Cooling fin and tubular heat exchanger

Abstract

The invention belongs to the field of heat exchangers, and particularly relates to a radiating fin and a tubular heat exchanger, the radiating fin comprises a square straight fin, a plurality of radiating units are arranged on the straight fin, and each radiating unit comprises a vortex generator set. Each vortex generator set comprises two round protrusions, two first oval protrusions and two second oval protrusions, the two round protrusions, the two first oval protrusions and the two second oval protrusions are arranged in a parabola structure and are symmetrical along the axis of the parabola structure, an opening hole is formed in an opening of each vortex generator set, and the two first oval protrusions and the two second oval protrusions are arranged in the parabola structure and are symmetrical along the axis of the parabola structure. The hole is used for allowing the heat exchange tube to penetrate through, the two round protrusions are located at the inwards-concave position of the parabola structure, the two first oval protrusions and the two second oval protrusions are located on the two sides of the parabola structure respectively, and the first oval protrusions are located between the second oval protrusions and the round protrusions. The heat exchange efficiency can be improved, energy consumption can be reduced, and the size and cost of equipment can be reduced.

Description

Technical Field

[0001] The invention belongs to the field of heat exchangers, and in particular relates to a heat dissipation fin and a tube-type heat exchanger. Background Art

[0002] In modern industry and construction, fin-tube heat exchangers are widely used due to their efficient heat exchange capabilities. Traditional fin-tube heat exchangers improve heat exchange efficiency by adding fins to the surface of the pipe, but there are certain limitations. For example, the heat transfer coefficient of the smooth tube wall is low, especially in applications with low temperature differences or high viscosity fluids, the heat transfer efficiency is difficult to meet the needs of industrial production. In order to solve this problem, researchers have proposed a variety of fin designs, such as longitudinal fins, transverse fins, corrugated fins, etc., which increase the contact area between the fluid and the tube wall and enhance the turbulence of the fluid, thereby improving the heat transfer efficiency. However, these designs have shortcomings in terms of manufacturing cost, installation complexity, maintenance difficulty, etc., and under specific working conditions, the improvement of heat transfer performance is not obvious. Summary of the invention

[0003] In order to solve the above technical problems, the present invention provides a heat dissipation fin and a tube heat exchanger, which can further improve the heat exchange efficiency, reduce energy consumption, and reduce the size and cost of the equipment.

[0004] The technical solution of the present invention includes a square straight fin, on which a plurality of heat dissipation units are arranged, each heat dissipation unit includes a vortex generator group, each vortex generator group includes two circular protrusions, two first elliptical protrusions and two second elliptical protrusions, the two circular protrusions, the two first elliptical protrusions and the two second elliptical protrusions are arranged in a parabolic structure and are symmetrical along the axis of the parabolic structure, an opening is provided at the opening of each vortex generator group, the opening allows the heat exchange tube to pass through, the two circular protrusions are both located in the inner recess of the parabolic structure, the two first elliptical protrusions and the two second elliptical protrusions are respectively located on both sides of the parabolic structure, and the first elliptical protrusion is located between the second elliptical protrusion and the circular protrusion.

[0005] Furthermore, a plurality of heat dissipation units are arranged in an array, and heat dissipation units in two adjacent rows are staggered with each other.

[0006] Furthermore, the length:width ratio of the straight fin is between 2 and 4.5:1, the thickness of the straight fin is between 0.0024 times and 0.003 times the width, the diameters of the two round protrusions are both between 0.021 times and 0.025 times the width of the straight fin, the major axis:minor axis ratio of the two first elliptical protrusions is both between 2.1 and 2.9:1, the major axis:minor axis ratio of the two first elliptical protrusions is both between 0.12 and 1.2:1, the major axis:minor axis ratio of the two second elliptical protrusions is both between 3.6 and 4.2:1, and the major axis:minor axis ratio of the two second elliptical protrusions is both between 1.6 and 2.4:1.

[0007] Furthermore, the spacing between the two circular protrusions is between 2 times and 2.4 times the diameter of the circular protrusion, the spacing between the circular protrusion and the first elliptical protrusion on the same side of the parabolic structure is between 2.9 times and 3.4 times the diameter of the circular protrusion, the spacing between the first elliptical protrusion and the second elliptical protrusion on the same side of the parabolic structure is between 4.1 times and 4.9 times the diameter of the circular protrusion, the spacing between the two first elliptical protrusions is between 6 times and 7 times the diameter of the circular protrusion, and the spacing between the two second elliptical protrusions is between 10 times and 11 times the diameter of the circular protrusion.

[0008] Furthermore, the major axis of the first elliptical protrusion on the same side of the parabola structure is collinear with the line connecting the center of the first elliptical protrusion and the center of the circular protrusion, and the major axis of the second elliptical protrusion on the same side of the parabola structure is collinear with the line connecting the center of the second elliptical protrusion and the center of the first elliptical protrusion.

[0009] Furthermore, the thickness of the two first elliptical protrusions, the two second elliptical protrusions and the two round protrusions is between 0.0048 times and 0.0056 times the width of the straight fin.

[0010] The present invention also provides a tubular heat exchanger, comprising a plurality of heat exchange tubes and heat dissipation fins, wherein the plurality of heat exchange tubes pass through the plurality of openings in a one-to-one correspondence, and the plurality of heat exchange tubes are all connected to the straight fins.

[0011] Furthermore, there are a plurality of straight fins, and the plurality of straight fins are arranged in sequence along the length direction of the heat exchange tube.

[0012] Furthermore, the cross-section of the heat exchange tube is circular, the inner diameter of the heat exchange tube is between 0.14 times and 0.18 times the width of the straight fin, the side wall thickness of the heat exchange tube is between 0.012 times and 0.036 times the width of the straight fin, the spacing between the center of the two first elliptical protrusions and the center of the heat exchange tube is between 0.8 times and 1 times the inner diameter of the heat exchange tube, and the spacing between the center of the two second elliptical protrusions and the center of the heat exchange tube is between 0.6 times and 0.9 times the inner diameter of the heat exchange tube.

[0013] Furthermore, the distance between two adjacent heat exchange tubes in the transverse direction is between 2.5 times and 2.9 times the diameter of the heat exchange tubes, and the distance between two adjacent heat exchange tubes in the longitudinal direction is between 1.6 times and 2.1 times the diameter of the heat exchange tubes.

[0014] Furthermore, the distance between two adjacent straight fins is between 0.08 times and 0.12 times the width of the straight fins.

[0015] The technical solution provided by the embodiment of the present invention has the following advantages compared with the prior art:

[0016] The second elliptical protrusion of the present invention is located at the opening of the vortex generator group. When the fluid passes through the fin, it first encounters the second elliptical protrusion. The second elliptical protrusion can divert a part of the fluid to between the vortex generator group and the heat exchange tube, and generate vortices between the vortex generator group and the heat exchange tube. Such vortices can enhance the disturbance of the fluid, thereby destroying the thermal boundary layer, thereby increasing the volume of fluid for heat exchange between the heat exchange tubes. Secondly, the fluid flows to the first elliptical protrusion. The first elliptical protrusion can make the fluid stay longer around the first elliptical protrusion and the heat exchange tube, thereby enhancing the heat transfer area. Finally, the fluid flows to the circular protrusion. The circular protrusion can retain a part of the fluid and increase its heat exchange time around the heat exchanger. Compared with the prior art, the present invention gathers the fluid around the heat exchange tube through vortices to increase the fluid heat exchange volume, extend the heat exchange time, and thus improve the heat exchange efficiency.

[0017] Other advantages, objectives and features of the present invention will be embodied in part through the following description, and in part will be understood by those skilled in the art through study and practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0019] Figure 1 This is a schematic diagram of the structure of a heat dissipation unit in one embodiment of the present invention;

[0020] Figure 2 A schematic diagram of a heat pipe array structure of a radiator according to one embodiment of the present invention;

[0021] Figure 3 This is a diagram showing the vortex effect generated between the vortex generator group and the heat exchange tube in one embodiment of the present invention;

[0022] Figure 4 for Figure 3 Enlarged view of point A in the middle;

[0023] Figure 5 for Figure 3 Enlarged view of point B in the middle;

[0024] Figure 6 for Figure 3 Enlarged view of center C.

[0025] Reference numerals:

[0026] 1. Round protrusion; 2. First elliptical protrusion; 3. Second elliptical protrusion; 4. Straight fin; 5. Heat exchange tube; 6. Heat dissipation unit. DETAILED DESCRIPTION

[0027] A specific implementation of the present invention is described in detail below in conjunction with the accompanying drawings, but it should be understood that the protection scope of the present invention is not limited by the specific implementation.

[0028] In the description of the present invention, it is to be understood that the terms “center”, “longitudinal”, “lateral”, “length”, “width”, “thickness”, “up”, “down”, “front”, “back”, “left”, “right”, “vertical”, “horizontal”, “top”, “bottom”, “inside”, “outside”, “axial”, “radial”, “circumferential”, etc., indicating orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, are only for the convenience of describing the technical solutions of the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0029] In the description of the embodiments of the present invention, unless otherwise specified, “plurality” means two or more.

[0030] In recent years, fin-tube heat exchangers with vortex generators have attracted widespread attention as a new type of heat exchanger structure. Vortex generators can enhance convective heat transfer in addition to the horseshoe-shaped vortex naturally formed around the tube by artificially generating longitudinal vortices on the fin surface. Studies have shown that under different Reynolds numbers, the heat transfer factor j of fin-tube heat exchangers with vortex generators increased by 2.9% to 4.0%, the resistance factor f increased by 1.6% to 2.0%, and the comprehensive performance factor JF increased by 2.2% to 3.4% compared with traditional fins, showing superior heat transfer performance.

[0031] In addition, the geometric changes of vortex generators have a significant impact on the thermo-fluid performance. For example, the Delta winglet vortex generator outperforms the rectangular winglet vortex generator in terms of heat transfer performance, while the hole-type rectangular winglet shows a promising thermo-fluid performance improvement of more than 16%. These studies show that fin-tube heat exchangers with vortex generators have great potential in improving heat transfer efficiency and reducing energy consumption.

[0032] In summary, although existing fin-tube heat exchangers have been widely used in multiple industries, there is still room for improvement in improving heat transfer efficiency and reducing energy consumption.

[0033] like Figures 1 to 6 As shown, the present invention provides a heat dissipation fin, including a square straight fin 4, the length: width ratio of the straight fin 4 is between 2 and 4.5:1, the thickness of the straight fin 4 is between 0.0024 times and 0.003 times the width, and a plurality of heat dissipation units 6 are arranged on the straight fin 4, each heat dissipation unit 6 includes a vortex generator group, each vortex generator group includes two circular protrusions 1, two first elliptical protrusions 2 and two second elliptical protrusions 3, the two circular protrusions 1, the two first elliptical protrusions 2 and the two second elliptical protrusions 3 are arranged in a parabolic structure and are symmetrical along the axis of the parabolic structure, an opening is provided at the opening of each vortex generator group, and the opening allows a heat exchange tube 5 to pass through, the two circular protrusions 1 are both located at the inner concave part of the parabolic structure, the two first elliptical protrusions 2 and the two second elliptical protrusions 3 are respectively located on both sides of the parabolic structure, and the first elliptical protrusion 2 is located between the second elliptical protrusion 3 and the circular protrusion 1.

[0034] The second elliptical protrusion 3 of the present invention is located at the opening of the vortex generator group. When the fluid passes through the fin, it first encounters the second elliptical protrusion 3. The second elliptical protrusion 3 can divert a part of the fluid to between the vortex generator group and the heat exchange tube 5, and generate vortices between the vortex generator group and the heat exchange tube 5. This vortex can enhance the disturbance of the fluid, thereby destroying the thermal boundary layer, thereby increasing the volume of fluid exchanged between the heat exchange tubes 5 and the heat exchange tubes 5. Secondly, the fluid flows to the first elliptical protrusion 2. The first elliptical protrusion 2 can make the fluid stay longer around the first elliptical protrusion 2 and the heat exchange tube 5, thereby enhancing the heat transfer area. Finally, the fluid flows to the circular protrusion 1. The circular protrusion 1 can retain a part of the fluid and increase its heat exchange time around the heat exchanger. Compared with the prior art, the present invention gathers the fluid around the heat exchange tube through vortices to increase the fluid heat exchange volume, extend the heat exchange time, and thus improve the heat exchange efficiency.

[0035] In the embodiment provided by the present invention, a plurality of heat dissipation units 6 are arranged in an array, and the heat dissipation units 6 in two adjacent rows are staggered with each other. The staggered arrangement has the following advantages:

[0036] A. Increase disturbance: When fluids such as air or coolant pass through the heat exchanger, if the heat exchange tubes 5 are arranged in a straight line, the fluid may flow along a smoother path, resulting in the formation of a boundary layer (i.e., a thin layer of fluid close to the solid surface), which will reduce the heat exchange efficiency; while the staggered arrangement can destroy the boundary layer of the heat exchange tubes 5, making the fluid more turbulent, thereby increasing the contact opportunity and heat exchange between the fluid and the wall of the heat exchange tubes 5.

[0037] B. Optimize fluid distribution: Staggered arrangement can help ensure uniform distribution of fluid throughout the heat exchanger and avoid "dead zones" in certain areas, that is, areas with extremely low or even no flow, which usually lead to increased thermal resistance and affect the efficiency of the entire system.

[0038] In the embodiment provided by the present invention, the spacing between the two circular protrusions 1 is between 2 times and 2.4 times the diameter of the circular protrusion 1, the spacing between the circular protrusion 1 and the second elliptical protrusion 3 on the same side of the parabola structure is between 2.9 times and 3.4 times the diameter of the circular protrusion 1, the spacing between the first elliptical protrusion 2 and the second elliptical protrusion 3 on the same side of the parabola structure is between 4.1 times and 4.9 times the diameter of the circular protrusion 1, the spacing between the two first elliptical protrusions 2 is between 6 times and 7 times the diameter of the circular protrusion 1, and the spacing between the two second elliptical protrusions 3 is between 10 times and 11 times the diameter of the circular protrusion 1.

[0039] The advantage of setting the distance between the two circular protrusions 1 is that a part of the fluid forms a local vortex in the two circular protrusions 1, while not excessively affecting the flow of the remaining fluid to the next heat exchange tube 5.

[0040] The benefits of setting the distance between the circular protrusion 1 and the first elliptical protrusion 2 are: enhancing turbulence, reducing thermal resistance, accelerating heat transfer, and optimizing the film heat transfer coefficient.

[0041] The advantage of setting the distance between the first elliptical protrusion 2 and the second elliptical protrusion 3 is that when the fluid flows through the elliptical protrusion, a local vortex can be generated between the vortex generator and the heat exchange tube 5, thereby enhancing heat exchange.

[0042] In the embodiment provided by the present invention, the ratio range of the major axis:minor axis of the two first elliptical protrusions 2 is between 2.1 and 2.9:1, the ratio range of the major axis:minor axis of the two first elliptical protrusions 2:diameter of the circular protrusion 1 is between 0.12 and 1.2:1, the ratio range of the major axis:minor axis of the two second elliptical protrusions 3 is between 3.6 and 4.2:1, the ratio range of the major axis:minor axis of the two second elliptical protrusions 3:diameter of the circular protrusion 1 is between 1.6 and 2.4:1, and the diameters of the two circular protrusions 1 are between 0.021 times and 0.025 times the width of the straight fin 4.

[0043] It can be understood that a reasonable aspect ratio design can ensure that the fluid maintains a relatively uniform temperature change when passing through the heat exchanger, preventing the formation of local hot spots or cold spots, which has a positive effect on the overall heat transfer efficiency. Specifically:

[0044] The resistance provided by the thickness of the straight fin 4 is relatively low, which can produce a small pressure drop. Moreover, this thickness will not cause the fin to be too thin, thereby guiding and disturbing the flow of the fluid and reducing turbulence.

[0045] The ratio of the long and short axes of the second elliptical protrusion 3: It is the first vortex generator encountered by the fluid. The ratio of the long and short axes of the second elliptical protrusion 3 is large, that is, the ellipse is "flatter" or "longer". It will produce a stronger directional influence in the fluid and guide the fluid to flow in a specific direction. The main purpose is to make more fluid form a more regular vortex structure and form a stronger directional vortex.

[0046] The first elliptical protrusion 2 has a ratio of the major axis to the minor axis: it is the second type of vortex generator encountered by the fluid, which is lower than the ratio of the major axis to the minor axis of the first elliptical protrusion 2. It is designed to produce more random and intense local turbulence, break the boundary layer more evenly, and make the mixing between the various parts of the fluid more complete. This shape will promote more disordered turbulence, make the temperature distribution inside the fluid more uniform, and better destroy the boundary layer, improving the overall heat exchange efficiency.

[0047] The benefit of setting the diameter of the circular protrusion 1 is that it is the third vortex generator encountered by the fluid, and its purpose is to extend the heat exchange time around the heat exchange tube 5 without affecting the continued flow of the fluid. While ensuring sufficient turbulence intensity, it reduces the local stress concentration generated when the fluid passes through and minimizes additional pressure loss.

[0048] In the embodiment provided by the present invention, the major axis of the first elliptical protrusion 2 on the same side of the parabola structure is collinear with the line connecting the center of the first elliptical protrusion 2 and the center of the circular protrusion 1. The major axis of the second elliptical protrusion 3 on the same side of the parabola structure is collinear with the line connecting the center of the second elliptical protrusion 3 and the center of the first elliptical protrusion 2.

[0049] The long axis of the first elliptical protrusion 2 is colinear with the line connecting the center of the ellipse and the center of the circular protrusion 1: the circular protrusion 1 and the first elliptical protrusion 2 play a better cooperation role and jointly form the vertex area of ​​the parabola structure. At the same time, part of the fluid stays around the heat exchange tube 5 for a longer time, and will not affect the remaining fluid to continue to pass through the fins along the incoming flow direction to continue heat exchange around the next heat exchange tube 5.

[0050] The major axis of the second elliptical protrusion 3 is tangent to the first elliptical protrusion 2, so that the second elliptical protrusion 3 and the first elliptical protrusion 2 can cooperate better and form an opening area of ​​a parabolic structure together, and at the same time, part of the fluid stays around the heat exchange tube 5 for a longer time.

[0051] In the embodiment provided by the present invention, the thickness of the two first elliptical protrusions 2 , the two second elliptical protrusions 3 , and the two round protrusions 1 are all between 0.0048 times and 0.0056 times the width of the straight fin 4 .

[0052] The thickness is set to generate local eddy currents around the heat exchange tube 5 without increasing the pressure drop, thereby enhancing the heat exchange, and will not excessively affect the remaining fluid from continuing to pass through the fins along the incoming flow direction to continue the heat exchange around the next heat exchange tube 5.

[0053] like Figure 2 As shown, the present invention further provides a tubular heat exchanger including a plurality of heat exchange tubes 5 and heat dissipation fins, wherein the plurality of heat exchange tubes 5 pass through a plurality of openings in a one-to-one correspondence, and the plurality of heat exchange tubes 5 are all connected to the straight fins 4 .

[0054] Furthermore, the vortex generator group is located downstream of the heat exchange tube 5 in the wind direction, and can divert the fluid to between the vortex generator combined heat exchange tubes 5 through the vortex generator group to form a vortex area to facilitate heat exchange on the heat exchange tube 5.

[0055] In the embodiment provided by the present invention, the cross-section of the heat exchange tube 5 is circular, the inner diameter of the heat exchange tube 5 is between 0.14 times and 0.18 times the width of the straight fin 4, the side wall thickness of the heat exchange tube 5 is between 0.012 times and 0.036 times the width of the straight fin 4, the spacing distance between the center of the two first elliptical protrusions 2 and the center of the heat exchange tube 5 is between 0.8 times and 1 times the inner diameter of the heat exchange tube 5, and the spacing between the center of the two second elliptical protrusions 3 and the center of the heat exchange tube 5 is between 0.6 times and 0.9 times the inner diameter of the heat exchange tube 5.

[0056] The cross section of the heat exchange tube 5 is circular: the circular cross section has a uniform pressure distribution characteristic when subjected to internal pressure, which can minimize stress concentration and provide better pressure resistance. This means that the circular pipe can more effectively resist the internal fluid pressure without deformation or rupture. At the same time, the symmetry of the circular cross section makes the heat transfer more uniform, avoiding the problem of local thermal resistance caused by irregular shape. In addition, the fluid flow in the circular pipe is usually more stable, which is conducive to the formation of effective turbulence and enhances the heat exchange effect.

[0057] The benefits of setting the ratio of the inner diameter of the heat exchange tube 5 to the fin width: The inner diameter of the heat exchange tube 5 and the fin width are two interrelated key design parameters that jointly affect the overall performance of the tubular heat exchanger. Such a ratio can balance the heat exchange efficiency, pressure loss, manufacturing cost and maintenance convenience, ensuring that the economy and reliability are achieved while meeting the functional requirements.

[0058] Advantages of setting the ratio of the side wall thickness of the heat exchange tube 5: The side wall thickness of the heat exchange tube 5 and the fin width are designed in coordination. The purpose of such a ratio setting is to achieve the best possible heat exchange efficiency and mechanical performance.

[0059] The advantage of setting the distance between the second elliptical protrusion 3 and the heat exchange tube 5 is that the second elliptical protrusion 3 is the first vortex generator encountered by the fluid, and the distance from the heat exchange tube 5 is to allow more fluid to form vortices around the heat exchange tube 5 along the second elliptical protrusion 3. This setting can effectively generate appropriate turbulence intensity in the fluid, thereby destroying the boundary layer, increasing the contact opportunity between the fluid and the surface of the heat exchange tube 5, and improving the heat exchange efficiency.

[0060] The advantage of setting the distance between the first elliptical protrusion 2 and the heat exchange tube 5 is that the first elliptical protrusion 2 is the second vortex generator encountered by the fluid, and the distance to the heat exchange tube 5 is close to allow the fluid led here by the second elliptical protrusion 3 to better exchange heat with the heat exchange tube 5. If the distance is too large, the effect of the vortex generator may be weakened, and the boundary layer cannot be fully broken, thereby reducing the heat exchange efficiency.

[0061] The second elliptical protrusion 3 and the first elliptical protrusion 2 can cooperate better to form an inner area of ​​the parabolic structure. At the same time, part of the fluid can stay around the heat exchange tube 5 for a longer time, thereby improving the heat exchange efficiency and forming a local vortex around the heat exchange tube 5. The fluid close to the wall is mixed with the fluid far from the wall, thereby enhancing the heat exchange between the cold and hot flows.

[0062] In the embodiment provided by the present invention, the distance between two adjacent heat exchange tubes 5 in the transverse direction is between 2.5 times and 2.9 times the diameter of the heat exchange tube 5 , and the distance between two adjacent heat exchange tubes 5 in the longitudinal direction is between 1.6 times and 2.1 times the diameter of the heat exchange tube 5 .

[0063] The lateral spacing set in this way can ensure that the fluid has enough space to flow when passing through the heat exchange tube 5, avoiding local high-speed and low-speed areas caused by overcrowding, helping to maintain a relatively uniform flow velocity distribution and reduce fluid resistance.

[0064] The longitudinal spacing set in this way can effectively promote the turbulence of the fluid, destroy the boundary layer, increase the contact opportunity between the fluid and the wall of the heat exchange tube 5, and thus improve the heat transfer efficiency. At the same time, the longitudinal spacing is smaller than the transverse spacing to avoid wasting space and form a compact design.

[0065] In the embodiment provided by the present invention, there are a plurality of straight fins 4 , which are sequentially arranged along the length direction of the heat exchange tube 5 , and the distance between two adjacent straight fins 4 is between 0.08 and 0.12 times the width of the straight fin 4 .

[0066] The spacing between the straight fins 4 can ensure that the fluid maintains a relatively uniform temperature gradient when flowing through the heat exchanger, prevent the formation of local hot spots or cold spots, and improve the overall heat exchange efficiency.

[0067] The present invention can make the fluid easier to generate local vortices, effectively disrupt the boundary layer, and mix the fluid near the wall with the fluid far from the wall. This mixing promotes heat exchange because the temperature difference between the high temperature zone and the low temperature zone is more effectively utilized. Due to the change in the flow state of the fluid, the effective area actually involved in heat exchange increases, and the area that may have been at a lower heat exchange efficiency now becomes more active and participates in a more efficient heat transfer process, forming multiple local vortices around the heat exchange tube 5, effectively enhancing heat exchange.

[0068] It should be noted that, in this article, the terms "include", "comprises" or any other variations thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, an element defined by the sentence "comprises a ..." does not exclude the existence of other identical elements in the process, method, article or device including the element.

[0069] Although the embodiments of the present invention have been disclosed above, they are not limited to the applications listed in the specification and the embodiments. It can be fully applied to various fields suitable for the present invention. For those familiar with the art, additional modifications can be easily realized. Therefore, without departing from the general concept defined by the claims and equivalent scope, the present invention is not limited to the specific details and the illustrations shown and described here.

Claims

1. A heat dissipation fin, characterized in that: The invention comprises a square straight fin (4), wherein a plurality of heat dissipation units (6) are arranged on the straight fin (4), wherein each heat dissipation unit (6) comprises a vortex generator group, wherein the vortex generator group comprises two circular protrusions (1), two first elliptical protrusions (2) and two second elliptical protrusions (3), wherein the two circular protrusions (1), the two first elliptical protrusions (2) and the two second elliptical protrusions (3) are arranged in a parabolic structure and are symmetrical along the axis of the parabolic structure, and an opening is arranged at the opening of the parabolic structure, wherein the opening allows a heat exchange tube (5) to pass through; The two circular protrusions (1) are both located at the inner concave part of the parabolic structure, the two first elliptical protrusions (2) and the two second elliptical protrusions (3) are both located at two sides of the parabolic structure, and the first elliptical protrusion (2) is located between the second elliptical protrusion (3) and the circular protrusion (1).

2. A heat dissipation fin according to claim 1, characterized in that: A plurality of the heat dissipation units (6) are arranged in an array, and the heat dissipation units (6) in two adjacent rows are staggered with respect to each other.

3. A heat dissipation fin according to claim 2, characterized in that: The length:width ratio of the straight fin (4) is in the range of 2 to 4.5:1, and the thickness of the straight fin (4) is in the range of 0.0024 to 0.003 times the width; The diameters of the two circular protrusions (1) are both between 0.021 and 0.025 times the width of the straight fin (4); The ratio of the major axis to the minor axis of the two first elliptical protrusions (2) is between 2.1 and 2.9:1, and the ratio of the major axis to the diameter of the circular protrusion (1) is between 0.12 and 1.2:

1. The ratio of the major axis to the minor axis of the two second elliptical protrusions (3) is between 3.6 and 4.2:1, and the ratio of the major axis to the diameter of the circular protrusion (1) is between 1.6 and 2.4:

1.

4. A heat dissipation fin according to claim 3, characterized in that: The spacing between the two circular protrusions (1) is between 2 and 2.4 times the diameter of the circular protrusion (1); the spacing between the circular protrusion (1) and the first elliptical protrusion (2) on the same side of the parabolic structure is between 2.9 and 3.4 times the diameter of the circular protrusion (1); the spacing between the first elliptical protrusion (2) and the second elliptical protrusion (3) on the same side of the parabolic structure is between 4.1 and 4.9 times the diameter of the circular protrusion (1); the spacing between the two first elliptical protrusions (2) is between 6 and 7 times the diameter of the circular protrusion (1); and the spacing between the two second elliptical protrusions (3) is between 10 and 11 times the diameter of the circular protrusion (1).

5. A heat dissipation fin according to claim 4, characterized in that: The major axis of the first elliptical protrusion (2) on the same side of the parabola structure is collinear with a line connecting the center of the first elliptical protrusion (2) and the center of the circular protrusion (1); The major axis of the second elliptical protrusion (3) on the same side of the parabola structure and the line connecting the center of the second elliptical protrusion (3) and the center of the first elliptical protrusion (2) are collinear.

6. A heat dissipation fin according to claim 5, characterized in that: The thickness of the two first elliptical protrusions (2), the two second elliptical protrusions (3) and the two round protrusions (1) is between 0.0048 times and 0.0056 times the width of the straight fin (4).

7. A tubular heat exchanger, characterized in that: It comprises a plurality of heat exchange tubes (5) and a heat dissipation fin as claimed in any one of claims 2 to 6, wherein the plurality of heat exchange tubes (5) pass through the plurality of openings in a one-to-one correspondence, and the plurality of heat exchange tubes (5) are all connected to the straight fins (4).

8. A tubular heat exchanger according to claim 7, characterized in that: There are a plurality of straight fins (4), and the plurality of straight fins (4) are arranged in sequence along the length direction of the heat exchange tube (5).

9. A tubular heat exchanger according to claim 8, characterized in that: The cross section of the heat exchange tube (5) is circular, the inner diameter of the heat exchange tube (5) is between 0.14 times and 0.18 times the width of the straight fin (4), and the side wall thickness of the heat exchange tube (5) is between 0.012 times and 0.036 times the width of the straight fin (4); The distance between the center of the two first elliptical protrusions (2) and the center of the heat exchange tube (5) is between 0.8 times and 1 times the inner diameter of the heat exchange tube (5), and the distance between the center of the two second elliptical protrusions (3) and the center of the heat exchange tube (5) is between 0.6 times and 0.9 times the inner diameter of the heat exchange tube (5).

10. A tubular heat exchanger according to claim 9, characterized in that: The distance between two adjacent heat exchange tubes (5) in the transverse direction is between 2.5 times and 2.9 times the diameter of the heat exchange tube (5); The distance between two adjacent heat exchange tubes (5) in the longitudinal direction is between 1.6 times and 2.1 times the diameter of the heat exchange tube (5); The distance between two adjacent straight fins (4) is between 0.08 times and 0.12 times the width of the straight fin (4).

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