An integrated corrugated finned tube heat transfer element and heat exchanger

Abstract

The utility model relates to heat exchanger technical field discloses a kind of integral corrugated finned tube heat transfer elements, comprising: integrally processing and shaping finned tube group and heat transfer base pipe;Heat transfer base pipe extends along first direction, and heat transfer base pipe includes first side wall and second side wall being oppositely arranged and arranged along second direction, and first plane and second plane being oppositely arranged and arranged along third direction, first side wall and second side wall are all semicircular;Finned tube group is respectively arranged in the first plane and second plane;Finned tube group is opened m separate grooves along second direction, to separate finned tube group into m+1 finned tube sections, and each finned tube section includes heat dissipation fin being spaced apart and arranged along multiple first direction, and heat dissipation fin in adjacent two finned tube sections is staggered arrangement between them.Its beneficial effect lies in: finned tube group and heat transfer base pipe are integrally formed, and contact thermal resistance between fin and heat transfer base pipe is completely eliminated, and heat dissipation fin is staggered arrangement effectively improves heat transfer efficiency.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, specifically to an integral corrugated finned tube heat transfer element and heat exchanger. Background Technology

[0002] Traditional indirect cooling tower air-cooled systems in power plants typically use round tubes, multi-row finned tubes, or externally wound finned tubes. These finned tubes have separate heat dissipation fins and heat transfer tubes, resulting in significant contact thermal resistance between the fins and the base tube. With prolonged use and seasonal changes in operating conditions—specifically, variations in the temperature of the fluid inside the tubes and the air between the fins—the heat transfer tubes and fins expand and contract with temperature, increasing the contact thermal resistance. This leads to a significant decrease in the heat transfer efficiency of the finned tubes over time, thus reducing the heat dissipation capacity of the indirect cooling tower air-cooled system. While existing integrated heat transfer elements address the contact thermal resistance issue, they enhance heat transfer by abruptly changing the shape of the fins to increase air turbulence, thereby increasing airflow resistance. Consequently, the heat transfer efficiency of the finned tubes does not reach the ideal level. Utility Model Content

[0003] The purpose of this invention is to overcome the shortcomings of the existing technology and provide an integral corrugated finned tube heat transfer element with non-contact thermal resistance and low air flow resistance.

[0004] Another objective of this invention is to provide a heat exchanger having the aforementioned integral corrugated finned tube heat transfer element.

[0005] To achieve the above objectives, this utility model provides the following technical solution:

[0006] An integral corrugated finned tube heat transfer element includes: an integrally formed finned tube assembly and a heat transfer base tube; the heat transfer base tube extends along a first direction, and includes a first sidewall and a second sidewall arranged and opposite to each other along a second direction, and a first plane and a second plane arranged and opposite to each other along a third direction, the two ends of the first sidewall and the second sidewall are connected to the first plane and the second plane, and both the first sidewall and the second sidewall are semi-circular; the finned tube assembly is respectively disposed on the first plane and the second plane; the finned tube assembly has m dividing grooves along the second direction to divide the finned tube assembly into m+1 finned tube segments, each finned tube segment including heat dissipation fins arranged at intervals along multiple first directions, and the heat dissipation fins in adjacent finned tube segments are staggered; along the second direction, each heat dissipation fin includes a first straight section, a corrugated section and a second straight section connected together, so that the straight section can play a rectifying role when air flows in and out of the heat dissipation fin surface, and the first direction, the second direction and the third direction are perpendicular to each other. With the above configuration, the finned tube assembly is directly machined into the first and second planes of the heat transfer base tube, allowing the finned tube assembly and the heat transfer base tube to be integrally formed. This completely eliminates the contact thermal resistance between the fins and the heat transfer base tube, maximizing internal heat transfer within the finned tube and reducing the rate of decrease in heat transfer efficiency over time. The two sidewalls of the heat transfer base tube arranged along the second direction are semi-circular, effectively reducing wind resistance when air flows over the sidewall surface. The finned tube assembly has m dividing slots along the second direction, dividing it into m+1 finned tube segments. Adjacent finned tube segments are designed to be open, and the heat dissipation fins in adjacent segments are arranged in a discontinuous and staggered manner. This repeatedly interrupts the growth of the airflow boundary layer, enhancing the convective heat transfer coefficient between the air and the fins and improving the overall heat transfer capacity of the radiator. The straight sections at both ends of the heat dissipation fins have a rectifying and drag-reducing effect on the air. The air inlet and outlet sections of each heat dissipation fin are designed as straight sections. These straight sections at the inlet and outlet have a rectifying effect on the air entering and exiting the heat dissipation fins, further reducing airflow resistance.

[0007] Furthermore, the heat dissipation fins are generally arc-shaped with a radius of R, and the angle between the heat dissipation fins and the first or second plane is θ, where 0° < θ < 90°. With this configuration, under the same vertical height as traditional fins, the arc-shaped heat dissipation fins increase the heat dissipation area by 2-3%, effectively improving heat transfer efficiency.

[0008] Furthermore, the finned tube assembly and heat transfer base tube are integral aluminum structures. This design effectively reduces the overall weight of the heat transfer elements.

[0009] Furthermore, the inner cavity of the heat transfer base tube is provided with n reinforcing ribs spaced at intervals along the second direction, and each reinforcing rib extends along the first direction to divide the inner cavity of the heat transfer base tube into n+1 fluid channels extending along the first direction. By providing reinforcing ribs, the strength of the heat transfer base tube is improved, making it less prone to freezing and cracking in winter, and extending its service life.

[0010] Furthermore, m = n, the partition groove and the reinforcing rib are arranged opposite each other, and a finned tube section is arranged above and below each fluid channel.

[0011] Furthermore, the length ratio of the first straight section, the corrugated section, and the second straight section is 1:(1.2~3):1. The straight section located at the air inlet and outlet has the effect of rectifying and reducing air resistance, while the corrugated section can increase the disturbance to the flowing air. By optimizing the proportion of each section of the heat dissipation fins, the heat transfer efficiency is improved.

[0012] Furthermore, the length of the partition groove along the second direction is c, and the range of c is 1 to 5 mm. The length range of the partition groove is determined by experimental simulation to ensure that the partition groove plays a role in cutting off the continuous growth of the airflow boundary layer, thereby improving the average heat transfer coefficient of the heat dissipation fins.

[0013] Furthermore, the spacing between adjacent heat dissipation fins in the finned tube segment is S. f The thickness of the heat sink fins is δ f The vertical height is h f .

[0014] Furthermore, the ripple wavelength of the ripple segment is λ, and the distance between the trough and the crest is f.

[0015] A heat exchanger includes the aforementioned integral corrugated finned tube heat transfer element. Its finned tube assembly and heat transfer base tube are integrally formed, completely eliminating the contact thermal resistance between the heat dissipation fins and the heat transfer base tube. This maximizes the heat transfer capacity of the finned tube assembly and the heat transfer base tube. The heat transfer base tube is an elongated oval flat tube with internal reinforcing ribs, resulting in high strength and preventing freezing and cracking in winter, thus extending its service life. Simultaneously, the semi-circular sidewalls on both sides reduce the airflow resistance, eliminate vortex wake regions, and provide excellent cleaning performance. The corrugated sections of the heat dissipation fins increase the disturbance to the flowing air, while the straight sections have a rectifying effect on the air at the inlet and outlet, further reducing flow resistance. The inclusion of dividing grooves interrupts the continuous growth of the airflow boundary layer, improving the average heat transfer coefficient of the fins. The cross-arrangement of the heat dissipation fins further enhances heat transfer efficiency.

[0016] This invention has the following advantages over the prior art:

[0017] 1. The integral corrugated finned tube heat transfer element of this utility model directly carves the finned tube assembly onto the first and second planes of the heat transfer base tube, making the finned tube assembly and the heat transfer base tube integrally formed. This completely eliminates the contact thermal resistance between the fins and the heat transfer base tube, maximizes the internal heat transfer of the finned tube, and reduces the rate of decrease in the heat transfer efficiency of the finned tube over time. In this utility model, the first and second sidewalls of the heat transfer base tube are both semi-circular. When air enters or exits the finned tube assembly along the second direction, the air flows in or out along the semi-circular first and second sidewalls, effectively reducing airflow resistance. In this invention, the finned tube assembly has m partition grooves along the second direction to divide the finned tube assembly into m+1 finned tube segments. Each finned tube segment includes heat dissipation fins arranged at intervals along multiple first directions. The heat dissipation fins in adjacent finned tube segments are staggered to cut off the growth of the flow boundary layer when air flows over the fins, thereby further improving the convective heat transfer efficiency of the fins. Along the second direction, each heat dissipation fin includes a first straight section, a corrugated section, and a second straight section connected together. The straight sections at both ends of the heat dissipation fin have a rectifying and drag-reducing effect on the air. The air inlet and outlet sections of each heat dissipation fin are designed as straight sections. These straight sections at the inlet and outlet have a rectifying effect on the air entering and exiting the heat dissipation fins, further reducing airflow resistance.

[0018] 2. The heat dissipation fins in this invention are arc-shaped, and the fins are inclined at an acute angle to the heat transfer base tube. Under the condition that the vertical height of the heat dissipation fins is the same, the arc-shaped fins increase the heat dissipation area by 2-3%, further enhancing its heat transfer capacity. The heat transfer base tube in this invention is equipped with reinforcing ribs to improve the overall strength of the heat transfer base tube, making it less prone to freezing and cracking in winter, and extending its service life. The arc-shaped corrugated fins and the staggered arrangement increase the heat exchange surface area and improve heat transfer efficiency, while reducing airflow resistance. The integral structure of the fins and heat transfer base tube enhances the strength of the finned tube, making it lightweight and low-cost. It also has better anti-freeze performance and cleaning performance. The integral corrugated finned tube heat transfer element in this invention is an integral aluminum structure, which is lightweight. Due to its significantly improved heat transfer efficiency, under the condition of transferring the same amount of heat, it can save a lot of material and reduce production costs compared with the widely used through-tube or externally wound finned tubes. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of the integral corrugated finned tube heat transfer element structure in an embodiment of this utility model;

[0020] Figure 2 This is a front view of the integral corrugated finned tube heat transfer element in this embodiment of the present invention.

[0021] Figure 3 This is a top view of the integral corrugated finned tube heat transfer element in an embodiment of this utility model.

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

[0023] Figure 5 This is a side view of the integral corrugated finned tube heat transfer element in an embodiment of this utility model.

[0024] In the diagram: 1. Finned tube assembly; 101. Finned tube section; 102. Heat dissipation fin; 1021. First straight section; 1022. Corrugated section; 1023. Second straight section; 103. Separating groove; 2. Heat transfer base tube; 201. First plane; 202. Second plane; 203. First sidewall; 204. Second sidewall; 205. Reinforcing rib; 206. Fluid channel; X, First direction; Y, Second direction; Z, Third direction. Detailed Implementation

[0025] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0026] It should be noted that in the description of this utility model, the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model.

[0027] Furthermore, it should be understood that, for ease of description, the dimensions of the various components shown in the accompanying drawings are not drawn to actual scale.

[0028] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined or described in one figure, it will not need to be further discussed and described in the description of the subsequent figures.

[0029] Example:

[0030] refer to Figures 1-5An integral corrugated finned tube heat transfer element includes: a finned tube assembly 1 and a heat transfer base tube 2. The heat transfer base tube 2 extends along a first direction and includes a first sidewall 203 and a second sidewall 204 arranged and opposite to each other along a second direction, and a first plane 201 and a second plane 202 arranged and opposite to each other along a third direction. Both ends of the first sidewall 203 and the second sidewall 204 are connected to the first plane 201 and the second plane 202, and both the first sidewall 203 and the second sidewall 204 are semi-circular. The finned tube assembly is respectively disposed on the first plane and the second plane. The heat transfer base tube 2 is formed by sequentially enclosing the first sidewall 203, the first plane 201, the second sidewall 204, and the second plane 202. The heat transfer base tube 2 and the finned tube assembly 1 are integral aluminum structures. The finned tube assembly is directly machined from the first plane 201 and the second plane 202 of the heat transfer base tube 2, and the two are integrally formed without contact thermal resistance.

[0031] The finned tube assembly 1 has m partition grooves 103 along the second direction to divide it into m+1 finned tube segments 101. Each finned tube segment 101 includes heat dissipation fins 102 arranged at intervals along multiple first directions, with the heat dissipation fins 102 in adjacent segments 101 arranged alternately. Along the second direction, each heat dissipation fin 102 includes a first straight section 1021, a corrugated section 1022, and a second straight section 1023 connected together, so that the straight section can perform a rectification function when air flows in and out of the surface of the heat dissipation fin 102. (Refer to...) Figure 5 The heat dissipation fins 102 are generally arc-shaped with a radius of R. The angle between the heat dissipation fins 102 and the first or second plane is θ, where 0° < θ < 90°. The first, second, and third directions are perpendicular to each other. m is a natural integer, for example, 2 to 10, and its specific value is determined by the width of the heat transfer base tube 2 along the second direction; the wider the heat transfer base tube 2, the larger the value of m can be. The number of partition grooves 103 on heat transfer base tubes 2 of different widths needs to be reasonably set to ensure that air can receive sufficient heat exchange when flowing through the heat dissipation fins, thereby effectively improving the heat transfer effect. The radius R of the heat dissipation fins 102 ranges from 10 to 20 mm, determined by the size of the heat transfer element itself and the internal space of the heat exchanger.

[0032] Specifically, the inner cavity of the heat transfer base tube 2 is provided with n reinforcing ribs 205 spaced apart along the second direction, and each reinforcing rib 205 extends along the first direction to divide the inner cavity of the heat transfer base tube 2 into n+1 parallel, non-communicating fluid channels extending along the first direction. High-temperature fluid flows into each fluid channel simultaneously. Because the heat transfer base tube 2 is oval, the fluid channels on both sides are semi-circular on the outer side and rectangular on the inner side, while the fluid channels arranged inside the heat transfer base tube 2 are rectangular. N is a natural integer, for example, 2 to 10, and its specific value is determined by the width of the heat transfer base tube 2 along the second direction; the wider the heat transfer base tube 2, the larger the value of n can be. The number of fluid channels divided by heat transfer base tubes 2 of different widths needs to be reasonably set according to the actual situation to ensure reasonable diversion of high-temperature fluid, thereby effectively improving the heat transfer effect.

[0033] The working process of this integral corrugated finned tube heat transfer element is as follows: a high-temperature fluid (such as water or antifreeze) flows in from one end of the heat transfer base tube 2 along a first direction and then flows out from the other end, while the lower-temperature air flows through the heat dissipation fins 102 along a second direction. This achieves heat exchange between the hot fluid in the heat transfer base tube and the cold air flowing through the heat dissipation fins. The air dissipates heat when it flows out of the heat dissipation finned tube. The heat dissipation fins 102 adopt an intermittent staggered arrangement design, which repeatedly interrupts the growth of the airflow boundary layer to enhance the convective heat transfer coefficient between the air and the heat dissipation fins, thereby improving the overall heat transfer capacity of the radiator.

[0034] The integral corrugated finned tube heat transfer element in this embodiment has the following advantages compared with currently used finned tubes with through-tube or externally wound fins, as well as existing finned tubes that enhance heat transfer by abruptly changing the shape of the fins to improve air turbulence:

[0035] (1) Significantly improved heat transfer efficiency. The heat dissipation fins 1 and heat transfer base tube 2 of this integral all-aluminum arc-shaped corrugated finned tube heat exchange element adopt an integral aluminum structure and are integrally formed, which completely eliminates the contact thermal resistance between the heat dissipation fins and the heat transfer tube, and maximizes the heat transfer inside the finned tube. At the same time, the heat dissipation fins are arc-shaped and corrugated, and the fins adopt an intermittent staggered arrangement. When the air passes over the heat dissipation fins, the turbulence is intense, thus enhancing the heat transfer performance, and its heat transfer coefficient K is increased by 8 to 26%.

[0036] (2) Low heat transfer efficiency decay rate. The temperature of the cooling medium inside the tube changes with the seasons, causing the fins and base tube of the finned tube type or the finned tube type with external fins to be subject to thermal expansion and contraction. This results in the contact thermal resistance between the fins and the base tube gradually increasing over time, leading to a large decay in the heat transfer efficiency of the radiator. In contrast, the integral all-aluminum arc-shaped corrugated finned tube heat exchanger uses the base tube and fins to be integrally formed, which significantly reduces the thermal efficiency decay rate.

[0037] (3) The arc-shaped and corrugated heat dissipation fins increase the heat exchange surface area. The heat dissipation fins are inclined at an acute angle to the heat transfer base tube and are arc-shaped. Under the condition that the vertical height of the fins is the same, the heat dissipation area of ​​the heat dissipation fins is increased by 2-3%, which further enhances the heat transfer capacity of the heat dissipation fins in this utility model.

[0038] (4) The heat transfer efficiency is higher when the heat dissipation fins are intermittently staggered. m slots are opened in the middle of the finned tube group to divide it into m+1 finned tube segments. The heat dissipation fins in each finned tube segment are intermittently staggered with the heat dissipation fins of the adjacent segments, which cuts off the growth of the flow boundary layer when the air flows through the fins and further improves the convective heat transfer efficiency of the fins.

[0039] (5) The straight sections at both ends of the heat dissipation fins have a rectifying effect on the airflow and reduce resistance. The air inlet and outlet sections at both ends of each heat dissipation fin are designed as straight sections. These straight sections at the inlet and outlet have a rectifying effect on the airflow when it enters and exits the heat dissipation fins, further reducing airflow resistance.

[0040] (6) Small size and light weight. Due to the greatly improved heat transfer efficiency, under the same heat transfer conditions, the integral all-aluminum arc-shaped corrugated finned tube heat exchanger can save a lot of materials and reduce production costs compared with the widely used finned tube or externally wound finned tube.

[0041] (7) Simple processing technology and low cost. The integral all-aluminum arc-shaped corrugated heat dissipation fins and the heat transfer base tube with multiple fluid channels are integrally formed, which is equivalent to completing the forming of fins and multiple water pipes at the same time. There is no need to weld between the fins and the water pipes. Compared with the currently used finned tube type or tube-wound finned tube, it reduces many processes such as fin making, bridging, drilling, hole flanging, tube stringing, tube expansion, and welding into tube bundle. The processing technology is simple and the cost is low.

[0042] (8) The base tube is an oblong flat tube with reinforcing ribs inside, which has high strength and is not prone to freezing and cracking in winter, and has a long service life.

[0043] In this embodiment, m = n, the number of finned tube segments 101 is the same as the number of fluid channels 206, the partition groove 103 and the reinforcing rib 205 are arranged opposite each other, and a finned tube segment 101 is arranged above and below each fluid channel 206. With this arrangement, each fluid channel 206 and its corresponding finned tube segment 101 is an independent heat transfer unit, which effectively improves heat transfer efficiency and ensures the overall strength of the integral corrugated finned tube after slotting.

[0044] In another embodiment, the values ​​of m and n may not be equal, and can be adjusted according to the actual usage.

[0045] In this embodiment, the length ratio of the first straight segment 1021, the corrugated segment 1022, and the second straight segment 1023 is 1:(1.2~3):1. For example, the first straight segment 1021 can be 3mm, the corrugated segment 1022 can be 6mm, and the second straight segment 1023 can be 3mm; or the first straight segment 1021 can be 5mm, the corrugated segment 1022 can be 15mm, and the second straight segment 1023 can be 5mm; or the first straight segment 1021 can be 10mm, the corrugated segment 1022 can be 24mm, and the second straight segment 1023 can be 10mm, etc. The values ​​of the first straight segment 1021, the corrugated segment 1022, and the second straight segment 1023 can be reasonably adjusted according to actual usage. The straight section located at the air inlet and outlet has the effect of rectifying and reducing air resistance, while the corrugated section can increase the disturbance to the flowing air. By optimizing the proportion of each section of the heat dissipation fins, the air can flow over the surface of the heat dissipation fins at a suitable flow rate, thereby improving the heat transfer efficiency.

[0046] The length of the partition groove 103 along the second direction is c, and the range of c is 1 to 5 mm. For example, 1 mm, 2 mm, 3 mm, 4 mm or 5 mm, etc. The length range of the partition groove 103 is simulated according to experiments to ensure that the partition groove 103 plays a role in cutting off the continuous growth of the air flow boundary layer, thereby improving the average heat transfer coefficient of the heat dissipation fins.

[0047] refer to Figure 2 and Figure 3 The spacing between adjacent heat dissipation fins 102 in the finned tube section is Sf; the thickness of the heat dissipation fin 102 is δ. f The vertical height is h f The corrugated wavelength of the corrugated section 1022 is λ, and the distance between the trough and the crest is f. The length of the first straight section 1021 and the second straight section 1022 is e, the thickness of the heat transfer base tube 2 is B, and the width of the reinforcing rib 205 is δ. w The length of the fluid channel 206 is a, the width is b, and the radius of the first sidewall 203 and the second sidewall 204 is r. The range of values ​​in this embodiment is reasonably determined according to the actual heat exchange requirements and the internal space of the heat exchanger.

[0048] This embodiment also includes a heat exchanger comprising the aforementioned integral corrugated finned tube heat transfer element. The finned tube assembly 1 and the heat transfer base tube 2 are integrally formed, completely eliminating the contact thermal resistance between the heat dissipation fins 102 and the heat transfer base tube 2. The finned tube assembly 1 and the heat transfer base tube 2 maximize heat transfer capacity. The heat transfer base tube 2 is an elongated oval flat tube with internal reinforcing ribs 205, resulting in high strength and preventing freezing and cracking in winter, thus extending its service life. Simultaneously, the semi-circular sidewalls on both sides reduce the airflow resistance, eliminate vortex wake regions, and provide excellent cleaning performance. The corrugated sections of the heat dissipation fins 102 increase the disturbance to the flowing air, while the straight sections have a rectifying effect on the air at the inlet and outlet, further reducing flow resistance. The partition grooves 103 interrupt the continuous growth of the airflow boundary layer, improving the average heat transfer coefficient of the fins. The cross-arrangement of the heat dissipation fins 102 further enhances heat transfer efficiency.

[0049] In practice:

[0050] This utility model's integral corrugated finned tube heat transfer element consists of heat dissipation fins 1 and a heat transfer base tube 2. The heat transfer base tube 2 has a cross-sectional thickness of B, a width of D, a total length of L for the heat dissipation fins, and a total height of H for the finned tube. The heat transfer base tube 2 is divided into n+1 non-communicating fluid channels 206 along a second direction. The outer side of the fluid channels 206 at both ends is a semi-circle with a radius of r, and the inner side is rectangular. The fluid channels arranged inside are rectangular, with a flow height of b, a width of a, and a wall thickness between the channels of δ. W Heat dissipation fins 1 are directly cut out on both sides of the heat transfer base tube 2. The heat dissipation fins 1 and the heat transfer base tube 2 are integrated. Along the second direction, m slots are cut on the heat dissipation fins 102 to form m+1 segments of heat dissipation fins 102. The length of each segment of heat dissipation fin 102 is L. f Each finned tube segment 101 has its heat dissipation fins 102 staggered with those in adjacent finned tube segments 101. Each heat dissipation fin has two straight sections of length e at both ends. During the cutting process of the heat dissipation fins 102, the heat dissipation fins 102 naturally tilt towards the heat transfer base tube 2 at an angle θ (0° < θ < 90°), and simultaneously form an arc shape with a radius R. The spacing between the heat dissipation fins 102 is S. f The fin thickness is δ f The vertical height is h f The ripple wavelength is λ, and the distance from the trough to the peak height is f. The values ​​of each data are reasonably determined according to the actual heat exchange requirements and the internal space of the heat exchanger. During operation, the high-temperature fluid (such as water or antifreeze) flows in from one end of the fluid channel in the heat transfer base tube 2 and flows out from the other end of the fluid channel, while the lower-temperature air flows over the heat dissipation fins 1 on both sides of the heat transfer base tube 2, thereby realizing the heat exchange between the hot fluid in the heat transfer base tube 2 and the cold air flowing over the heat dissipation fins 102, and the heat is dissipated as the air flows out of the finned tube.

[0051] This utility model discloses a heat exchanger with integral all-aluminum arc-shaped corrugated fins. The heat dissipation fins are integrally formed with the base tube, which completely eliminates the contact thermal resistance between the fins and the water pipe. The cross-arranged heat dissipation fins improve the heat transfer efficiency of the finned tube. Under the same heat exchange conditions in the air-cooled system of the power plant intercooling tower, the height of the heat exchanger is reduced, material consumption is reduced, and costs are reduced. The integral structure of the corrugated fins and the heat transfer base tube greatly enhances the structural strength of the aluminum finned tube bundle.

[0052] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. An integral corrugated finned tube heat transfer element, characterized in that, include: Integrated finned tube assembly and heat transfer base tube; The heat transfer base tube extends along a first direction and includes a first sidewall and a second sidewall arranged and opposite to each other along a second direction, and a first plane and a second plane arranged and opposite to each other along a third direction. Both ends of the first sidewall and the second sidewall are connected to the first plane and the second plane, and both the first sidewall and the second sidewall are semi-circular. The finned tube assembly is respectively disposed on the first plane and the second plane. The finned tube assembly has m partition grooves along the second direction to divide the finned tube assembly into m+1 finned tube segments. Each finned tube segment includes heat dissipation fins arranged at intervals along multiple first directions, and the heat dissipation fins in adjacent finned tube segments are staggered. Along the second direction, each heat dissipation fin includes a first straight section, a corrugated section and a second straight section connected to each other so that the straight section can play a rectifying role when air flows in and out of the heat dissipation fin surface. The first direction, the second direction and the third direction are perpendicular to each other.

2. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The heat dissipation fins are generally arc-shaped with a radius of R, and the angle between the heat dissipation fins and the first plane or the second plane is θ, where 0° < θ < 90°.

3. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The finned tube assembly and heat transfer base tube are integral aluminum structures.

4. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The inner cavity of the heat transfer base tube is provided with n reinforcing ribs at intervals along the second direction, and each of the reinforcing ribs extends along the first direction to divide the inner cavity of the heat transfer base tube into n+1 fluid channels extending along the first direction.

5. The integral corrugated finned tube heat transfer element according to claim 4, characterized in that: Where m = n, the partition groove and the reinforcing rib are arranged opposite each other, and a finned tube section is arranged above and below each fluid channel.

6. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The length ratio of the first straight section, the corrugated section, and the second straight section is 1:(1.2~3):

1.

7. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The length of the dividing groove along the second direction is c, and the range of c is 1 to 5 mm.

8. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The spacing between adjacent heat dissipation fins in the finned tube section is S. f The thickness of the heat sink fins is δ f The vertical height is h f .

9. The integral corrugated finned tube heat transfer element according to claim 1, characterized in that: The ripple wavelength of the ripple segment is λ, and the distance between the trough and the crest is f.

10. A heat exchanger, characterized in that: The integral corrugated finned tube heat transfer element includes any one of claims 1 to 9.

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