020167015869A KR101817553B1 (ko) 2014-08-01 2014-08-01 휜앤 튜브형 열교환기의 스트림라인 파형 휜
US15/104,926 US10982912B2 (en) 2014-08-01 2014-08-01 Streamlined wavy fin for finned tube heat exchanger
EP14898379.4A EP3104111B1 (en) 2014-08-01 2014-08-01 Streamline wavy fin for finned tube heat exchanger
JP2016541683A JP6200598B2 (ja) 2014-08-01 2014-08-01 フィンチューブ式熱交換器の予め設定された流線型のウェイビーフィン

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109470077A (zh) * 2017-09-08 2019-03-15 美的集团股份有限公司 翅片和换热器
WO2026091384A1 (zh) * 2024-10-28 2026-05-07 广东美的制冷设备有限公司 换热装置及空气调节装置

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6548324B2 (ja) * 2015-06-30 2019-07-24 東京ラヂエーター製造株式会社 熱交換器のインナーフィン
US11313630B2 (en) * 2016-07-01 2022-04-26 Mitsubishi Electric Corporation Heat exchanger and refrigeration cycle apparatus having heat exchanger
JP7031524B2 (ja) * 2018-07-27 2022-03-08 日本軽金属株式会社 冷却器
CN109944677B (zh) * 2019-03-01 2024-03-01 冀凯河北机电科技有限公司 一种空气发动机用新型发动机翅片
CN109883238A (zh) * 2019-03-08 2019-06-14 西安交通大学 一种板翅式热交换器芯体及其翅片结构
JP7150157B2 (ja) * 2019-05-07 2022-10-07 三菱電機株式会社 熱交換器および冷凍サイクル装置
CN110207530B (zh) * 2019-05-24 2020-06-12 西安交通大学 一种采用双向离散凸起的高强度换热翅片
CN111997965B (zh) * 2020-08-27 2022-09-27 中国石油天然气股份有限公司 一种稳流器
CN113153536A (zh) * 2021-04-28 2021-07-23 浙江意动科技股份有限公司 一种燃气涡轮用回热器
US20250189234A1 (en) * 2023-12-11 2025-06-12 Baltimore Aircoil Company, Inc. Heat exchanger

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3515207A (en) * 1968-07-17 1970-06-02 Perfex Corp Fin configuration for fin and tube heat exchanger
JPS59210296A (ja) * 1984-04-20 1984-11-28 Matsushita Electric Ind Co Ltd フイン付熱交換器
WO2006004009A1 (ja) * 2004-06-30 2006-01-12 Daikin Industries, Ltd. 熱交換器及び空気調和装置
WO2007013623A1 (ja) * 2005-07-29 2007-02-01 The University Of Tokyo 熱交換器およびこれを用いた空気調和装置並びに空気性状変換器
CN103759566A (zh) * 2013-12-30 2014-04-30 中山职业技术学院 一种变频co2热泵热水器波纹翅片换热器的设计方法

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1915742A (en) * 1930-11-28 1933-06-27 Manuf Generale Metallurg Sa Heat exchange apparatus
US1920313A (en) * 1930-11-28 1933-08-01 Manuf Generale Metallurg Sa Heat exchange apparatus
US3645330A (en) * 1970-02-05 1972-02-29 Mcquay Inc Fin for a reversible heat exchanger
DE2428042C3 (de) * 1973-06-14 1978-06-15 Igor Martynovitsch Kalnin Röhrenwärmeaustauscher
JPS6334393B2 (zh) * 1979-06-20 1988-07-11 Efujenii Urajimirobitsuchi Deyuburofusukii
JPS59210298A (ja) * 1984-04-20 1984-11-28 Matsushita Electric Ind Co Ltd フイン付熱交換器
JPS61153498A (ja) * 1984-12-27 1986-07-12 Matsushita Electric Ind Co Ltd フイン付熱交換器
US5168923A (en) * 1991-11-07 1992-12-08 Carrier Corporation Method of manufacturing a heat exchanger plate fin and fin so manufactured
US5927393A (en) * 1997-12-11 1999-07-27 Heatcraft Inc. Heat exchanger fin with enhanced corrugations
US7261147B2 (en) * 2003-05-28 2007-08-28 Lg Electronics Inc. Heat exchanger
US6889759B2 (en) * 2003-06-25 2005-05-10 Evapco, Inc. Fin for heat exchanger coil assembly
JP5077926B2 (ja) 2007-01-25 2012-11-21 国立大学法人 東京大学 熱交換器
JP6194471B2 (ja) 2012-12-25 2017-09-13 パナソニックＩｐマネジメント株式会社 フィンチューブ熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3515207A (en) * 1968-07-17 1970-06-02 Perfex Corp Fin configuration for fin and tube heat exchanger
JPS59210296A (ja) * 1984-04-20 1984-11-28 Matsushita Electric Ind Co Ltd フイン付熱交換器
WO2006004009A1 (ja) * 2004-06-30 2006-01-12 Daikin Industries, Ltd. 熱交換器及び空気調和装置
WO2007013623A1 (ja) * 2005-07-29 2007-02-01 The University Of Tokyo 熱交換器およびこれを用いた空気調和装置並びに空気性状変換器
CN103759566A (zh) * 2013-12-30 2014-04-30 中山职业技术学院 一种变频co2热泵热水器波纹翅片换热器的设计方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109470077A (zh) * 2017-09-08 2019-03-15 美的集团股份有限公司 翅片和换热器
WO2026091384A1 (zh) * 2024-10-28 2026-05-07 广东美的制冷设备有限公司 换热装置及空气调节装置

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JP6200598B2 (ja) 2017-09-20
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EP3104111A1 (en) 2016-12-14
US20160320147A1 (en) 2016-11-03
US10982912B2 (en) 2021-04-20
EP3104111B1 (en) 2021-01-27
KR101817553B1 (ko) 2018-02-21
EP3104111A4 (en) 2017-03-15

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