Fin and heat exchanger with same

Abstract

The utility model provides a fin and a heat exchanger with the same, the fin comprises a body, the body is provided with a through hole, the through hole is used for being matched with a heat exchange tube in an inserted mode, one side of the through hole is provided with a turnup edge, the turnup edge is annularly arranged on the edge of the through hole, and the turnup edge extends in the direction deviating from the thickness direction of the body; and the drainage structure is arranged on the turned-over edge, and the drainage structure extends in the circumferential direction of the turned-over edge. According to the technical scheme, the problem that in the prior art, when a heat exchanger serves as an evaporator to operate in a low-temperature environment, condensate water on the surfaces of the fins is prone to frosting, and consequently the defrosting efficiency of the heat exchanger is low can be solved.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, and more specifically, to a finned heat exchanger and a heat exchanger having the same. Background Technology

[0002] Heat exchangers play a crucial role in refrigeration and air conditioning systems. Finned tube heat exchangers mainly consist of heat exchange tubes and finned tubes, with the fin structure being an important component for optimizing heat exchange efficiency. When a heat exchanger operates as an evaporator in a low-temperature environment, condensate easily forms on the fin surface.

[0003] In traditional finned structures, over time, condensate will frost over at low temperatures, forming an insulating layer on the fin surface that hinders effective heat exchange. This not only reduces heat exchange efficiency but also prolongs the defrosting cycle, increases system energy consumption, and affects the overall system performance and reliability. Utility Model Content

[0004] This invention provides a fin and a heat exchanger having the same, to solve the problem in the prior art where, when a heat exchanger operates as an evaporator in a low-temperature environment, condensate on the surface of the fins easily frosts, resulting in low defrosting efficiency.

[0005] According to one aspect of the present invention, a fin is provided, the fin comprising: a body having a through hole for inserting and engaging with a heat exchange tube, one side of the through hole having a flange annularly disposed at the edge of the through hole, the flange extending in a direction away from the thickness of the body; and a drainage structure disposed on the flange, the drainage structure extending circumferentially along the flange.

[0006] By applying the technical solution of this utility model, a drainage structure is provided on the flange, extending circumferentially along the flange 20, providing a drainage path for condensate. This drainage structure collects and discharges the condensate, effectively preventing condensate from forming on the surface of the heat exchanger at low temperatures and reducing the likelihood of frost formation on the fins. Even if a small amount of frost forms on the fins, it melts quickly during defrosting and is discharged through the drainage structure, significantly reducing defrosting time, energy consumption, and improving the heat exchanger's heat exchange efficiency and reliability, thereby enhancing the system's operating efficiency.

[0007] Furthermore, the bottom of the flange has a groove that extends through the side wall of the flange and extends circumferentially, forming a drainage structure. This design allows condensate to collect at the groove along the surface of the flange or heat exchange tubes. The condensate can then be quickly discharged under gravity, preventing it from remaining on the surface of the heat exchange tubes and fins for extended periods and reducing the likelihood of frost formation on the tubes and fins.

[0008] Furthermore, the slot can be rectangular or rhomboid in shape. With the same dimensions along the flange extension direction, the rectangular structure has a larger cross-sectional area than other structures. This increases the condensate collection area within the slot, making it easier for condensate to collect, increasing the collection speed and volume, and improving the condensate discharge rate, thereby enhancing the drainage effect of the drainage structure.

[0009] Furthermore, the flange has a top and a bottom that are oppositely arranged in the radial direction. A guide portion is provided on the outer wall of the flange, which slopes from the top to the bottom of the flange. The guide portion and the flange cooperate to form a drainage structure for draining condensate on the flange. In this way, the guide portion can guide the flow of condensate on the flange surface, allowing the condensate to flow along the guide portion to the bottom of the flange for discharge, reducing the residence time of condensate on the flange surface, and thus reducing the possibility of frost formation on the flange surface.

[0010] Furthermore, the flange has a first end and a second end located near and away from the body, and a guide portion extends to the first end and / or the second end. This design avoids the guide portion being too short, allowing the guide portion to quickly collect and flow to the bottom of the flange for drainage, thus ensuring the guide portion's effective drainage function.

[0011] Furthermore, the first end is annularly disposed at the edge of the through hole and connected to the body, while the second end has multiple opposing recesses and multiple protrusions, with the protrusions and recesses sequentially connected along the circumference of the flange; and / or, the end of the protrusion away from the first end has a bent section, which bends outward toward the flange. The recess design reduces the weight of the flange, achieving fin weight reduction. The length of the bent section can be changed to alter the length of the protrusions, thereby meeting different fin spacing requirements and improving the adaptability of the fin.

[0012] Furthermore, the end of the bent section away from the protrusion has a curled structure, with the end of the bent section curled towards the flange. This reduces the disturbance of the fluid to the bent section during ventilation between the fins, improves the structural stability of the flange, prevents excessive shaking of the bent section from interfering with the heat exchange tubes and adjacent fins, and ensures the stable operation of the heat exchanger.

[0013] Furthermore, the length of the protrusion at the bottom of the flange is l1, and the length of the protrusion at the top of the flange is l2, where l1 > l2; the width of the opening of the recess at the bottom of the flange is m1, and the width of the opening of the recess at the top of the flange is m2, where m1 > m2. This configuration increases the contact area between the protrusion at the bottom of the flange and the heat exchange tube, thus increasing the support strength for the heat exchange tube. Moreover, this design forms a guiding structure, directing the flow of condensate, causing it to collect on the protrusion at the bottom of the flange and then drip off under gravity, improving drainage efficiency during defrosting. When the condensate collects in the recess at the bottom of the flange, the wider opening of the recess increases the dripping range, further reducing the amount of condensate retained on the heat exchange tube and fins, further improving drainage efficiency during defrosting.

[0014] Furthermore, the inner diameter of the through hole is D, the axial length of the flange is L, and the circumferential length of the groove along the flange is h1, where D / 3 ≤ h1 ≤ D / 2; the axial length of the groove along the flange is h2, where L / 3 ≤ h2 < L. This configuration ensures both the structural strength of the flange and a sufficiently large condensate collection area for rapid dripping, reducing the amount of frost forming between the heat exchange tube and the flange.

[0015] According to another aspect of this utility model, a heat exchanger is provided, comprising: a heat exchange tube extending along the thickness direction of the body, with a flanged sleeve on the outer periphery of the heat exchange tube; and multiple fins, as described above, spaced apart along the thickness direction of the body, with flanged sleeves on the outer periphery of the heat exchange tube. The above-described heat exchanger effectively solves the problem in the prior art where condensate on the fins and heat exchange tube cannot be effectively discharged, easily forming frost and resulting in low defrosting efficiency of the system. Attached Figure Description

[0016] The accompanying drawings, which form part of this application, are used to provide a further understanding of the present invention. The illustrative embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an undue limitation of the present invention. In the drawings:

[0017] Figure 1 A schematic diagram of the structure of a fin in the prior art is shown;

[0018] Figure 2 A schematic diagram of the flange structure provided by this utility model is shown;

[0019] Figure 3 This diagram shows a structural schematic of the flange provided in Embodiment 1 of the present invention from one perspective;

[0020] Figure 4This shows a structural schematic diagram of the flange provided in Embodiment 1 of the present invention from another perspective;

[0021] Figure 5 This diagram shows a structural schematic of the flange provided in Embodiment 2 of the present invention from one perspective;

[0022] Figure 6 This shows a structural schematic diagram of the flange provided in Embodiment 2 of this utility model from another perspective;

[0023] Figure 7 A schematic diagram of the structure of the fins provided by this utility model is shown.

[0024] The above figures include the following reference numerals:

[0025] 10. Ontology;

[0026] 20. Flanging; 201. Grooving; 202. Guide section;

[0027] 21. First end; 22. Second end;

[0028] 221. Depression;

[0029] 222. Protrusion; 2221. Bend;

[0030] 01. Fin; 02. Flanged edge. Detailed Implementation

[0031] 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. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present utility model or its application or use. All other embodiments obtained by those skilled in the art based on the embodiments of the present utility model without creative effort are within the scope of protection of the present utility model.

[0032] like Figure 2 As shown, this embodiment of the utility model provides a fin, which includes a body 10 and a drainage structure. The body 10 has a through hole for insertion into a heat exchange tube. One side of the through hole has a flange 20, which is annularly disposed at the edge of the through hole and extends in a direction opposite to the thickness of the body 10. The drainage structure is disposed on the flange 20 and extends circumferentially along the flange 20. The drainage structure is used to drain condensate from the body 10 and the heat exchange tube. The heat exchange tube is made of copper, which has good thermal conductivity and corrosion resistance; the fin is made of aluminum foil, which has good thermal conductivity and processing performance.

[0033] By applying the technical solution of this utility model, a drainage structure is provided on the flange 20, extending circumferentially along the flange 20, providing a drainage path for condensate. This drainage structure collects and discharges the condensate, effectively preventing condensate from forming on the surface of the body 10 under low-temperature conditions, thus reducing the likelihood of frost formation on the fin surface. Even if a small amount of frost forms on the fins, it melts quickly during defrosting and is discharged through the drainage structure, significantly reducing defrosting time, lowering energy consumption, improving the heat exchanger's heat exchange efficiency and reliability, and ultimately enhancing the system's operating efficiency.

[0034] In some embodiments, the drainage structure may be an opening or flow channel provided through the flange 20, so that condensate water is collected at the outer end of the opening or flow channel and then discharged; in other embodiments, the drainage structure may be a guide channel provided on the flange 20, which guides the condensate water so that it is collected and discharged.

[0035] like Figures 3 to 6 As shown, the bottom of the flange 20 has a groove 201, which penetrates the side wall of the flange 20 and extends circumferentially, forming a drainage structure. This design allows condensate to collect at the groove 201 along the surface of the flange or heat exchange tube. The condensate can then be quickly discharged under gravity, preventing it from remaining on the surface of the heat exchange tube and fins for extended periods and reducing the likelihood of frost formation on the heat exchange tubes and fins. Furthermore, compared to existing technologies, such as… Figure 1 As shown, in a traditional finned structure, fin 01 is tightly fitted to the heat exchange tube via a flange 02, which is a closed cylindrical shape. Due to the closed nature of the traditional cylindrical flange 02, condensate often has difficulty draining quickly from the contact surface between the flange 02 and the heat exchange tube. Furthermore, during defrosting, a layer of fin 01 separates the heat exchange tube from the frost, resulting in low thermal conductivity. In this application, the portion of the heat exchange tube located at the slot 201 can directly contact the external frost, allowing the heat from the heat exchange tube to be directly transferred to the external frost for heating, thus improving thermal conductivity and shortening the defrosting time of the heat exchanger. In this embodiment, the specific structure of the slot 201 is not limited; the slot 201 can be circular, square, or other shapes.

[0036] In the first embodiment provided in this application, as Figure 3 and Figure 4 As shown, slot 201 has a rhomboid structure.

[0037] Preferably, in Embodiment 2 provided in this application, as Figure 5 and Figure 6As shown, the difference from Embodiment 1 is that the slot 201 is a rectangular structure. The length of the rectangular structure extends along the circumferential direction of the flange 20. With the same dimensions of the slot 201 along the extension direction of the flange 20, the rectangular structure has a larger cross-sectional area compared to other structures. This increases the condensate collection area within the slot 201, making it easier for the condensate to collect, increasing the collection speed and volume, and improving the condensate discharge rate, thereby enhancing the drainage effect of the drainage structure. Simultaneously, it also increases the direct contact area between the heat exchange tube and the outside, thereby improving the heat exchange efficiency of the device and shortening the defrosting time.

[0038] like Figure 6 As shown, the flange 20 has a top and a bottom that are arranged opposite each other in the radial direction. A guide portion 202 is provided on the outer wall of the flange 20. The guide portion 202 is inclined from the top of the flange 20 to the bottom of the flange 20. In this way, the guide portion 202 can guide the flow of condensate on the surface of the flange 20, so that the condensate flows along the guide portion 202 to the bottom of the flange 20 for discharge. The guide portion 202 and the flange 20 cooperate to form a drainage structure for draining condensate on the flange 20. This allows the condensate to collect and flow more quickly, reducing the residence time of condensate on the surface of the flange 20, thereby reducing the possibility of frost forming on the surface of the flange 20.

[0039] The guide section 202 includes multiple spaced protrusions that extend along the axial direction of the flange 20. These protrusions and the flange 20 work together to form multiple drainage structures, greatly increasing the drainage speed. Simultaneously, the guide section 202 also enhances the structural strength of the flange 20 and improves the stability of the heat exchange tube support.

[0040] Preferably, multiple protrusions are arranged in parallel to ensure the consistency of condensate water guidance and the uniformity of drainage, thereby improving the drainage effect of the guide section 202.

[0041] In other embodiments of this application, the guide portion 202 may also be configured as a plurality of grooves, or a combination of grooves and protrusions.

[0042] Furthermore, the flange 20 has a first end 21 and a second end 22 located near the body 10 and away from the body 10, respectively. The first end 21 and the second end 22 are located at both ends of the slot 201 along the circumference of the flange 20, and the guide portion 202 extends to the first end 21 and / or the second end 22. With the above arrangement, the guiding length of the guide portion 202 can be avoided from being too short. In this way, the guide portion 202 can allow condensate from at least one end of the flange 20 to quickly collect and flow to the bottom of the flange 20 or into the slot 201 for discharge, ensuring the guiding and drainage effect of the guide portion 202.

[0043] In some embodiments of this application, the guide portion 202 extends to the first end 21 of the flange 20 to guide and drain the condensate located at the first end 21, so that it flows from one end of the groove 201 into the bottom of the flange 20 or into the groove 201 and is discharged.

[0044] In some other embodiments of this application, the guide portion 202 extends to the second end 22 of the flange 20 to guide and drain the condensate located at the second end 22, so that it flows from the other end of the slot 201 into the bottom of the flange 20 or into the slot 201 and is discharged.

[0045] In this embodiment, the guide portion 202 extends to the first end 21 and the second end 22 of the flange 20, so as to guide the condensate located at the first end 21 and the second end 22, so that the condensate on both sides of the flange 20 flows into the groove 201 from both ends of the groove 201 and converges and is discharged, thereby improving the drainage effect of the guide portion 202.

[0046] like Figure 5 As shown, the inner diameter of the through hole is D, and the length of the flange 20 along the axial direction is L. The length of the slot 201 along the circumferential direction of the flange 20 is h1, where D / 3 ≤ h1 ≤ D / 2. If h1 < D / 3, the length of the slot 201 along the circumferential direction of the flange 20 is too small, resulting in a small area for condensate collection and a small amount of condensate dripping. This can easily lead to condensate between the heat exchange tube and the flange 20 not draining in time and forming frost. If h1 > D / 2, the length of the slot 201 along the circumferential direction of the flange 20 is too large, resulting in low structural strength of the flange 20. Therefore, setting it to D / 3 ≤ h1 ≤ D / 2 ensures both the structural strength of the flange 20 and allows for a sufficiently large area for condensate collection and rapid dripping, reducing condensate buildup between the heat exchange tube and the flange 20. Frost accumulation; the length of the groove 201 along the extension direction of the flange 20 is h2, where L / 3 ≤ h2 < L. If h2 < L / 3, the length of the groove 201 along the extension direction of the flange 20 is too small, resulting in a small area for condensate to collect and a small amount of condensate dripping. This easily leads to condensate between the heat exchange tube and the flange 20 not being discharged in time and thus frosting. If h2 ≥ L, the length of the groove 201 along the extension direction of the flange 20 is too large, resulting in low structural strength of the flange 20. Therefore, setting it to L / 3 ≤ h2 < L ensures both the structural strength of the flange 20 and allows for a sufficiently large area for condensate to collect and drip quickly, reducing the amount of frost accumulation between the heat exchange tube and the flange 20. In this application, the inner diameter D of the through hole and the axial length L of the flange 20 are not limited; they can be selected according to customer needs and actual working conditions.

[0047] like Figure 4As shown, the first end 21 is annularly disposed at the edge of the through hole and connected to the body 10. The second end 22 has multiple recesses 221 and multiple protrusions 222 disposed opposite to each other. The protrusions 222 and recesses 221 are sequentially connected along the circumference of the flange 20. When the heat exchanger is used as an evaporator, due to the limitations of the elongation and cupping value of the aluminum foil, if the fin spacing between adjacent fins 01 needs to reach a first preset value, the material thickness of the aluminum foil needs to reach a second preset value so that the processed flange 02 can achieve the aforementioned required fin spacing. This application, through the alternating arrangement of the recesses 221 and protrusions 222, ensures that when processing the flange 20, if the fin spacing also needs to reach the first preset value, the required thickness of the aluminum foil material due to the design of the recesses 221 will be lower than the second preset value. This saves the weight of the aluminum foil material, reduces the consumption of raw materials, saves manufacturing costs, and the design of the recesses 221 reduces the weight of the flange 20, achieving fin lightweighting. Meanwhile, the above design ensures that the heat exchange tubes are not completely covered by the flange 20, increasing the direct contact area between the heat exchange tubes and the frost, significantly improving heat exchange efficiency, and thus enhancing the reliability and adaptability of the heat exchanger.

[0048] In this embodiment, the specific structural outlines of the recessed portion 221 and the protruding portion 222 are not limited, and can be sawtooth structure, wave structure or other irregular structure, etc.

[0049] In this application, the number of recesses 221 and protrusions 222 is not limited, and can be set to 2, 3 or 6, etc.

[0050] The first end 21 is a closed circular structure, which can improve the stability of the flange 20. The circular structure is compatible with the structure of the heat exchange tube, which can effectively prevent the body 10 from damaging the heat exchange tube and extend the service life of the heat exchange tube.

[0051] like Figure 7 As shown, the end of the protrusion 222 away from the first end 21 has a bent section 2221. The bent section 2221 bends outward toward the flange 20 to avoid damaging the heat exchange tubes inside the flange 20. Thus, the length of the protrusion 222 can be changed by altering the length of the bent section 2221, thereby meeting different fin spacing requirements and improving the adaptability of the fins. Furthermore, the bent section 2221 effectively prevents the protrusion 222 from scratching adjacent fins, ensuring the service life of the fins.

[0052] The end of the bent section 2221 away from the protrusion 222 has a curled structure, with the end of the bent section 2221 curled towards the flange 20. This reduces the disturbance of the fluid to the bent section 2221 during ventilation between the fins, improves the structural stability of the flange 20, prevents excessive shaking of the bent section 2221 that could interfere with the heat exchange tubes and adjacent fins, and ensures the stable operation of the heat exchanger.

[0053] In some embodiments of this application, the length of the protrusion 222 at the bottom of the flange 20 is l1, and the length of the protrusion 222 at the top of the flange 20 is l2, where l1 > l2. This arrangement increases the contact area between the protrusion 222 at the bottom of the flange 20 and the heat exchange tube, thereby increasing the support strength for the heat exchange tube. Furthermore, the flange 20 forms a guiding structure from the top protrusion 222 to the bottom protrusion 222, thus ensuring the structural strength of the flange 20 while guiding the flow of condensate. This allows the condensate to collect on the protrusion 222 at the bottom of the flange 20 and then drip off under gravity, improving the drainage efficiency during defrosting.

[0054] In some other embodiments of this application, the width of the opening of the recess 221 at the bottom of the flange 20 is m1, and the width of the opening of the recess 221 at the top of the flange 20 is m2, where m1 > m2. With this configuration, when condensate collects at the recess 221 at the bottom of the flange 20, the wider opening of the recess 221 increases the dripping range of the condensate, further reducing the amount of condensate retained on the heat exchange tubes and fins, and improving the drainage efficiency during defrosting. It also further increases the direct contact area between the heat exchange tubes and the frost, shortening the defrosting time.

[0055] like Figure 2 As shown, multiple protrusions 222 and multiple recesses 221 form a serrated structure. When machining the flange 20, a dividing point is directly identified on the part corresponding to the through hole on the body 10. Then, according to requirements, the part is divided along the horizontal plane in different directions from the dividing point to directly obtain multiple protrusions 222. The gaps between adjacent protrusions 222 form multiple recesses 221, thus forming a serrated structure. This machining method eliminates the need for complex shapes and cumbersome dividing steps, making machining very convenient.

[0056] In this embodiment, multiple recesses 221 and multiple protrusions 222 are provided correspondingly, that is, the number of recesses 221 and protrusions 222 is the same, and both recesses 221 and protrusions 222 are set to 8.

[0057] Preferably, a plurality of protrusions 222 and a plurality of recesses 221 are evenly distributed at the second end 22, which facilitates the processing and forming of the flange 20.

[0058] Specifically, the flange 20 is stamped from the body 10. In this way, there are no welding points between the flange 20 and the body 10, avoiding the low strength of the fin due to processing errors and improving the overall structural strength of the fin.

[0059] In another embodiment of this utility model, a heat exchanger is provided, comprising a heat exchange tube and a plurality of fins. The heat exchange tube extends along the thickness direction of the body 10, and a flange 20 is fitted around the outer periphery of the heat exchange tube. A plurality of fins are arranged at intervals along the thickness direction of the body 10, and the flange 20 is fitted around the outer periphery of the heat exchange tube. The fins are those provided in the above embodiment. The aforementioned fins effectively solve the problem in the prior art where condensate on the fins cannot be effectively and promptly discharged, easily leading to frost formation and low defrosting efficiency of the system. The heat exchanger with the aforementioned fins also has the above advantages.

[0060] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0061] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of this invention. It should also be understood that, for ease of description, the dimensions of the various parts shown in the drawings are not drawn to actual scale. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following drawings denote similar items; therefore, once an item is defined in one drawing, it need not be further discussed in subsequent drawings.

[0062] In the description of this utility model, it should be understood that the directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" 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. Unless otherwise stated, these directional terms 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, and therefore should not be construed as a limitation on the scope of protection of this utility model. The directional terms "inner" and "outer" refer to the inner and outer contours of each component itself.

[0063] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0064] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be construed as limiting the scope of protection of this utility model.

[0065] The above description is merely a preferred embodiment of this utility model and is not intended to limit the utility model. Various modifications and variations can be made to this utility model by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. A fin, characterized in that, The fins include: The body (10) has a through hole for inserting and engaging with a heat exchange tube. One side of the through hole has a flange (20) which is circumferentially arranged at the edge of the through hole and extends away from the thickness direction of the body (10). A drainage structure is provided on the flange (20), and the drainage structure extends circumferentially along the flange (20).

2. The fin according to claim 1, characterized in that, The bottom of the flange (20) has a groove (201) that penetrates the side wall of the flange (20) and extends circumferentially along the flange (20), forming the drainage structure.

3. The fin according to claim 2, characterized in that, The slot (201) is a rectangular or rhomboid structure.

4. The fin according to claim 1, characterized in that, The flange (20) has a top and a bottom that are arranged opposite each other in the radial direction. A guide (202) is provided on the outer side wall of the flange (20). The guide (202) is inclined from the top of the flange (20) to the bottom of the flange (20). The guide (202) and the flange (20) cooperate with each other to form the drainage structure.

5. The fin according to claim 4, characterized in that, The flange (20) has a first end (21) and a second end (22) located near the body (10) and away from the body (10), and the guide portion (202) extends to the first end (21) and / or the second end (22).

6. The fin according to claim 5, characterized in that, The first end (21) is circumferentially disposed at the edge of the through hole and connected to the body (10). The second end (22) has a plurality of recesses (221) and a plurality of protrusions (222) disposed opposite to each other. The protrusions (222) and the recesses (221) are sequentially connected along the circumference of the flange (20). And / or, the end of the protrusion (222) away from the first end (21) has a bent section (2221) that bends toward the outside of the flange (20).

7. The fin according to claim 6, characterized in that, The end of the bent section (2221) away from the protrusion (222) has a curled structure, and the end of the bent section (2221) is curled toward the flange (20).

8. The fin according to claim 6, characterized in that, The length of the protrusion (222) at the bottom of the flange (20) is l1, and the length of the protrusion (222) at the top of the flange (20) is l2, where l1 > l2; The width of the opening of the recess (221) at the bottom of the flange (20) is m1, and the width of the opening of the recess (221) at the top of the flange (20) is m2, where m1 > m2.

9. The fin according to claim 2, characterized in that, The inner diameter of the through hole is D, the length of the flange (20) along the axial direction is L, and the length of the slot (201) along the circumferential direction of the flange (20) is h1, where D / 3≤h1≤D / 2; The length of the slot (201) along the axial direction of the flange (20) is h2, and L / 3 ≤ h2 < L.

10. A heat exchanger, characterized in that, The heat exchanger includes: The heat exchange tube extends along the thickness direction of the body (10), and the flange (20) is sleeved on the outer periphery of the heat exchange tube; The fins as described in any one of claims 1 to 9 are provided in a plurality of fins, the plurality of fins being arranged at intervals in the thickness direction of the body (10), and the flange (20) being sleeved on the outer periphery of the heat exchange tube.

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