Fins, heat exchangers and air conditioners

Abstract

The utility model belongs to heat exchanger technical field, concretely provides a kind of fin, heat exchanger and air conditioner. To solve the problem that the fin of existing heat exchanger will form larger flow stagnation zone after air flow bypasses pipe hoop part, and affect fin heat exchange performance, the fin of the utility model includes sheet body part, multiple pipe hoop parts and multiple converging flow parts.Each pipe hoop part is provided with through-hole for fixing refrigerant pipe, the plane of the axis passing through pipe hoop part and perpendicular to the windward direction of pipe hoop part is marked as middle surface.Each converging flow part corresponds to a pipe hoop part respectively;Converging flow part penetrates middle surface, and converging flow part is inclined to pipe hoop part along the leeward direction of pipe hoop part, to make converging flow part and pipe hoop part define converging flow groove.Converging flow groove is used to compress air flow, and guide compressed air flow to the leeward side of pipe hoop part.The utility model improves the heat exchange performance of fin.

Description

Technical Field

[0001] This utility model belongs to the field of heat exchanger technology, and specifically provides a finned heat exchanger and an air conditioner. Background Technology

[0002] A heat exchanger is a major component of an air conditioner, used to heat or cool the air flowing through the air conditioner, thereby heating or cooling the environment in which the air conditioner is located.

[0003] Heat exchangers typically consist of fins and refrigerant pipes running through the fins. The fins usually have clamps to thermally connect them to the refrigerant pipes. This causes a large stagnant flow zone (vortex) to form on the leeward side of the clamp after the airflow bypasses it, affecting the heat exchange efficiency between the airflow and the fins and reducing the heat exchange performance of the fins. Utility Model Content

[0004] One objective of this invention is to solve the problem that the heat exchange performance of existing heat exchangers is affected by the large flow stagnation zone formed by the airflow after it passes around the tube clamp.

[0005] To achieve the above objectives, the present invention provides, in a first aspect, a fin suitable for a heat exchanger, comprising:

[0006] Body part;

[0007] Multiple pipe clamps, each of which is provided with a through hole for fixing the refrigerant pipe, and the plane passing through the axis of the pipe clamp and perpendicular to the windward direction of the pipe clamp is called the mid-plane;

[0008] Multiple flow-gathering sections, each of which corresponds to one of the clamp sections; the flow-gathering sections penetrate the dividing surface and are inclined toward the clamp section along the leeward direction of the clamp section, so that the flow-gathering section and the clamp section define a flow-gathering groove;

[0009] The flow-gathering groove is used to compress the airflow and guide the compressed airflow to the leeward side of the pipe clamp.

[0010] Optionally, each of the pipe clamps is provided with a flow-gathering section on each of its two sides perpendicular to its windward direction, so that each of the pipe clamps corresponds to two flow-gathering grooves.

[0011] Optionally, the flow-gathering section is a rectangular or triangular sheet-like structure.

[0012] Optionally, the flow-gathering section is a structure formed on the fin by a stamping process, thereby forming a turbulence-causing hole on the fin body; the turbulence-causing hole is located on the side of the flow-gathering section near or away from the clamp portion; and / or, the included angle β between the flow-gathering section and the fin body is selected from any value from 20° to 90°; and / or, the ratio of the height H of the flow-gathering section protruding from the fin body to the distance S between two adjacent fins in the heat exchanger is selected from any value from 0.3 to 0.8.

[0013] Optionally, the flow-gathering section is a columnar structure; and / or, the ratio of the height H of the flow-gathering section protruding from the fin portion to the distance S between two adjacent fins in the heat exchanger is selected from any value from 0.15 to 0.5.

[0014] Optionally, the flow-gathering section includes at least two spaced-apart flow-gathering segments.

[0015] Optionally, in the same flow-gathering section, the inclination angles of each flow-gathering segment are the same; and / or, in two adjacent flow-gathering segments, the leeward end of the flow-gathering segment on the windward side is located on the side of the flow-gathering segment on the leeward side that is closer to the pipe clamp.

[0016] Optionally, the angle γ between the extension direction of the converging part and the split plane is selected from any value from 5° to 45°; and / or, the ratio of the length L of the converging part along the leeward direction to the inner diameter D of the clamp is selected from any value from 0.5 to 2; and / or, the ratio of the minimum distance d1 between the converging part and the clamp to the inner diameter D of the clamp is selected from any value from 0.2 to 1.5; and / or, the ratio of the minimum distance d2 between the projection of the converging part on the split plane and the axis of the clamp to the inner diameter D of the clamp is selected from any value from 0.8 to 2.

[0017] Optionally, the fin includes at least one row of the clamp portions, each row of clamp portions having the same dividing surface; in the same row of clamp portions, the center distance between two adjacent clamp portions is denoted as P, and the minimum distance between two flow-gathering portions between two adjacent clamp portions is denoted as d3, then 0.2≤d3 / P≤0.8.

[0018] The present invention provides a heat exchanger in a second aspect, comprising a refrigerant pipe and fins as described in any one of the first aspects, wherein the refrigerant pipe passes through the through hole and is thermally connected to the pipe clamp.

[0019] In a third aspect, this utility model provides an air conditioner that includes the heat exchanger described in the second aspect.

[0020] Based on the foregoing description, those skilled in the art will understand that in the aforementioned technical solution of this utility model, by providing multiple flow-gathering sections on the fins and tilting these sections towards the leeward side of the tube clamp, a flow-gathering groove is defined by the flow-gathering sections and the tube clamp. This allows the airflow to be compressed through the flow-gathering groove and guided to the leeward side of the tube clamp. Because the flow-gathering groove can compress the airflow, the airflow expands instantaneously after exiting the groove, effectively disrupting the vortex and bringing the airflow closer to the leeward side of the tube clamp, thus improving the heat transfer performance of the fins. Furthermore, because the flow-gathering groove guides the compressed airflow to the leeward side of the tube clamp, the heat transfer performance of the fins is further improved.

[0021] Furthermore, by having two flow-gathering grooves corresponding to each pipe clamp, the vortex on the leeward side of the pipe clamp is doubly restricted.

[0022] Furthermore, by setting the ratio of the height H of the converging section protruding from the fin body to the distance S between two adjacent fins in the heat exchanger to any value between 0.3 and 0.8, or any value between 0.15 and 0.5, a pressure relief gap can be formed between the converging section and the adjacent fins, allowing the compressed air in the converging channel to be depressurized through this gap. This reduces or avoids the large air resistance generated by the large compression of the airflow in the converging channel, as well as the large wind noise generated during sudden expansion.

[0023] Other beneficial effects of this utility model will be described in detail below with reference to the accompanying drawings, so that those skilled in the art can more clearly understand the improvement purpose, features and advantages of this utility model. Attached Figure Description

[0024] To more clearly illustrate the technical solution of this utility model, some embodiments of this utility model will be described below with reference to the accompanying drawings. Those skilled in the art should understand that the same reference numerals may indicate the same or similar components or parts in different drawings; the drawings of this utility model are not necessarily drawn to scale. In the drawings:

[0025] Figure 1 This is a schematic diagram of the structure of a heat exchanger provided by this utility model (only a few fins are shown in detail);

[0026] Figure 2 This is a schematic diagram of another heat exchanger provided by this utility model (only a few fins are shown in detail);

[0027] Figure 3 This is a simulation diagram of airflow in a heat exchanger in the existing technology;

[0028] Figure 4This is a top view of the fins having one row of tube clamps in the first embodiment of this utility model;

[0029] Figure 5 This is a top view of the fins with two rows of tube clamps in the second embodiment of this utility model;

[0030] Figure 6 yes Figure 5 A cross-sectional view of the middle fin along the AA direction (1 fin);

[0031] Figure 7 yes Figure 5 A cross-sectional view of the middle fin along the AA direction (2 fins);

[0032] Figure 8 This is a perspective view of the fins in the third embodiment of this utility model;

[0033] Figure 9 This is a perspective view of the fins in the fourth embodiment of this utility model;

[0034] Figure 10 This is a perspective view of the fins in the fifth embodiment of this utility model;

[0035] Figure 11 This is a perspective view of the fins in the sixth embodiment of this utility model;

[0036] Figure 12 This is a perspective view of the fins in the seventh embodiment of this utility model;

[0037] Figure 13 This is a schematic diagram of an air conditioner provided in this utility model.

[0038] Explanation of reference numerals in the attached figures:

[0039] 001. Heat exchanger;

[0040] 100. Fin; 101. Split surface; 102. Converging channel; 110. Fin body; 111. Turbulence hole; 120. Pipe clamp; 121. Through hole; 130. Converging section; 131. Converging segment; 140. Diverting section;

[0041] 200. Refrigerant pipe;

[0042] 002, Air conditioner; 300, Indoor air conditioner unit; 400, Outdoor air conditioner unit. Detailed Implementation

[0043] Those skilled in the art should understand that the embodiments described below are merely some embodiments of the present invention, and not all embodiments of the present invention. These embodiments are intended to explain the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. Based on the embodiments provided by the present invention, all other embodiments obtained by those skilled in the art without creative effort should still fall within the scope of protection of the present invention.

[0044] It should be noted that in the description of this utility model, terms such as "center," "upper," "lower," "top," "bottom," "left," "right," "vertical," "horizontal," "inner," and "outer," which indicate direction or positional relationships, are based on the direction or positional relationships shown in the accompanying drawings. These are used merely for ease of description and do not indicate or imply that the corresponding device or element 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. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0045] Furthermore, it should be noted that, in the description of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances. For example, unless otherwise specified, the terms "installation," "connection," "joining," and "fixing" can specifically refer to any feasible connection form such as bolt connection, screw connection, welding, insertion, riveting, fusion welding, or snap-fit.

[0046] Furthermore, it should be noted that in the description of this utility model, mm represents millimeter, cm represents centimeter, and m represents meter.

[0047] Furthermore, it should be noted that in the description of this utility model, the terms "coldness" and "heat" are two descriptions of the same physical state. That is, the higher the "coldness" of a target object (e.g., evaporator, air, condenser, etc.), the lower its "heat," and vice versa. A target object absorbs "coldness" while releasing "heat," and releases "coldness" while absorbing "heat." A target object retains "coldness" or "heat" to maintain its current temperature. "Refrigeration" and "heat absorption" are two descriptions of the same physical phenomenon; that is, a target object (e.g., evaporator) absorbs heat while refrigerating.

[0048] like Figure 1 and Figure 2 As shown, the heat exchanger 001 of this utility model includes multiple fins 100 and refrigerant pipes 200 passing through the multiple fins 100. The refrigerant pipes 200 are thermally connected to the fins 100, specifically by contacting each other and fixing them together by means of clamping, welding, etc., so that heat can be transferred between the refrigerant pipes 200 and the fins 100. That is, heat can be conducted from the refrigerant pipes 200 to the fins 100, or from the fins 100 to the refrigerant pipes 200.

[0049] like Figure 3 As shown, in the prior art, due to the presence of the pipe clamp 120, the airflow, after bypassing the pipe clamp 120, will be on the leeward side of the pipe clamp 120 (e.g., Figure 3 As shown in section F, a large flow stagnation zone (vortex) is formed, which affects the heat exchange efficiency between the airflow and the fin 100 and reduces the heat exchange performance of the fin 100.

[0050] To overcome the aforementioned technical problems in the prior art, this utility model provides a plurality of flow-concentrating sections 130 on the fin 100, and the flow-concentrating sections 130 are inclined toward the leeward side of the clamp section 120, so that the flow-concentrating sections 130 and the clamp section 120 define a flow-concentrating groove 102. This allows the airflow to be compressed through the flow-concentrating groove 102, and the compressed airflow to be guided to the leeward side of the clamp section 120. This will be described in detail below.

[0051] like Figure 4 and Figure 5 As shown, in this utility model, the fin 100 includes a fin body portion 110, multiple tube clamp portions 120 and multiple flow convergence portions 130.

[0052] Each clamp section 120 is provided with a through hole 121 for fixing the refrigerant pipe 200, and the through hole 121 is provided with the through hole 121 passing through the axis of the clamp section 120 and aligned with the windward direction of the clamp section 120. Figure 4 and Figure 5 The plane perpendicular to the middle fin 100 (the arrow on the right points in the opposite direction) is called the bisecting plane 101.

[0053] Each converging section 130 corresponds to a clamp section 120. The converging section 130 penetrates the dividing surface 101 and is positioned along the leeward side of the clamp section 120 (in contrast to...). Figure 4 and Figure 5 The middle fin 100 is inclined toward the clamp portion 120 in the direction indicated by the arrow on the right, so that the flow-gathering portion 130 and the clamp portion 120 define the flow-gathering groove 102.

[0054] The flow-gathering channel 102 is used to compress the airflow and guide the compressed airflow to the leeward side of the pipe clamp 120.

[0055] Those skilled in the art will understand that by providing multiple converging sections 130 on the fin 100 and tilting the converging sections 130 towards the leeward side of the clamp section 120, the converging sections 130 and the clamp section 120 define a converging channel 102. This allows the airflow to be compressed through the converging channel 102 and guided to the leeward side of the clamp section 120. Because the converging channel 102 can compress the airflow, the airflow expands instantaneously after exiting the converging channel 102, effectively disrupting vortices and bringing the airflow closer to the leeward side of the clamp section 120, thus improving the heat transfer performance of the fin 100. Furthermore, because the converging channel 102 guides the compressed airflow to the leeward side of the clamp section 120, the heat transfer performance of the fin 100 is further improved.

[0056] In this invention, the fin 100 includes at least one row of clamp portions 120, each row of clamp portions 120 having the same midpoint 101. For example, Figure 4 The fin 100 in the first embodiment shown has a row of clamp portions 120. Figure 5 The fin 100 in the second embodiment shown has two rows of clamp portions 120.

[0057] in other words, Figure 4 The first embodiment shown is the same as Figure 5 The second embodiment shown differs only in the number of columns of the clamp section 120; all other features are identical.

[0058] like Figure 4 and Figure 5 As shown, in the first and second embodiments of this utility model, each pipe clamp 120 can be provided with a flow-gathering part 130 on both sides perpendicular to its windward direction, so that each pipe clamp 120 corresponds to two flow-gathering grooves 102, thereby playing a dual role in restricting the eddy current on the leeward side of the pipe clamp 120.

[0059] like Figure 4 As shown, in the first and second embodiments of this utility model, the angle γ between the extending direction of the flow-gathering section 130 and the dividing surface 101 is selected from any value between 5° and 45°, so as to avoid the flow-gathering section 130 generating large wind resistance while ensuring that the flow-gathering groove 102 can compress the airflow. Specifically, γ can be any feasible value such as 5°, 8°, 10°, 12°, 15°, 18°, 20°, 25°, 30°, 34°, 37°, 40°, 45°, 50°, etc.

[0060] Furthermore, the included angle γ is preferably selected from any value between 10° and 30°.

[0061] Continue reading Figure 4 In the first and second embodiments of this utility model, the ratio of the length L of the converging section 130 along the leeward direction to the inner diameter D of the clamp section 120 is selected from any value between 0.5 and 2, so as to avoid the converging section 130 being too long or too short. Specifically, the ratio of L to D can be any feasible value such as 0.5, 0.55, 0.6, 0.7, 0.85, 0.9, 1, 1.2, 1.5, 1.7, 2, etc.

[0062] Continue reading Figure 4 In the first and second embodiments of this utility model, the ratio of the minimum distance d1 between the flow-gathering section 130 and the clamp section 120 to the inner diameter D of the clamp section 120 is selected from any value between 0.2 and 1.5, so as to avoid large wind noise while ensuring that the airflow can suddenly diffuse when it flows out of the flow-gathering groove 102. Specifically, the ratio of d1 to D can be any feasible value such as 0.2, 0.25, 0.3, 0.4, 0.5, 0.55, 0.6, 0.7, 0.85, 0.9, 1, 1.2, 1.5, etc.

[0063] Continue reading Figure 4 In the first and second embodiments of this utility model, the ratio of the minimum distance d2 between the projection of the flow-gathering section 130 on the dividing plane 101 and the axis of the clamp section 120 to the inner diameter D of the clamp section 120 is selected from any value from 0.8 to 2, so as to avoid the flow-gathering section 130 generating large wind resistance while ensuring that the flow-gathering groove 102 can compress the airflow. Specifically, the ratio of d2 to D can be any feasible value such as 0.8, 0.85, 0.9, 1, 1.2, 1.5, 1.6, 1.785, 1.9, 2, etc.

[0064] like Figure 4 and Figure 5 As shown, in the first and second embodiments of this utility model, in the same row of pipe clamp sections 120, the center distance between two adjacent pipe clamp sections 120 is denoted as P, and the minimum distance between two flow convergence sections 130 between two adjacent pipe clamp sections 120 is denoted as d3. Then, 0.2≤d3 / P≤0.8. This is to avoid the flow convergence section 130 generating large wind resistance while ensuring that the flow convergence groove 102 can compress the airflow.

[0065] The ratio of d3 to P can be any feasible value such as 0.2, 0.25, 0.3, 0.4, 0.5, 0.55, 0.6, 0.7, or 0.8.

[0066] like Figure 6 and Figure 7As shown, in the first and second embodiments of this utility model, the height H of the flow-gathering section 130 protruding from the fin section 110 is less than the distance S between two adjacent fins 100 in the heat exchanger 001, so that a pressure relief gap (not marked in the figure) can be formed between the flow-gathering section 130 and the adjacent fins 100, allowing the compressed air in the flow-gathering channel 102 to be depressurized through this pressure relief gap. This reduces or avoids the large wind resistance generated by the large compression of the airflow in the flow-gathering channel 102, and the large wind noise generated during sudden expansion.

[0067] The following reference Figures 8 to 10 The structure of the current-gathering part 130 of this utility model will be described in detail below.

[0068] like Figure 8 As shown, the third embodiment differs from the first and second embodiments described above in that the flow-concentrating section 130 is a rectangular sheet structure. Furthermore, the flow-concentrating section 130 is a structure formed on the fin 100 by a stamping process, thereby forming turbulence holes 111 on the sheet body 110.

[0069] from Figure 8 As can be seen, the turbulence hole 111 is located on the side of the flow-gathering section 130 closer to the clamp section 120. Alternatively, those skilled in the art may, as needed, position the turbulence hole 111 on the side of the flow-gathering section 130 away from the clamp section 120.

[0070] Continue reading Figure 8 In the third embodiment of this utility model, the included angle β between the flow-gathering part 130 and the sheet part 110 is selected from any value between 20° and 90°, so that when the air pressure in the flow-gathering groove 102 is large, the flow-gathering part 130 can guide the excess airflow through the turbulence hole 111 to the other side of the sheet part 110, thereby realizing the turbulence function.

[0071] Specifically, β can be any feasible value such as 20°, 25°, 30°, 35°, 38°, 40°, 45°, 46°, 48°, 50°, 56°, 61°, 68°, 70°, 75°, 80°, 83°, 89°, 90°, etc.

[0072] Furthermore, the included angle β is preferably selected from any value between 40° and 80°.

[0073] Furthermore, the ratio of the height H of the converging section 130 protruding from the fin section 110 to the distance S between two adjacent fins 100 in the heat exchanger 001 is selected from any value from 0.3 to 0.8, specifically any feasible value such as 0.3, 0.4, 0.5, 0.55, 0.6, 0.7, 0.8, etc.

[0074] Continue reading Figure 8In the third embodiment of this utility model, the extension length of the flow-gathering part 130 is m1, and the width of the flow-gathering part 130 is m2, then m2 / m1≥1.1.

[0075] like Figure 9 As shown, in the fourth embodiment, compared to the third embodiment, the flow-gathering section 130 has a triangular sheet-like structure. Furthermore, the apex of the triangle can point towards the windward direction of the clamp section 120.

[0076] like Figure 10 As shown, the fifth embodiment differs from the first and second embodiments described above in that the flow-gathering part 130 is a columnar structure, which can be fixed to the plate body by welding.

[0077] Furthermore, the ratio of the height H of the converging portion 130 protruding from the fin portion 110 to the distance S between two adjacent fins 100 in the heat exchanger 001 is selected from any value from 0.15 to 0.5, specifically any feasible value such as 0.15, 0.17, 0.2, 0.25, 0.3, 0.4, 0.5, etc.

[0078] Continue reading Figure 10 In the fifth embodiment of this utility model, the ratio of the extension length of the flow-gathering part 130 to the diameter of the flow-gathering part 130 is greater than or equal to 1.1.

[0079] like Figure 11 As shown, in the sixth embodiment, compared to any of the preceding embodiments, the flow-gathering section 130 includes at least two spaced-apart flow-gathering segments 131. Furthermore, within the same flow-gathering section 130, the inclination angle of each flow-gathering segment 131 can be the same. Also, in two adjacent flow-gathering segments 131, the leeward end of the windward flow-gathering segment 131 is located on the side of the leeward flow-gathering segment 131 near the hose clamp 120, to perform secondary compression of the airflow.

[0080] like Figure 12 As shown, in the seventh embodiment shown, compared with any of the previous embodiments, the fin 100 further includes a flow divider 140, which is perpendicular to the dividing surface 101 and is used to guide the airflow to flow in a direction perpendicular to the dividing surface 101.

[0081] Furthermore, the structure of the diverter 140 can be the same as that of the convergence section 130 described above.

[0082] It should be noted that the heat exchanger 001 described in any of the preceding embodiments is applicable to air conditioners.

[0083] like Figure 13 As shown, the present invention also provides an air conditioner 002, which includes the heat exchanger 001 described in any of the preceding embodiments.

[0084] The air conditioner 002 of this utility model can be a split-type air conditioner or an integrated air conditioner.

[0085] Among them, split-type air conditioners, such as Figure 13 The illustrated unit includes an indoor air conditioning unit 300 and an outdoor air conditioning unit 400. The indoor air conditioning unit 300 can be a wall-mounted air conditioner, a floor-standing air conditioner, a ducted air conditioner, a ceiling-mounted air conditioner, etc. The heat exchanger 001 described in any of the preceding embodiments can be arranged in the indoor air conditioning unit 300 or in the outdoor air conditioning unit 400.

[0086] Among them, the integrated air conditioner can be a window unit.

[0087] Furthermore, in the air conditioner 002, the heat exchanger 001 can be any feasible configuration such as type I, type L, type U, type O, multi-fold type, etc.

[0088] The technical solution of this utility model has been described in conjunction with several embodiments above. However, it will be readily understood by those skilled in the art that the protection scope of this utility model is not limited to these specific embodiments. Without departing from the technical principles of this utility model, those skilled in the art can disassemble and combine the technical solutions in the above embodiments, and can also make equivalent changes or substitutions to the relevant technical features. Any changes, equivalent substitutions, improvements, etc., made within the technical concept and / or technical principles of this utility model will fall within the protection scope of this utility model.

Claims

1. A fin suitable for a heat exchanger, characterized in that, include: Body part; Multiple pipe clamps, each of which is provided with a through hole for fixing the refrigerant pipe, and the plane passing through the axis of the pipe clamp and perpendicular to the windward direction of the pipe clamp is called the mid-plane; Multiple flow-gathering sections, each of which corresponds to one of the clamp sections; the flow-gathering sections penetrate the dividing surface and are inclined toward the clamp section along the leeward direction of the clamp section, so that the flow-gathering section and the clamp section define a flow-gathering groove; The flow-gathering groove is used to compress the airflow and guide the compressed airflow to the leeward side of the pipe clamp.

2. The fin according to claim 1, characterized in that, Each of the pipe clamps is provided with a flow-gathering section on each of its two sides perpendicular to its windward direction, so that each of the pipe clamps corresponds to two flow-gathering grooves.

3. The fin according to claim 1, characterized in that, The flow-gathering section is a rectangular or triangular sheet-like structure.

4. The fin according to claim 3, characterized in that, The current-gathering section is a structure formed on the fin by a stamping process, thereby creating turbulence-causing holes on the fin body; the turbulence-causing holes are located on the side of the current-gathering section near or away from the clamp portion; and / or, The included angle β between the flow-gathering section and the sheet section is selected from any value between 20° and 90°; and / or The ratio of the height H of the converging section protruding from the finned section to the distance S between two adjacent fins in the heat exchanger is selected from any value between 0.3 and 0.

8.

5. The fin according to claim 1, characterized in that, The flow-gathering section is a columnar structure; and / or, The ratio of the height H of the converging section protruding from the finned section to the distance S between two adjacent fins in the heat exchanger is selected from any value between 0.15 and 0.

5.

6. The fin according to claim 1, characterized in that, The flow-gathering section includes at least two flow-gathering segments spaced apart.

7. The fin according to claim 6, characterized in that, In the same flow-gathering section, the inclination angles of each flow-gathering segment are the same; and / or, In two adjacent flow-gathering sections, the leeward end of the flow-gathering section on the windward side is located on the side of the flow-gathering section on the leeward side that is closer to the pipe clamp.

8. The fin according to any one of claims 1 to 7, characterized in that, The angle γ between the extending direction of the flow-gathering section and the dividing surface is selected from any value between 5° and 45°; and / or, The ratio of the length L of the flow-gathering section along the leeward direction to the inner diameter D of the clamp section is selected from any value between 0.5 and 2; and / or, The ratio of the minimum distance d1 between the flow-gathering section and the clamp section to the inner diameter D of the clamp section is selected from any value between 0.2 and 1.5; and / or, The ratio of the minimum distance d2 between the projection of the flow-gathering part on the split plane and the axis of the clamp part to the inner diameter D of the clamp part is selected from any value between 0.8 and 2.

9. The fin according to claim 2, characterized in that, The fin includes at least one row of the clamp portions, each row of the clamp portions having the same split surface; In the same column of the clamp sections, the center-to-center distance between two adjacent clamp sections is denoted as P, and the minimum distance between two converging sections between two adjacent clamp sections is denoted as d3. 0.2≤d3 / P≤0.

8.

10. A heat exchanger, characterized in that, It includes a refrigerant pipe and fins as described in any one of claims 1 to 9, wherein the refrigerant pipe passes through the through hole and is thermally connected to the pipe clamp.

11. An air conditioner, characterized in that, Includes the heat exchanger described in claim 10.

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